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    • 专利摘要:
    A piston engine (1) for converting heat to work or for heating or cooling by work, comprising at least one chamber assembly (8) having at least two chambers (2,3,4) connected by at least one connecting channel (9, 10) at least two of the chambers (2, 4) are substantially thermally insulated from one another, and with a working fluid-impermeable piston (5, 6, 7) movably mounted in the respective chambers (2, 3, 4) for changing one of the chambers (2, 3, 4) and the piston (5, 6, 7) limited part volume of work, wherein at least one of the chambers (2, 4) heat transfer surfaces (34, 45) to increase its surface, wherein the pistons (5, 6, 7) and associated elements are associated with actuation means for defining movement profiles for each of the pistons (5, 6, 7), and wherein the actuation means are arranged to define at least two different movement profiles of the pistons (5, 6, 7) of the chamber ng (8) are formed.
    公开号:AT514226A1
    申请号:T50261/2013
    申请日:2013-04-16
    公开日:2014-11-15
    发明作者:Alfred Spiesberger
    申请人:Alfred Spiesberger；
    IPC主号:
    专利说明:

    1
    The invention relates to a reciprocating engine and to a method for its operation for the conversion of heat into work or for heating or cooling by the expenditure of labor, with at least one chamber arrangement having at least two, connected by at least one connecting channel chambers, wherein at least two of the chambers from each other are substantially thermally insulated, and movably disposed in the respective chambers, for a working medium impermeable piston for changing a limited by the chamber and the piston part-working volume, wherein at least one of the chambers heat transfer surfaces to increase its surface, and wherein the piston and associated elements are connected to actuating means for defining motion profiles for each of the pistons.
    The most common and well-known reciprocating engines for converting heat into work are automotive engines, such as the diesel engine or the gasoline engine. The thermodynamic cycle process underlying these machines is the diesel process or the Otto process or, in general, the Seiliger process. The preferred comparison process of the present invention, i. in contrast, the thermodynamic cyclic process which the present invention preferably approximates is the Carnot process known per se. This describes the physical maximum of the conversion of heat into mechanical energy for given heat sources and sinks. Consequently, both the above-mentioned cycle processes, as well as, for example, the machines modeled in connection with turbomachines Joul, Ericsen or Clausius-Rankine processes have an inherently suboptimal efficiency. An exception to this are Stirling machines whose comparison process is the Stirling process, since theoretically the same efficiency could be achieved by using a regenerator assumed to be perfectly functioning as in the Carnot process. However, this possibility has proven to be disadvantageous in many cases because the regenerator during a Prozessarbeitsspiels or process run or cycle of a cycle, which or which is the unique sequence of the cyclic characterizing thermodynamic state changes, including any intermediate clocks or steps, never the stored heat for In its entirety, 1/56 2 can create large dead or dead spaces through it.
    DE 27 36 472 A1 shows a valveless piston machine with two cylinders and arranged therein pistons whose cranks are offset so that the movement of the piston has a fixed phase shift of 90 °. To improve the heat transfer in the cylinders, one of which has a heating chamber and the other a cold space on the working medium (preferably helium) or vice versa, the piston and the cylinders are provided with complementary, projecting into the working space surfaces.
    The cylinders are connected by a heat exchanger extending arcuately between the cylinders, which has areas for heat storage and thus is a typical Regenerator for Stirling machines.
    The heat engine known from DE 103 19 806 B4 also works according to the Stirling principle. An expansion cylinder with a heater forms an expansion space and a compression cylinder with a cooler forms a compression space.
    The two work spaces have a plurality of parallel, conical tubes, in which engage respective piston pins of the respective associated pistons and fill them. The work spaces are connected via separate overflow channels, which are used as heat exchanger surfaces and provided with check valves, and the movement of the two pistons is also offset by 90 crank angle degrees.
    A disadvantage of the machines described in DE 27 36 472 A1 and DE 103 19 806 B4 is that in each case both pistons follow the same sequence of movements, namely essentially a sinusoidal movement, which is achieved only by a phase shift of 90 ° (corresponding to a quarter of a working cycle ) is offset in time between the pistons. However, such a process can roughly approximate an ideal Stirling process so that only a reduced degree of efficiency is achieved on its own.
    Pistons with different motion profiles have already been shown in connection with fundamentally different Stirling engines, but always at least one piston is a regenerator, which can never be permeable to a working medium, since the working fluid always either passes through or can or must be able to pass. Examples of such machines can be found in DE 195 28 103 Al, DE 198 54 839 CI and CH 701 391 Bl. Due to the completely different structure and the different operation but heat transfer surfaces are not provided in the chambers in any of these machines. Therefore, and also because all of the machines shown have a considerable dead space due to the regenerators alone, none of these machines is suitable for recreating the Carnot process.
    Accordingly, it is an object of the present invention to propose a reciprocating piston engine which operates according to an approximately ideal Carnot process by reducing dead spaces as much as possible, achieving optimal heat exchange between the chamber walls and the working medium in certain chambers, and at the same time the ideal state changes the Carnot process adapted movements of the piston allows.
    This object is achieved in a piston engine of the type mentioned in that the actuating means are designed to establish at least two different movement profiles of the piston of the chamber assembly. With which actuation means the motion profiles, i. the timings of the piston movements, are set, is of less importance. The term movement profile is intended to express in particular that different movement specifications are involved with different movement profiles in terms of their temporal characteristics, for example by achieving a fundamentally different chronological sequence of the piston movements. For example, only time-shifted or amplitude-different motion profiles are not different within the meaning of the invention, i. Different movements are not synonymous with different movement profiles. In addition, it is of central importance that - as already mentioned - the pistons assigned to the actuating means are impermeable to the working medium, that is, they can not pass the working medium through them and close tightly with the chamber walls, since this is the only way to avoid efficient operation. 3/56 4 dezindernden dead spaces can be achieved, which makes the invention different motion profiles for the solution of the task only makes sense. By contrast, machines with permeable or non-tight-fitting pistons pursue a completely different goal, namely the implementation of the stirring process, with the respective pistons usually operating as regenerators.
    Accordingly, in a method of the initially mentioned type for operating such a piston engine, the stated object is achieved in that in the course of a run in the chamber assembly run of the approximate Carnot process each of the pistons involved in the run at least once during a dead phase in the Substantially stands still, wherein one of the piston and its associated chamber limited part-working volume during the dead phase is substantially zero. The dead phase in this case denotes a temporal portion of a certain (finite) duration and not just a point in time, such as the reversal point or dead center typical in pistons.
    The term partial working volume refers to above and below to the one at a particular time in a chamber, i. limited by the chamber and its associated piston or existing therein volume. The term working volume refers in each case to the sum of the volumes of those partial working volumes and those volumes of the connecting channels, which are all interconnected, ie not sealed from each other, wherein the working medium contained in the working volume and the working medium contained in the sum of the volumes are identical. This also means that the working volume at least a certain part-working volume and vice versa the part-working volume is assigned a specific volume of work. In other words, and taking into account the relatively small volumes of the connection channels, it can also be said that the working volume is essentially the sum of the mutually associated partial working volumes assigned to it. In addition, it follows that a partial working volume of a chamber is always smaller (theoretically at most equal if there were exactly one working volume associated partial working volume and the related volumes of the communication channels would be zero) than the working volume assigned to it. Thus, for the purpose of increasing the efficiency, it is also possible for a chamber arrangement to have two or more still more separate working volumes in the chamber arrangement from four chambers, the pistons of the chamber arrangement being able to control different working media during different periods of time Different working media does not necessarily have to mean different types of working media, but it means that the different working media are in different volumes of work. Accordingly, a plurality of cycle processes, each of which in this case has its own working medium, can be executed in parallel in the chamber arrangement. If these circular processes are similar in their nature, for example two approximate Carnot processes, then one can also say that the approximate Carnot process is performed twice in the chamber arrangement. However, the circular processes performed in parallel in the chamber arrangement may also be different in their nature, for example an approximate Carnot and an approximate Stirling process. During operation of the piston engine according to the invention, the state points of a cycle process carried out with it can change from one cycle to another, without necessarily having to change the type of cycle process. This means that one cycle of a cycle, for example in the p-V diagram, may look different than another cycle of the same cycle. In particular, in actuating means for generating variable motion profiles, it is also possible that during operation of the piston engine according to the invention changes the nature of a cycle performed with her, for example, an initially executed in the chamber arrangement approximate Stirling process later transferred into an approximate Carnot process become.
    Furthermore, it may be that during a cycle of a cycle, or during the duration of this cycle, not all pistons of the chamber arrangement with the working medium involved in the passage, which may be in the chamber arrangement with other, independent working media, come into contact. Even if the chamber arrangement has only one single working medium, or a circular process is carried out in the chamber arrangement with only a single working medium, it is not absolutely necessary for all the pistons of the chamber arrangement to participate in one and the same cycle of the cycle because For example, some pistons of the chamber assembly may be stationary all the time during the one pass to receive only heat from its heat source, thus only one set of pistons involved in that one pass may exist in the chamber assembly.
    In any case, above and below, each run of a cyclic process is considered to be unique, even if two cycles of a cycle appear identical, for example, to their p-V diagrams.
    When at least two of the chambers have the heat transfer surfaces to increase their surface area, efficient and rapid heat exchange with the chamber environment can advantageously be achieved both in heat absorption and in heat release.
    In order to achieve the most ideal state change possible in one of the other chambers, in particular with regard to the isotropic state change aimed at during the Carnot process, it is advantageous if at least one of the motion profiles defined by the actuating means has at least one dead phase during which one of the corresponding with the Actuator connected piston is substantially stationary.
    Furthermore, it is favorable for such motion profiles to avoid dead spaces when a part of the working volume limited by the piston located in the dead phase of its movement profile and the chamber assigned to it is substantially zero. The temporarily stationary piston not only closes-as previously stated-tightly against its associated chamber, but also fills it completely, so that any working fluid is removed from the chamber. Of course, in relation to one of the other pistons, whose movement profile also has a dead phase, a partial working volume deviating from zero during the dead phase can be provided.
    To the own Carnot process asymmetry with regard to the timing of the working volume or the partial working volumes and the best possible practical feasibility of state changes, such as necessary for isentropic state changes relatively high speed of expansion and compression or necessary for isothermal state changes relatively slow Speed of expansion and compression or even the relatively short period of time for adiabatic chamber change of the working medium, to take into account, it has proved to be advantageous if at least one of the motion profiles different time intervals between a reversal point and the following dead phase on the one hand and between the Totphase and the temporal following reversal point on the other hand, in particular is direction-dependent. The different time intervals can be understood, for example, in the case of the isotropic expansion compared to the isentropic compression, which is illustrated in the following, with the result that at the same piston speed and the same piston cross-sectional area of the considered piston, the isentropic expansion lasts longer as the isentropic compression. Furthermore, it is in the isothermal state changes in order to perform this faithfully as possible, this compared to the change of the working medium in the other chamber - this intermediate cycle takes place beneficially faster, because time-saving and rather adiabatic-slow proceed.
    When the actuation means of the chamber arrangement or the motion profiles defined by them are coordinated with one another such that the observation is directed to a single working volume, which is essentially the sum of the associated, associated partial working volumes, at least one of the chambers during operation and at most two of the chambers have or have a substantially different from zero part-working volume, on the one hand advantageously a clear spatial separation of the state changes can be achieved and on the other hand makes sense the change of the working medium of the 7/56 8 nen in the other chamber be, while meanwhile, depending on the number of existing chambers of the chamber assembly, it is favorable to perform a change in state of the working medium - especially in 2 chambers - or no change of state - especially in more than 2 chambers. Thus, the working volume, i. Also, the working fluid, always a change of state or a chamber change in the (or the) designated chamber (s) subjected, which increases the efficiency of the piston engine. This applies regardless of whether more than one working medium is conveyed in a chamber arrangement with four or more chambers. In these cases too, at least one of the chambers and at most two of the chambers have, during operation, a proportion of one and the same working volume which is substantially different from zero. Possibly enclosed by other chambers of the chamber assembly and by the relevant working volume at any time during a process run tightly separated (partial) working volumes are therefore not excluded.
    To avoid efficiency-reducing losses during transport of the working medium between the chambers, it is advantageous if the at least one connecting channel is valveless. Thus, the opposite of a valve to the working fluid resistance, which is among other things, the necessary force to open the valve, avoided. In addition, valveless connection channels have the advantage of simpler construction and greater reliability.
    A way known in other machines to achieve the required heat transfer surfaces is that the heat transfer surfaces of one of the chambers are formed by the in-nenbewandung of the corresponding chamber and arranged in the corresponding chamber piston has a complementary to the heat transfer surfaces of the corresponding chamber surface, which is preferably also designed to transfer heat. With such a chamber geometry, a relatively large piston cross-section can be simulated with regard to the heat transfer in a relatively small space, with the same heat transfer, the piston movement relative to the simulated piston cross-section, i. on the actual 8/56 9
    Piston surface, apparently slowed down. As a result, a favorable surface-to-volume ratio is achieved, which favors a rapid heat exchange or a rapid compensation of any temperature differences in the working medium.
    In addition, one can accomplish that the heat transfer surfaces of one of the chambers are formed with a garland-like heat transfer body, which is arranged in the corresponding chamber or between the corresponding chamber and its associated piston. Such a garland-like heat transfer body is stretched or compressed during a piston movement and can achieve any surface enlargement depending on the number of layers or turns. With suitable dimensions, i. if the cross-section or base area of the fully compressed ("combined") heat transfer body substantially corresponds to the piston cross section, the partial working volume of the chamber in question can advantageously be reduced to zero, in particular if within the corresponding chamber or on the associated piston more complementary to the merged heat transfer body body is present. Another advantage of such a heat transfer body is the simple and good heat exchange with the chamber during the dead phase, since the necessary for the transmission distance is significantly shortened at superimposed layers. Of course, it is within the meaning of the invention, also several heat transfer surfaces in this manner, i. with garland-like heat transfer bodies, and it is also possible for a plurality of such heat transfer bodies to form the heat transfer surfaces or be arranged in a single chamber.
    Another possibility to constructively compensate for the asymmetry of the Carnot process explained above is that at least two of the chambers have different capacities and working temperatures, wherein in particular one chamber with relatively low working temperature has a larger capacity than the other chamber with relatively high working temperature. In particular, the capacity can be adjusted by different chamber cross sections. 9/56 10
    Moreover, it is advantageous if the pistons in their associated chamber have an approximately equal lift capacity. This results in a good use of space, since typically at least one outer dimension of the piston engine according to the invention anyway depends on the chamber with the largest lifting capacity. Furthermore, this promotes an advantageous identical parts concept of the components used.
    Particularly flexible and precisely configurable motion profiles can be achieved if at least one of the actuating means has a cam element with which the piston associated with the actuating means or elements connected to the piston is or are connected via a rolling element. In this case, the curve element, which may be formed for example by a cam, emulate exactly the desired movement through its arbitrarily producible form and optionally simultaneously act as a flywheel.
    To avoid any losses in reversing the direction of movement of the piston, i. between pulling and pushing movement, to avoid the rolling element can consist of at least two profile rollers, the at least two profile rollers do not change their directions of rotation due to their arrangement during a running in the chamber assembly (8) run a circular process with the same direction of rotation of their associated cam element. In this case, in particular, one of the profile rollers can be arranged radially inwardly relative to the cam element and the other profile roller opposite to it radially, so that during thrust movements a force transmission via the radially inner profile roller and during tensile movements a force transmission via the radially outer profile roller.
    In order to keep unwanted because losses causing forces or torques as low as possible, it has proven to be favorable when a determined in the stroke direction center distance between a guide roller of the rolling elements and one of the profile rollers of the same rolling element is small compared to a Lifting direction determined distance between the axis of rotation of the profile roller and the rolling element associated piston, preferably about zero, so that a possible friction 10/56 11 free movement of the rolling element associated piston is achieved in the chamber. As a result, particularly high friction-causing lateral forces on the piston can be avoided, which would otherwise worsen the efficiency of the piston engine.
    A mechanically even less limited power transmission from or to a piston can be achieved if at least one of the actuating means has a motor-generator unit and the or the actuating means associated (n) piston or associated elements with the rotor of Motor-generator unit is connected or are. The motor-generator unit can of course also consist of a motor and a separate generator whose rotor are mechanically coupled. Likewise, a possible servo amplifier and / or a programmable controller may belong to the motor-generator unit.
    The movement profiles realized with the aid of such actuating means can even be adaptable during operation if at least one of the actuating means is suitable, in particular freely programmable, for generating variable movement profiles. As a result, consideration can be given in particular to a different amount of available heat or work and the other changing boundary conditions for the operation of the piston engine according to the invention.
    Since the forces exerted by or on the pistons naturally also vary in magnitude depending on the chamber, it is favorable if at least one of the actuating means and its associated piston a transmission gear, in particular a pantographartiges coupling gear, or a ball screw is interposed. For example, this also favorable movement speeds of the rotor of electromagnetic actuation means can be achieved without having to do without the optimum for the state change process speed.
    In the case of two of the chambers with the heat transfer surfaces and to be able to perform as faithfully as possible isentropic state changes despite the limited in the chambers with the heat transfer surfaces 11/56 12 conditions for an adiabatic change in state of the working medium, it is advantageous if the chamber arrangement has three chambers, wherein the middle chamber is connected by two of the connecting channels with the other two chambers and the central chamber is free of heat transfer surfaces to increase their surface and thermally at least one of the other chambers, in particular at least opposite the chamber with relatively high operating temperature isolated.
    In this case, given, for example, due to mechanical limitations, given piston speed a comparatively even faster volume change can be achieved if the middle chamber has a larger capacity than one of the chambers with a relatively high operating temperature. In addition, the required in one of the isentropic state change of the working medium maximum of the working volume can be made available as appropriate.
    Due to the different tasks relating to heat exchange with the working fluid and to avoid a heat flow between the chambers, it is advantageous if one of the chambers with the heat transfer surfaces made of a material with relatively high heat capacity and good thermal conductivity, in particular copper or aluminum or their alloys is and the middle chamber is made of a thermally poorly conductive material, in particular ceramic or glass ceramic.
    If one of the chamber arrangements has a gas with a high specific gas constant, in particular helium, as working medium, the flow losses during the transport of the gas between the cylinders can be reduced since the moved mass can remain small. Furthermore, the installation space of the chamber arrangement can thereby be reduced with the same energy converted by the chamber arrangement. Of course, it is particularly advantageous if several or even all chamber arrangements have a corresponding working medium, but different working media can also be used. On the other hand, 12/56 13 is also associated with the use of air as a working medium with advantages; For example, depending on the working pressure, the tightness of the chamber arrangement is less problematic, since leakage of air into the environment is generally not critical.
    The forces to be transmitted between one of the pistons and its associated actuating means can further be optimized and the associated losses reduced if at least one of the pistons is connected to a spring element, in particular a magnetic, mechanical or gaseous spring element, to support the actuating means associated with the piston is. In particular, this can be any losses caused by the actuating means, in particular caused by electromagnetically operating actuation means while they predict dead phases, can be reduced.
    The forces transmitted to the necessary linear movements of the pistons, for example, to a substrate or to a bearing of the piston engine naturally lead, e.g. due to unavoidable damping, etc., to losses, which can be reduced if at least one further, substantially identical to the chamber arrangement chamber arrangement is provided with piston, with the mass inertia effects of the pistons together with associated elements of all chamber arrangements substantially cancel. The essential mass inertia effects are in particular the inertia forces of the pistons, and those of the elements connected to the piston, wherein also moments of inertia, for example, the actuating means are included.
    It is also advantageous if at least two different chamber arrangements belonging pistons are connected to a common actuating means. Preferably, the pistons connected to a common actuating means are related, i. the volume changes achieved by them belong to similar state changes in the various chamber arrangements. The common actuating means may for example cause a symmetrical movement of the pistons of different chamber arrangements, the synchronization of the movements being guaranteed naturally by the unit of the actuating means.
    In the above-mentioned method for operating a piston engine of the type described so far, it is particularly favorable if a working volume of the chamber arrangement, which is essentially the sum of the associated, associated partial working volumes, at all times substantially to its associated part Working volumes of one o-the two of the chambers is distributed. In such a distribution, i. If, at any given time or at any time during a cycle, any third or further chambers of the same chamber arrangement have a substantially zero working volume, a nearly ideal and thus almost unaltered change of state of the working medium or a change in chamber of the working medium be achieved, which is desirable to achieve the optimum efficiency.
    In order to achieve a homogeneous temperature in the entire volume of the working medium, it is favorable if the duration of the dead phase of one of the pistons or in the chamber associated with the piston is almost equal to or greater than the duration of time with this dead phase at least partially with respect to the passage overlapping pass associated with the approximately isothermal state change in one of the other chambers involved in the pass. In such a process, the isothermal state change preferably takes place entirely in a single chamber of the chamber arrangement.
    If within the chamber arrangement with respect to the passage each of the dead phases involved is at least 15%, in particular at least 25%, of the time of passage, a particularly good and uniform temperature distribution in the relevant chamber or its associated piston can adjust during one of the dead phases whereby, for example, the following in the chamber following its dead phase state change of the working medium can follow the desired desired state change particularly well.
    It is advantageous if, in one of the other chambers participating in the passage 14/56 15 of a chamber process carried out in the chamber assembly, a change in state of the working medium can be carried out undisturbed and further corresponds to a clear assignment of a chamber to a few, immediately successive state changes, if each of the pistons involved in the pass has in one of its associated chambers with direct connection to exactly one more of the chambers involved in the passage exactly one pass associated with the dead phase. For the same reasons, it is advantageous if each of the pistons involved in the pass has exactly one dead phase associated with the pass in one of its associated chambers having unidirectionally flowed through the unidirectionally flowed direct connection to exactly two other of the chambers involved therein.
    Conversely, a plurality of similar state changes, especially if they do not require heat exchange, also be performed in the same chamber, so that each of the pistons involved in the passage in one of their associated chambers with bidirectional flow through the participating working medium direct connection to two more of the involved chambers with respect to the passage has two dead phases associated with the passage.
    A particularly good approximation to the comparison process can be achieved if the total duration of all the pass associated Totphasen the piston, which participates in at least one of the involved participating in the pass approximately isentropic state changes, is longer than the dead phase of the piston in one of the Pass involved participates in approximately isothermal state changes. Accordingly, it is favorable if, in total, the two approximately isotropic state changes of the pass are carried out more rapidly, in particular at least twice, faster than the sum of the two approximately isothermal state changes assigned to the pass. Thereby, enough time can be given to the heat exchange during the isothermal state change, while counteracting a change in entropy in the short time during the faster isentropic state changes. 15/56 16
    In the present method, an adjustment of the working volume during operation of the subject piston machine can also be made if at least one thermodynamic state variable of one of the working media in the chamber arrangement is determined and the time course of one of the working volumes of at least one of the chamber arrangements, which is substantially the sum its associated, inter-related partial working volumes is changed as a function of at least one determined state variable, whereby the approximate Carnot process modified and better adapted to changing boundary conditions, such as the available heat energy. This means that subsequent runs of the cycle may be different with respect to their state points.
    Instead of directly determining a thermodynamic state variable or additionally at least one measured variable, in particular the position of one of the pistons, which are determined by the working medium or the upper or lower process temperature available for the cycle, can be determined is associated with a thermodynamic state quantity of one of the working media in the chamber arrangement, and the time course of one of the working volumes of at least one of the chamber arrangements, which is essentially the sum of the associated, associated partial working volumes, are changed as a function of the at least one determined measured variable , It is irrelevant whether a thermodynamic state variable is actually derived from the measured variable determined and / or whether other measured variables or specifications would be required for it.
    The invention will be explained below with reference to particularly preferred embodiments, to which it should not be limited, and with reference to the drawings. In detail in the drawing:
    Figure 1 is a perspective view of a piston engine according to the invention with three pistons, which are each connected to a cam.
    Fig. 2 is a perspective view of an alternative heat transfer body for use in a chamber of an inventive piston machine;
    3a is a perspective view of a spiral-shaped heat transfer body;
    FIGS. 3b and 3c are fragmentary sectional views, respectively, of the heat transfer body of FIG. 3a in a chamber in a partially open or fully compressed position;
    4a and 4b are schematic plan views of two different chamber geometries, with circular or elliptical bases;
    5 is a perspective view of a rolling element with lateral guide rollers.
    6 is a partial sectional view of an alternative rolling element with two profile rollers.
    7 shows a schematic view of a rotationally symmetrical cam, with which three pistons are connected, along an axis of rotation;
    Fig. 8 is a schematic partial sectional view through a device with two related pistons of different chamber arrangements, a common motor-generator unit and intermediate gear transmission and left / right-handed Doppelkugelgewindetrieb;
    9 is a temperature entropy diagram of the ideal Carnot process;
    Fig. 10 is a pressure-volume diagram of the ideal Carnot process;
    Figure 11 is a diagram of the various partial working volumes of a three chamber chamber arrangement as a function of time during a process run;
    Fig. 12 is a diagram of the various partial working volumes of a two chamber chamber assembly as a function of time during a process run;
    Fig. 13 is a diagram of the various partial working volumes of a two-chamber chamber arrangement as a function of time during a process run, the state changes taking place in other chambers as compared to Fig. 12;
    FIG. 14 shows a further variant of the time profile of the individual partial working volumes; FIG. and
    Fig. 15 is a diagram of the various partial working volumes of a chamber arrangement with four chambers as a function of time 17/56 18 during a process run.
    In Fig. 1, a reciprocating engine 1 for converting heat into work or for heating or cooling by the expenditure of work is shown. The piston engine 1 has three chambers 2, 3, 4, each with one of the respective chamber 2, 3, 4 associated piston 5, 6, 7. The three chambers 2, 3, 4 together form the single chamber assembly 8 of the piston engine 1. The chambers 2, 3, 4 are connected by connecting channels 9, 10 between the chambers 2 and 3 or 3 and 4, wherein between the two outer chambers 2, 4 no direct connection channel exists, but these two chambers 2, 4 only through the middle chamber 3 communicate with each other through. The chambers connecting the chambers 2, 3, 4 connecting channels 9, 10 are to avoid dead space (dead space) with as small as possible, but the requirements of the most feasible without resistance flow through volumes.
    In each chamber 2, 3, 4, a single piston 5, 6, 7 is arranged. However, the cross sections of the pistons 5, 6, 7 are different between the chambers 2, 3, 4. Each piston 5, 6, 7 is connected to an actuating means in the form of a cam 11, 12, 13, wherein the three cam discs 11, 12, 13 are rotatably connected to a common axis 14. The cams 11, 12, 13 control the movement of the respective piston 5, 6, 7 or are arranged for the transmission of power to and from the piston 5, 6, 7. The axis 14 of the cams 11, 12, 13 is mounted in a frame 15, which also carries the chamber assembly 8. The pistons 5, 6, 7 are arranged vertically above the axis 14 of the cams 11, 12, 13 and connected via connecting elements 16 with the cams 11, 12, 13.
    The connection of the pistons 5, 6, 7 with the cams 11, 12, 13 works mainly on arcuate rolling elements 17, which are mounted on the cams 11, 12, 13 and are connected via piston rods 18 with the piston 5, 6, 7 in connection ,
    The rolling elements 17 (see Fig. 5 for a detailed illustration) are also also mounted on lateral guide rails 19 in order to prevent any losses in the power transmission, for example in the form of lateral force components. 18/56 19
    In each case two guide rollers 20 (see Fig. 5) attached laterally to the rolling elements 17 are in contact with a guide rail 19 on each side.
    The cams 11, 12, 13 have circumferentially se se a se with a radially variable distance from the axis of rotation 14 of the cam 11, 12, 13 open profile groove 21, in each of which a profile roller 22 of the rolling elements 17 engages. The profile groove 21 is characterized by a thinner compared to the cam 11, 12, 13 side wall 23, which increases the cam 11, 12, 13 radially outward, and by a substantially the outer edge 24 of the cam 11, 12, 13 in the course the following
    Outside wall 25 formed. The function of the outer wall 25 is it, in addition to the forces exerted by the cam 11, 12, 13
    Pressure forces on the piston 5, 6, 7 can also exert tensile forces. In sections 26, which respectively correspond to a dead phase of the respective cam 11, 12, 13 associated piston 5, 6, 7, i. a completely pushed into the respective chamber 2, 3, 4 position of the piston 5, 6, 7, the profile groove 21 is therefore interrupted and the profile roller 22 only at the outer edge 24 of the cam 11, 12, 13 be stored, as outgoing from This position no tensile forces on the part of the piston 5, 6, 7 are possible.
    The top of each rolling element 17 is rigidly connected via an adjusting element 27, by means of which the distance between the rolling element 17 and the piston 5, 6, 7 is exactly adjustable, with a piston rod 18. At the other end of the piston rod 18, the actual piston 5, 6, 7 is arranged, wherein the three pistons 5, 6, 7 are designed differently according to their different tasks. Two of the piston rods 18 of the pistons 5, 6 are each surrounded by a jacket 18 'which thermally isolates the piston rod from the environment.
    The left piston 5 is disposed in a warm chamber 2, i. the working temperature of this chamber 2 is higher than that of the cold chamber 4 on the right side. Accordingly, the piston 5, as well as the side wall 28 of the warm chamber 2 is insulated to the outside, which is indicated by insulating layers 29, wherein in the insulating layer 29 a plurality of mirrored Wärmeschutzble- 19/56 20 che integrated to minimize heat transfer by radiation , The insulating layer 29 itself consists of airgel. But it is also possible to remove the airgel and to evacuate the space thus liberated, since this space is stable and airtight. Instead of the airgel but other available insulation materials such as mineral wool can be used. In addition, the left and middle chambers 2, 3 of the chamber assembly 8 are only connected in each case via three pins 29 ', which in turn are hollow and made of a material with poor thermal conductivity, with the main body 8' of the chamber assembly 8. The inner surface of the main body 8 'of the chamber assembly 8 and the outer surface of the left and middle chambers 2, 3 span, so to speak, between them the space occupied by the insulating layer 29. In the upper part of the chamber 2, a heat transfer body 30 is fixed, which is surrounded by a heating chamber 31. The heat transfer body 30 thus separates the heating chamber 31 from the remaining chamber 2 and the partial working volume 33 of the warm chamber 2. For bottom facing the piston 5, the heat transfer body 30 heat transfer surfaces 34 to increase the surface of the warm chamber 2 by the bottom surface follows a serrated pattern, wherein the inclined located in the warm chamber 2 heat transfer surfaces 34 of the teeth are arranged so that their upper and lower edges 35, 36 each lie in one plane and in plan view with the axis of a connecting channel 9 to the middle Chamber 3 a right angle. On the opposite upper side of the piston 5, a complementary heat transfer body 37 is arranged, which is therefore also serrated and is moved with the piston 5, wherein the teeth are conclusively inserted into the interstices of the teeth of the upper heat transfer body 30, so that when fully into the chamber 2 guided piston 5 substantially no dead space between the heat transfer bodies 30, 37 remains. Accordingly, the partial working volume of the warm chamber 2 is limited by the two heat transfer bodies 30, 37 and the inner surface of the side wall 28 of the chamber 2 and the cylinder. The heating chamber 31 has on both sides of line connections 38, 39, which allow the supply and removal of a heating medium, for example, warm air or liquid in 20/56 21 or from the heating chamber 31, so that the temperature of the upper heat transfer body 30 and the lower Heat transfer body 37, which is in contact with the former during a dead phase over a large area, can be practically brought to those of the heating medium. In this case, both the line connections 38, 39 as well as the upper side of the heating chamber 31, the same insulation 29 as the side wall 28 of the hot chamber 2 and the piston fifth
    The connecting channel 9 to the middle chamber 3 is arranged in the side wall 28 of the hot chamber 2 approximately at the level of the lower edges 36 of the teeth of the upper, immobile heat transfer body 30. In order to facilitate the flow of the working medium through the connecting channel 9 and into the middle chamber 3 in the compression of the warm chamber 2, the lower tips of the upper heat transfer body 30 and the feet (ie in the lower region of the teeth) of the lower heat transfer body 37 are narrow Passage channels 40 interspersed, which allow an abbreviation of the flow of the working medium. At a fully compressed position of the piston 5, i. when the piston 5 is completely inserted into the chamber 2 (see piston 7 in the cold chamber 4), the passage channels 40 of the two heat transfer bodies 30, 37 respectively open into passage channels 40 of the other heat transfer body 37, 30. Preferably lie in this position all passageways 40 in a plane and at the height of the connecting channel. 9
    The middle chamber 3, which is connected by the short connecting channel 9, which is only long enough to traverse the side walls 28, 41 of the warm chamber 2 and the middle chamber 3 by the shortest route, with the warm chamber 2, also has a Circular base on, however, more than twice as large as that of the warm chamber 2. The connecting channel 9 is inserted in each case with a spherical end hinged and slightly displaceable in the side walls 28, 41 of the warm chamber 2 and the middle chamber 3, whereby a slight change in position of the warm and middle chamber 2, 3 is taken into account during operation. The interior of the middle chamber 3 is purely cylindrical, i. There are no heat transfer surfaces to enlarge the surface. On the contrary, both the side wall 41 of the chamber 3 and the upper inner surface and the inside of the piston 6, i. the part of the working volume of the middle chamber 3 facing side of the arranged in the chamber 3 piston 6, isolated, so that heat exchange with the working medium is avoided as much as possible. The piston 6 reduced in the illustrated compressed position, the available part-working volume of the chamber 3 to substantially zero, the flat top of the piston 6 is applied to the upper flat inner side of the chamber 3 conclusive. So that the working medium can easily leave the chamber 3 during compression, the upper flat inner side of the chamber 3 is arranged at the level of the connecting channel 9 to the warm chamber 2.
    Opposite the connecting channel 9 to the warm chamber 2, the side wall 41 of the middle chamber 3 has a further connecting channel 10, which connects the part-working volume of the middle chamber 3 with that of the cold chamber 4. The two connection channels 9, 10 are preferably at the same height and in this example even on a line. For improved removal of the working medium, the upper inner side of the chamber 3 has a peripheral recess in the manner of an outer drainage channel 42 so that working fluid forced outwardly from the piston 6 during compression reaches the lateral connection channels 9, 10 through the annular drainage channel 42 can. This outflow option is particularly advantageous because depending on the position in the cycle each only the drain through one of the two of the connecting channels 9, 10 is provided or possible, so that the working fluid through the drainage channel 42 can get better from one side to the other.
    The cold chamber 4 connected to the middle chamber 3 and opposite the warm chamber 2 has heat transfer bodies 43, 44 comparable to the warm chamber 2, whose serrated surface forms oblique heat transfer surfaces 45 for enlarging the surface of the interior of the chamber. In contrast to the warm chamber 2, neither the side wall 46 of the chamber 4 nor its upper side 47 or the piston 7 is insulated to the outside here.
    On the contrary, convectors 48 are connected on all sides with the chamber 22 and the piston 7, so that the working temperature of the cold chamber 4 can be kept as equal as possible to the ambient temperature of the piston engine 1. The convectors 48 have a basically with the heat transfer bodies 43, 44 comparable, serrated shape, but whose edges are aligned at right angles to the edges of the arranged in the chamber 4 heat transfer body 43, 44. Of course, other known heat exchangers could be used instead of the convectors 48.
    Rotates the axis 14 in one direction, so that the approximate Carnot process is passed right-handed, the piston engine 1 of the invention can be operated as an engine (engine), wherein on the axis 14 mechanical work is delivered, the warm chamber 2 (the Working medium) is supplied at the upper process temperature heat and the cold chamber 4 at the lower process temperature heat as so-called waste heat to the environment gives to compensate for the Entropiebilanz. If the axis 14 rotates in the other direction, so that the approximate Carnot process is passed through to the left, then the piston machine 1 according to the invention can be operated as a working machine (refrigeration machine, heat pump), mechanical work being supplied to the axis 14, the cold chamber 4 At the lower process temperature, heat is supplied or the cold chamber 4 extracts heat from the external environment at the lower process temperature and the warm chamber 2 at the upper process temperature heat as useful heat or waste heat, depending on the application and approach, to compensate for the Entropiebilanz again , The shapes or contours of the cams 11, 12, 13 or the movement profiles defined by these are different not only between the outer chambers 2, 4 and the middle chamber 3 but also between the outer chambers 2, 4, the difference the movement profiles of the outer chambers 2, 4 associated piston 5, 7 shows mainly by their opposite sense of direction.
    In Fig. 2, a garland-like heat transfer body 49 is shown in a partially expanded position. As can be clearly seen from the figure, the surface of this heat transfer body 49 exceeds its base area by a multiple. 23/56 24
    The garland-like heat transfer body 49 is made up of a stack of a plurality of annular discs 50 which are mutually spaced on both sides, i. with the two adjacent discs 50, are connected. The outer circumference of all disks 50 is the same, but the radius of the inner edge 51 increases from top to bottom in the stack, i. the lowermost annular disc 50 is narrower than the discs 50 above. The garland-like structure is achieved by forming the connections 52 to the adjacent discs 50 only along a connecting line passing through the center of the discs 50 and crossing the connecting lines at the top and bottom of each disc 50, in particular at right angles.
    A variant of a garland heat transfer body 49 is shown in Fig. 3a, wherein this heat transfer body 53 has substantially the shape of a spiral. In a partially expanded position, as shown in Fig. 3a, each turn of the spiral contributes to the enlargement of the surface, i. the surfaces of each individual turn form the heat transfer surfaces 54 for a work medium therebetween or surrounding the spiral. As with the heat transfer body 49 described above, the inner radius of the spiral increases from top to bottom, so that the spiral forms a conical inner space 55.
    In Fig. 3b and 3c of the spiral heat transfer body 53 shown in FIG. 3a is arranged in a chamber 56 with a piston 57 arranged. Instead of the spiral-shaped heat transfer body 53, the heat transfer body 49 according to FIG. 2 could just as well be used here, so that the following description applies analogously to the other heat transfer body 49. The heat transfer body 53 shown may be connected both to the top with the inside of the chamber 56 and down to the top of the piston 57. Such a connection is required when the position of the free state of the heat transfer body 53 is smaller than the maximum expanded position in the chamber 56, since in this case the heat transfer body 53 has to be pulled apart against the spring force exerted by it. In Fig. 3b, a 24/56 25 partially expanded position is shown. Inside the heat transfer body 53, a conical pin 58 can be seen, which projects into the conical inner space 55 formed by the heat transfer body 53, the radius of the pin 58 on its underside 59 corresponding to the inner radius of the lowermost layer 60 of the heat transfer body 53. In addition, the radius of the spigot 58 at the upper end 61 corresponds to the inner radius of the uppermost layer 62 of the heat transfer body 53. Thus, in a compressed position, the spigot 58 completely fills the heat transfer body 53, as can be seen in FIG. 3c. In this case, the layers 63 of the heat transfer body 53 lie directly against one another, so that substantially no dead space remains in the respective chamber 56.
    Of course, other forms are conceivable for the chambers instead of the previously described cylindrical base surfaces. For example, FIGS. 4a and 4b show a comparison of two chambers 64, 65 and 66, 67 with circular or elliptical base surfaces, wherein the surfaces are equal in magnitude. As can be seen from the comparison, with equally long connecting channels 68 or 69 between the mutually facing side walls of the elliptical chambers 66, 67 more space than in the circular chambers 64, 65, so that the elliptical chambers 66, 67 better insulated from each other thermally can be as the circular chambers 64, 65.
    In Fig. 5, one of the rolling elements 17 shown in FIG. 1 is shown enlarged. The rolling element 17 consists essentially of a bow-shaped or bridge-shaped basic body 70 with two side walls 71, 72 and a bridge element 73, which connects the two side walls 71, 72. Between the two side walls 71, 72, a profile roller 22 is mounted on one side, so that between the profile roller 22 and the opposite side wall 72 remains a distance. On the outer side of the two side walls 71, 72 are each two smaller guide rollers 20 are mounted, whose axes are angled relative to an axis of the profile roller 22, but lie advantageously with this in a plane. All rollers 22, 20 are equipped with largely frictionless ball bearings. At the top of the bridge member 73, a pin 74 is formed, which is a 25/56 26
    Passage opening 75, for example, for a coupling pin, has, and for the connection with a piston rod 18 (see Fig. 1) is arranged.
    An improved variant of the rolling element 17 according to FIG. 5 is shown in FIG. 6 together with a sectional view of the profile groove 21 of a cam 11, this rolling element 76 instead of a single profile roller 22 having two independent profile rollers 77, 78 of different diameters. The larger profile roller 78 is designed to bear on an outer edge 24 of the cam 11, while the smaller profile roller 77 is adapted to bear against the outer wall 25 of the profile 21. Accordingly, the two profile rollers 77, 78 rotate in a movement of the cam 11 in opposite directions of rotation. The advantage of such a roller arrangement is that the two profile rollers 77, 78 - in contrast to a single profile roller 22 which alternates at the outer edge 24 of the cam 11 and the outer wall 25 of the profile 21 - their direction of rotation at any time during a complete Rotation of the cam 11 must change.
    FIG. 7 schematically shows an expansion possibility of the piston engine 1 according to FIG. 1. In this case, in addition to the piston assembly 8 shown in FIG. 1, two further piston assemblies 79, 80 may be arranged symmetrically about the axis of rotation 81 of the cam 82, wherein three similar pistons 83, 84, 85 of the various piston assemblies 8, 79, 80 with a common cam 82nd are connected. In this case, the cam disk 82 has a symmetry corresponding to the piston arrangements 8, 79, 80, in this case a threefold rotational symmetry. In such a piston machine 86, the same state changes of identical circular processes are carried out in the chamber arrangements 8, 79, 80 at the same time, whereby forces acting on the cam disk 82 always have the same magnitude and symmetrical forces on the cam disk 82, so that no resulting radial force acts on the rotation axis 81 acts and thus losses, for example, in the bearings of the rotation axis 81, can be reduced and a nearly vibration-free operation of such a piston machine is given. Furthermore, the mass inertia effects 26/56 27 of the pistons 83, 84, 85 of the chamber arrangements 8, 79, 80 are also canceled out. In order to achieve a similar effect by means of another structure, instead of the cam 82, a cam ring could be used with an inner diameter placed cam element, wherein the symmetrically arranged chamber assemblies are centered about the axis of rotation of the ring, wherein the rolling elements outwardly on the cam elements of the cam ring would be directed.
    Fig. 8 shows a partial sectional view of a piston engine 87 with opposing chamber arrangements, of which only schematically the related pistons 88 with their common actuating means 89, a motor-generator unit, which is adapted both for application and for receiving torques shown are. The actuating means 89 and the actuating means 89 associated piston 88 is a common gear transmission 90 with the gears 91, 92 and one ball screw 93 interposed, one of which is left-hand and the other clockwise. Both ball screws 93 have the same pitch and number of gears, are rotatably connected to each other or are to be understood as a single Doppelkugelgewindetrieb with opposing threads, which is mounted on two bearings 94. The nuts 95 are each connected via a bearing between two rollers 96 guide frame 97 with the piston 88. The linear movement of at least one of the pistons 88 is thereby recorded by means of a displacement measurement 98. In this arrangement, the inertia forces of the pistons 88, assuming their same embodiment of course, and the rigidly connected elements, the same design also provided assuming, on.
    As explained in detail at the outset, the - basically known - comparison process of the piston machine according to the invention is the Carnot process. The diagram 99 shown in FIG. 9 qualitatively describes the relationship between temperature and entropy of the working medium during a passage of the cycle. The inherent entropy of the working medium is plotted on the abscissa axis 100, while the temperature of the working medium is plotted on the ordinate axis 101. The four edges 102, 103, 104, 105 of the rectangular course 106 of the 27/56 28
    Circular process each represent a state change of the working medium and connect four state points 107 in the corners of the rectangle. The edges 102, 104 parallel to the axis of abscissa 100 corresponding to isothermal state changes 102, 104 at an upper temperature To and a lower temperature Tu and the edges 103, 105 parallel to the ordinate axis 101 correspond to isentropic state changes 103, 105 at different entropy levels. Depending on whether the reciprocating engine 1 is used to convert heat to work or to heat or cool by the application of labor, the thermodynamic state of the working medium that is changing during the process follows the rectangle 106 clockwise and counterclockwise, respectively.
    In Fig. 10, the same - basically known - circular process as shown in Fig. 9 in another coordinate system or diagram. At the abscissa axis 108 of this p-V diagram 109, the working volume of the working medium and at the ordinate axis 110 the pressure is plotted. In-process state consecutive state points 107 are at both different pressure and volume levels, i. there is neither an isobaric nor an isochoric state change. The two isothermal state changes 102, 104 are shown as solid lines and the two isentropic state changes 103, 105 as dashed lines. As can be seen particularly well from this diagram 109, in the Carnot process shown, the volume changes, concerning the absolute difference value, during the isothermal state changes 102, 104 are un different, in particular the required volume change at the higher temperature To -. in the warm chamber 2 - considerably smaller than that at the lower temperature Tu - i. in the cold chamber 4. Also, the volume change during the isentropic state changes 103, 105 is dependent on isentropic compression or isentropic expansion: for example, in a heat engine (illustrated process, dextrorotatory) the volume change during isentropic Compression 105 is smaller than during the isentropic expansion 103. For comparison with the following figures, the working volumes VI, V2, V3, V4 in the four state points 107 are plotted on the abscissa axis 108 and on the ordinate axis 110 are the completeness half the associated pressures pl, p2, p3, p4 drawn.
    FIGS. 11 to 15 each show a qualitative diagram of the partial working volumes of the chambers of a chamber arrangement of the piston machine according to the invention as a function of time and for a complete passage 113 or complete working cycle. On the ordinate axis 111, on which the partial working volumes are plotted, the volume levels VI, V2, V3, V4 drawn in the diagram in FIG. 10 are also shown at the state points 107 for orientation. On the abscissa axis 112, on which the time or the position within the passage 113 is plotted, are also plotted the state changes, as indicated in the diagrams in FIGS. 9 and 10, wherein during some time sections, such as when the working medium remains in a state point 107, no state change takes place.
    In Fig. 11, the course of the partial working volumes of the three chambers 2, 3, 4 in a piston engine 1 according to FIG. 1 is shown. The solid line 114 represents the partial work volume or its course in the warm chamber 2, the dashed line 115, the partial working volume in the cold chamber 4 and the dotted line 116, the partial working volume in the middle chamber 3. At the origin the time axis 112 is the working medium entirely in the warm chamber 2 and expands during the first period 102 (of course approximately) isothermal, ie it is fed thermal energy. Once the isothermal expansion 102 is completed, the working medium is conveyed from the warm chamber 2 into the middle chamber 3 by compressing the partial working volume of the warm chamber 2 and expanding that of the middle chamber 3 at the same rate at the same time. The thermodynamic state of the working medium does not change during this time, i. despite a constant working volume V2, this transition does not constitute an isochronic change of state, because this process is to be understood as adiabatic due to the short duration of time and the embodiment of the middle chamber 3 already described. As soon as the working medium is conveyed completely into the middle chamber 3 and the partial working volume 114 of the warm chamber 2 is thus 29/56 30
    Zero, the isen-tropic expansion 103 or its period of time begins in the middle chamber 3, which runs much faster than the isothermal expansion 102, so that heat exchange is avoided as far as possible. As soon as the working medium has reached the maximum working volume V3, it is conveyed from the middle chamber 3 into the cold chamber 4, where then the isothermal compression 104 takes place and thermal energy from the working medium to the chamber 4 and in consequence the environment is released. Thereafter, the working medium changes again into the middle chamber 3, in which after the chamber change, the isentropic compression 105 takes place. After a renewed change of chamber back into the warm chamber 2, the next pass 113 begins. As can be seen from the course of the partial working volumes, at least either the partial working volume 114 of the warm chamber 2 or 115 of the cold chamber 4 is at any time Essentially zero. During the isentropic state changes 103, 105, even both partial working volumes 114, 115 are substantially zero. In addition, it can be seen from the graph in FIG. 11 that the two isotropic state changes 103, 105 require considerably less time than the two isothermal state changes 102, 104, with the isentropic expansion 103 simultaneously sweeping over the largest volume range and one of the smallest time segments the rate of volume change during isentropic expansion 103 is one of the largest. Furthermore, it can be seen from the diagram in FIG. 11 that the working volume is always essentially divided between the partial working volumes 114, 115, 116 of one or two chambers 2, 3, 4.
    The diagrams in FIGS. 12 to 14 show profiles of the partial working volumes of a piston engine with one or more piston arrangements, each with only two pistons. In the case of two chambers, in contrast to the operation of a 3-chamber machine shown in connection with FIG. 11, there can not be a separate piston for the isotropic state changes 103, 105. Since the isentropic state changes 103, 105 thus have to take place in a chamber 2, 4 which is subject to the process temperatures To, Tu and preferably heat transfer surfaces 34, 45, heat exchange can only take place over a maximum change in state 103, 105 be prevented. In addition, the working medium must of course be transported directly from the warm chamber into the cold chamber or vice versa.
    In the method according to FIG. 12, after the isothermal expansion 102, the isentropic expansion 103 still takes place in the warm chamber and the working medium is conveyed into the cold chamber 4 at a maximum volume V3 during a chamber change 117. There, the isothermal compression 104 is followed by the isentropic compression 105 before a chamber change 118 is completed back into the warm chamber. The chamber changes 117, 118 accordingly always follow an isentropic state change 103, 105.
    In contrast to FIG. 12, in a method according to FIG. 13, the chamber changes 117, 118 are performed before the isentropic state changes 103, 105. Consequently, the isentropic expansion 103 is already in the cold chamber 4 immediately before the isothermal compression 104 and after a chamber change 118 is followed by the isentropic compression 105 and immediately thereafter the next isothermal expansion 102 in the warm chamber. This method has the advantage that only the cold chamber has to hold the maximum volume V3 and the chamber cross-section can be adjusted accordingly. While in the previous methods and operating modes, the change of the working medium from one chamber to the next as a separate step - but without changing the thermodynamic state of the working medium - is performed, takes place in the method of FIG. 14, a change of chamber simultaneously with an isentropic state change. At the isothermal expansion 102, which naturally takes place in the warm chamber, immediately begins a compression of the warm chamber, which is accompanied by a much faster expansion of the cold chamber. The working volume is thus increased in total, which approximates an isentropic expansion at a correspondingly high speed.
    At the end of this combined chamber change 119, the isothermal compression 104 can begin immediately. Once completed, the second chamber change 120 is parallel to isentropic compression, i. the cold chamber significantly compresses 31/56 32 faster than the warm chamber expands. At the end of this process, the isentropically compressed working medium is already completely in the warm chamber. This method thus effectively manages with only four steps during a pass 113.
    Mixed forms of the methods illustrated in the diagrams of FIGS. 12 to 14 are also possible, which will not be discussed in greater detail because of their partial analogies to the methods already explained.
    The operation of a four-chamber piston engine according to the invention is finally shown schematically in FIG. 15 on the basis of the progressions of the partial working volumes. In this case, a separate chamber is provided for each of the isentropic expansion 103 and the isentropic compression 105. The working medium circulates in one direction through the four chambers (the warm chamber can be connected directly to the cold chamber via another connecting channel), each separate work steps for the thermodynamically static chamber changes 121, 122, 123, 124 are provided. The diagram shows the course of the partial working volume in the warm chamber 114, in the cold chamber 115 and in the isentropically expanding chamber 125 and the isentropically compressing chamber 126. If the isothermal compression 104 begins exactly at half of the working cycle 113 or the expansion part and the compression part of a run 113 take the same length, in such arrangements, two working volumes can work simultaneously in a chamber arrangement, the working volumes always in or between opposite chambers and the connecting channels would have to be equipped with valves. From a chamber arrangement with 6 chambers two or more working volumes are possible with even more chambers without valves.
    The illustrated and described embodiments may, of course, be modified or extended in the context of the invention in a professional manner. For example, instead of the external heat supply by means of a heating medium, an internal combustion can also be provided in one of the chambers, which can be adapted to the movement profile of the piston arranged in the warm chamber, for example by a time-variable quantity of the supplied fuel. Further possibilities of heat transfer to one of the pistons, e.g. Bundled sunlight or a flame directed from the outside onto a heat transfer body are likewise within the scope of what the person skilled in the art considers as use.
    For the sake of completeness, it should be mentioned that the time sequences of the partial working volumes shown in FIGS. 11 to 15, taking into account the respective piston area projected in the stroke direction, can be understood as temporal sequences of the piston positions within their chambers, which in turn corresponds to the movement profiles of the respective pistons , If a movement profile begins and ends in each case during a dead-phase section, these dead-phase sections together result in a dead-phase.
    The fields of use of the invention, i. The piston engine according to the invention and the method according to the invention are diverse. In particular, depending on the design and mode of operation of the reciprocating engine, uses may be made to drive a generator to generate electrical energy or to generate electrical energy directly by means of the motor-generator unit or any heat pump, e.g. for a family home or as a chiller for industrial applications, into consideration. 33/56
    权利要求:
    Claims (35)
    [1]
    A piston engine (1) for converting heat into work or for heating or cooling by the application of labor, comprising at least one chamber arrangement (8) which has at least two chambers (2, 3) connected by at least one connection channel (9, 10) , 3, 4), wherein at least two of the chambers (2, 4) are substantially thermally insulated from each other, and with in the respective chambers (2, 3, 4) movably arranged, for a working medium impermeable piston (5, 6, 7) for changing one of the chamber (2, 3, 4) and the piston (5, 6, 7) limited part-working volume, wherein at least one of the chambers (2, 4) heat transfer surfaces (34, 45) to increase their surface and wherein the pistons (5, 6, 7) or elements connected thereto are connected to actuating profiles for determining movement profiles for each of the pistons (5, 6, 7), characterized in that the actuating means for fixing at least two subscs different movement profiles of the piston (5, 6, 7) of the chamber assembly (8) are formed.
    [2]
    2. piston engine (1) according to claim 1, characterized in that at least two of the chambers (2, 4), the heat transfer surfaces (34, 45) to increase their surface area.
    [3]
    3. Piston engine (1) according to claim 1 or 2, characterized in that at least one of the actuating means fixed motion profiles has at least one dead phase, during which one of the associated with the corresponding actuating means connected to the piston (5, 6, 7) substantially stationary is.
    [4]
    4. piston machine (1) according to claim 3, characterized in that one of the in the dead phase of its movement profile located piston (5, 6, 7) and its associated chamber (2, 3, 4) limited part-working volume substantially zero is.
    [5]
    5. Piston engine (1) according to claim 3 or 4, characterized in that at least one of the motion profiles has different time intervals between a reversal point and the following dead phase on the one hand and between the dead phase and the temporal following reversal point on the other hand, in particular is directional.
    [6]
    6. piston engine (1) according to one of claims 1 to 5, characterized in that the actuating means of the chamber assembly (8) or the motion profiles defined by them are coordinated so that the consideration of a single working volume, which is substantially the Sum of its associated, inter-related partial working volumes is directed, in operation at least one of the chambers (2, 3, 4) and at most two of the chambers (2, 3, 4) has a substantially different from zero part-working volume or exhibit.
    [7]
    7. piston engine (1) according to one of claims 1 to 6, characterized in that the at least one connecting channel (9, 10) is valveless.
    [8]
    8. piston engine (1) according to one of claims 1 to 7, characterized in that the heat transfer surfaces (34, 45) of the chambers (2, 4) of the inner wall of the corresponding chamber (2, 4) are formed and in the corresponding chamber (2, 4) arranged piston (5, 7) has a to the heat transfer surfaces (34, 45) of the corresponding chamber (2, 4) complementary surface, which is preferably also formed for the transfer of heat.
    [9]
    9. piston engine (1) according to one of claims 1 to 8, characterized in that the heat transfer surfaces (34, 45) of one of the chambers (2, 4) with a garland-like heat transfer body (49, 53) are formed, which in the corresponding chamber (2, 4) or between the corresponding chamber (2, 4) and its associated piston (5, 7) is arranged.
    [10]
    10. piston engine (1) according to one of claims 1 to 9, characterized in that at least two of the chambers (2, 4) have different capacities and operating temperatures, in particular, the one chamber (4) with a relatively low operating temperature has a greater capacity than the other chamber (2) with a relatively high working temperature. 35/56 36
    [11]
    11. piston machine (1) according to one of claims 1 to 10, characterized in that the pistons (5, 6, 7) in their associated chamber (2, 3, 4) have an approximately equal lift capacity.
    [12]
    12. piston engine (1) according to one of claims 1 to 11, characterized in that at least one of the actuating means comprises a cam member, with which the actuating means associated piston (5, 6, 7) or with the piston (5, 6, 7) connected elements via a rolling element (17, 76) is or are.
    [13]
    13. piston machine (1) according to claim 12, characterized in that the rolling element (76) consists of at least two profile rollers (77, 78), wherein the at least two profile rollers (77, 78) due to their arrangement during a in the chamber assembly (8 ) executed cycle of a circular process with unchanged direction of rotation of their associated cam element does not change their directions of rotation.
    [14]
    14 piston machine (1) according to claim 12 or 13, characterized in that a determined in the stroke direction center distance between a guide roller (20) of the rolling elements (17, 76) and one of the profile rollers (22, 77, 78) of the same rolling element ( 17, 76) is small compared to a determined in the stroke direction distance between the axis of rotation of the profile roller (22, 77, 78) and the rolling element (17, 76) associated piston (5, 6, 7), preferably about zero, so that a possible frictionless movement of the rolling element associated piston is achieved in the chamber.
    [15]
    15. piston engine (1) according to one of claims 1 to 14, characterized in that at least one of the actuating means comprises a motor-generator unit (97) and the or the actuating means associated (n) piston (88, 89) or connected to the rotor of the motor-generator unit (97) is or are connected.
    [16]
    16. piston engine (1) according to claim 15, characterized in that at least one of the actuating means for generating va 36/56 37 movable movement profiles suitable, in particular freely programmable.
    [17]
    17. Piston engine (1) according to one of claims 1 to 16, characterized in that at least one of the actuating means and its associated piston (88, 89) a transmission gear (95), in particular a pantographartiges coupling gear, or a ball screw is interposed.
    [18]
    18. piston engine (1) according to one of claims 1 to 17, characterized in that the chamber arrangement (8) has three chambers (2, 3, 4), wherein the central chamber (3) through two of the connecting channels (9, 10) is connected to the other two chambers (2, 4) and the central chamber (3) is free of heat transfer surfaces to increase their surface and thermally at least one of the other chambers (2, 4), in particular at least one of the chambers (2) with relatively high working temperature, is isolated.
    [19]
    19. piston engine (1) according to claim 18, characterized in that the central chamber (3) has a greater capacity than the chamber (2) with a relatively high operating temperature.
    [20]
    20. piston engine (1) according to claim 18 or 19, characterized in that one of the chambers (2, 4) with the heat transfer surfaces (34, 45) made of a material having a relatively high heat capacity and good thermal conductivity, in particular copper or aluminum or their alloys, is produced and the middle chamber (3) is made of a thermally poorly conductive material, in particular ceramic or glass ceramic.
    [21]
    21. piston engine (1) according to one of claims 1 to 20, characterized in that one of the chamber assemblies (8) as a working medium having a gas with a high specific gas constant, in particular helium.
    [22]
    22. Piston engine according to one of claims 1 to 21, characterized in that at least one of the pistons (5, 6, 7) with a spring element, in particular a magnetic, mechanical or see 37-56 38 gaseous spring element to support the piston ( 5, 6, 7) associated actuating means.
    [23]
    23. Piston engine according to one of claims 1 to 22, characterized in that at least one further, substantially to the chamber assembly (8) identical chamber arrangement (79, 80) with piston (84, 85) is provided, wherein the mass inertia effects of the piston ( 83, 84, 85) together with associated elements of all chamber arrangements (8, 79, 80) substantially cancel.
    [24]
    24. Piston engine according to one of claims 1 to 23, characterized in that at least two different chamber arrangements (8, 79, 80) belonging to the piston (83, 84, 85) are connected to a common actuating means (82).
    [25]
    25. A method for operating a piston engine (1) having at least one chamber arrangement (8) with at least two, each in a chamber (2, 3, 4) arranged piston (5, 6, 7), in particular a piston machine (1) after a of claims 1 to 24, according to an approximate Carnot process with two isothermal and two isotropic state changes, characterized in that in the course of a run in the chamber assembly (8) run of the approximate Carnot process each of the involved in the flow piston (5, 6, 7) with respect to the passage at least once during a dead phase is substantially still, wherein one of the piston (5, 6, 7) and its associated chamber (2, 3, 4) limited part-working volume during the dead phase substantially Is zero.
    [26]
    26. The method according to claim 25, characterized in that a working volume of the chamber arrangement (8), which is essentially the sum of its associated, inter-related part-working volumes, at any time substantially to the associated therewith partial working volumes of one or two of the chambers (2, 3, 4) is distributed.
    [27]
    27. The method according to claim 25 or 26, characterized in that in terms of the passage, the duration of the dead phase of one of the piston (5, 6, 7) or in the piston (5, 6, 7) associated chamber (2, 3 , 4) is almost equal to or greater than the duration 38/56 39 of the time is at least partially overlapping with this dead phase, the passage associated with approximately isothermal state change in one of the other participating in the cycle chambers (2, 3, 4).
    [28]
    28. The method according to any one of claims 25 to 27, characterized in that within the chamber assembly (8) with respect to the passage each of the dead phases involved is at least 15%, in particular at least 25%, the time of passage.
    [29]
    29. The method according to any one of claims 25 to 28, characterized in that each of the pistons involved in the passage (5, 7) in one of their associated chambers (2, 4) with direct connection to exactly one of the other participating chambers ( 3) has a dead phase associated with the passage with respect to the passage.
    [30]
    30. The method according to any one of claims 25 to 28, characterized in that each of the pistons involved in the passage (5, 6, 7) in one of their associated chambers (2, 3, 4) with unidirectional by the participating working medium through -directed direct connection to exactly two other of the participating chambers (2, 3, 4) with respect to the passage exactly one pass associated dead phase.
    [31]
    31. The method according to any one of claims 25 to 28, characterized in that each of the pistons involved in the passage (6) in one of their associated chambers (3) by participating in the working medium bidirectionally flowed through direct connection to two other participating in it Chambers (2, 4) with respect to the passage has two dead pass associated with the passage.
    [32]
    32. The method according to any one of claims 25 to 31, characterized in that the total duration of all the pass associated dead phases of the piston (6), which participates in at least one of the involved in the pass approximately isentropic state changes (103, 105) is longer when the dead phase of the piston (5, 7) participates in the approximately isothermal state changes (102, 104) during one of the ann.
    [33]
    33. The method according to any one of claims 25 to 32, characterized in that in total the two approximately isentropic state changes (103, 105) of the run are performed faster, in particular at least 2 times faster than the sum total of the two associated with the pass approximately isothermal state changes ( 102, 104).
    [34]
    34. Method according to claim 25, characterized in that at least one thermodynamic state variable of one of the working media located in the chamber arrangement (8) is determined, and the time profile of one of the working volumes of at least one of the chamber arrangements (8), which essentially corresponds to Sum of its associated, inter-related partial work volumes is changed as a function of at least one determined state variable.
    [35]
    35. The method according to any one of claims 25 to 34, characterized in that at least one measured variable, in particular the position of one of the pistons (5, 6, 7) acting on one of the pistons (5, 6, 7) by the force Working medium or the available for the cycle process upper or lower process temperature is determined, which is related to a thermodynamic state variable of the in the chamber assembly (8) working media and the time course of one of the working volumes of at least one of the chamber assemblies (8), which in Substantially the sum of the associated, associated partial working volumes is changed as a function of the at least one determined measured variable. 40/56
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    同族专利:
    公开号 | 公开日
    US20160040623A1|2016-02-11|
    WO2014169311A3|2014-12-11|
    WO2014169311A2|2014-10-23|
    AT514226B1|2015-02-15|
    EP2986837A2|2016-02-24|
    EP2986837B1|2016-08-31|
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    法律状态:
    2018-12-15| MM01| Lapse because of not paying annual fees|Effective date: 20180416 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50261/2013A|AT514226B1|2013-04-16|2013-04-16|Piston engine and method for its operation|ATA50261/2013A| AT514226B1|2013-04-16|2013-04-16|Piston engine and method for its operation|
    US14/782,854| US20160040623A1|2013-04-16|2014-04-16|Piston machine and method for the operation thereof|
    EP14723684.8A| EP2986837B1|2013-04-16|2014-04-16|Piston machine and method for the operation thereof|
    PCT/AT2014/050094| WO2014169311A2|2013-04-16|2014-04-16|Piston machine and method for the operation thereof|
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