• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Piston machine (1) for converting heat into work or for heating or cooling by the application of work with a chamber (10), a working piston (6) and at least one displacer (7, 8), which separates the working medium from a region (11, 12, 13) of the chamber (10) to a further region (11, 12, 13) of the chamber (10) shifts, wherein at least two of the regions (11, 12, 13) have different temperature levels and the displacer piston (7, 8) is arranged between two adjacent ones of the regions (11, 12, 13), characterized in that two displacer pistons (7, 8) are arranged in the chamber (10) and the chamber (10) has three regions (11, 12, 13) ,
    公开号:AT520778A1
    申请号:T490/2017
    申请日:2017-12-20
    公开日:2019-07-15
    发明作者:Spiesberger Alfred
    申请人:Spiesberger Alfred；
    IPC主号:
    专利说明:

    Heat in work or for heating or cooling by using work with an internally tubular half-chamber with an at least partially closed end, with a working piston movably arranged in a cavity of the half-chamber, with at least a section of the half-chamber and at least a section of the working piston Chamber, which surrounds a cavity volume that is primarily variable in size by the working piston and that can be taken up by a working medium, the working piston being assigned a working actuating means that can interact with the working piston for movement of the working piston, with at least one enclosed by the working piston in the cavity of the half-chamber , Displacer piston movably arranged in the cavity of the half-chamber, which is likewise at least partially covered by the chamber and which repeats the working medium in an operating mode of the piston machine or shifts at least a portion of the working medium from one area of the chamber to a further area of the chamber, the chamber having at least these two areas and the areas each surrounding a portion of the cavity volume referred to below as area volume, and with at least one connecting channel for connecting at least two of the area volumes, wherein in the operating mode at least two of the areas have different temperature levels from each other and the areas of the chamber are characterized in that in the operating mode in the area volumes of two adjacent areas in each case different thermodynamic state changes of the working medium contained in the respective mode of the area volumes in the operating mode of an at least approximate thermodynamic cycle and wherein the displacer is essentially arranged between the area volumes of two adjacent areas and the Verd is a displacement actuator, which is capable of interacting with the displacement piston, for a movement of the displacement piston, and a method for operating a piston machine, in particular this piston machine.
    The most common and well-known piston machines for converting heat into work are automotive engines such as the diesel engine or the gasoline engine. The thermodynamic cycle underlying these machines is the diesel process, the Otto process or in general the Seiliger process. The preferred comparison process of the present invention, i. H.
    ]
    In contrast, that thermodynamic cycle, which the present invention preferably approximates, is the Carnot process, which is 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 circular processes mentioned above and, for example, the machines emulated by the Joul, Ericsen or Clausius-Rankine processes known in connection with turbomachines have an inherently suboptimal efficiency. An exception to this are Stirling engines, whose
    The comparison process is the Stirling process, since the use of a regenerator assumed to work perfectly would theoretically achieve the same efficiency as the Carnot process. However, this possibility has often proven to be disadvantageous because the regenerator never saves the stored heat during a work cycle, which is the movement sequence carried out by the relevant components of a piston machine for the unique sequence of the thermodynamic changes in state of the working medium, including any intermediate cycles or work steps, which characterize the cycle process can completely give up again and the regenerator itself creates large dead or damaged spaces.
    DE000002617971C2 shows a heat pump or a piston machine according to the Stirling principle with two pistons (working and displacement pistons) which can be moved separately in a container or a half-chamber, of which the first piston with the second piston has a compression space or an area volume of the working piston Displacement piston and the half-chamber, at least in sections, encompassing a region of at least a section comprising the working piston and half chamber, and the second piston with the container forming an expansion space or a further area volume of a further area of the chamber, at least in sections encompassing the displacer and the half-chamber, the latter two workspaces or areas one each
    Have heat exchangers and the gas respectively
    Working medium flows through a regenerator in the flow from the expansion space into the compression space and vice versa, and is arranged with areas in each of the two working spaces (compression and expansion space)
    Additional displacers or swirl discs, the drive of which occurs during the work process in the respective work area before or after the piston in question, so that the respective additional displacer or the respective swirl disk during the work process in question at least the gas volume or working medium located in the relevant work space or area volume of the area in question once through the associated, suitable openings
    3/37
    Presses the heat exchanger, but the working medium remains in the area volume of the respective area or in the respective area of the chamber and thus the swirl disk referred to as the additional displacer cannot be seen as a displacement piston in the sense of the present invention.
    It is found that the additional displacer mentioned from DE000002617971C2 optimizes the thermodynamic state change of a cycle process taking place in one of the work rooms and a displacement piston in the sense of the present invention shifts the working medium from one area to another area of the chamber where another state change of a cycle process is carried out or is approximated as in the previous area of the chamber,
    It should also be noted at this point that the areas of the chamber are distinguished in the sense of the present invention in that, in the operating mode in the area volumes of two adjacent areas in each case, different thermodynamic state changes in the working medium contained in the operating mode in the respective area volume of an at least approximate thermodynamic cycle are carried out, whereby two isothermal or isothermally approximated changes of state can nevertheless be different, for example when one isothermal change of state moves in the region of the upper and the other in the region of the lower process temperature of a thermodynamic cycle.
    A disadvantage of the machine described in DE000002617971C2 is that with the two working spaces (compression and expansion space) as the most effective cycle process for this machine, only the Stirling process can be approximated to a greater or lesser extent, and that in order to improve the efficiency somewhat, the regenerator mentioned The working gas has to flow through it, which creates harmful dead space and, in addition, considerable flow losses occur, which has a disadvantageous effect on the efficiency in both cases. Furthermore, it is disadvantageous that, in order to achieve an acceptable heat exchange with the working gas, a complex swirl mechanism, which in the area volume of the respective area of the chamber presses the working gas several times with each cycle through a heat exchanger that brakes the flow.
    The heat engine known from US Pat. No. 6,698,200 B1 is like a Stirling engine with a working piston comprising a cylinder and a piston that is movably arranged in the cylinder
    4/37
    Chamber, a displacer arranged movably in the cylinder, a regenerator, a hot and a cold region of the chamber and with the pistons operationally interacting actuating means, the actuating means being designed as cam disks. Due to the differently designed cam disks, different circular processes can be approximated.
    A disadvantage of the machine described in US Pat. No. 6,698,200 B1 is that the possibility of approximating different circular processes is severely restricted, since with the only two actuating means only two movement profiles are available for the two pistons, which means that, in addition to varying the cavity volume, the one in the cavity volume Working medium can be divided into only two areas of the chamber, also referred to below as chamber areas, in which state changes can be carried out.
    In particular, the implementation of an isentropic change of state is actually impossible, because due to the one heated and the other cooled chamber area during the desired change in state, heat transfer, in which the working medium absorbs heat, or heat transfer, in which the working medium releases heat, takes place, and entropy yes is transmitted together with heat. Even if the two chamber areas are kept at constant but different temperatures, a change in volume will result in a heat transfer in which the working medium absorbs or releases heat, since the thermal insulation mentioned in this machine does not exist between the working medium and the mentioned heat source or the mentioned Heat sink is arranged. Furthermore, the regenerator is located in the displacer piston, which, when it is flowed through by the working medium, exchanges heat with it and thus entropy in accordance with its purpose.
    In the machine known from EP000002986837B1, three actuating means for three working pistons are proposed.
    Furthermore, within a chamber arrangement, this machine has three chambers connected by means of connecting channels, each with only one chamber region. Each of the three chambers is essentially formed by a half-chamber and the previously mentioned working piston, which is impermeable to the working medium and is movably arranged in the half-chamber and closes the half-chamber. The working pistons of the machine known from EP000002986837B1 are acted upon with the full piston cross section by the pressure generated by the working medium.
    5/37
    In comparison to displacement pistons, working pistons have the primary task of varying the cavity volume of a chamber. On the other hand, the primary task of the displacement pistons is to push a working medium from one area of a chamber to another area of the chamber, but this does not necessarily mean that the entire working medium is shifted because a certain proportion of the working medium is in the Connection channels and / or any regenerators remains. Becomes a
    If the displacement piston is actuated by means of a piston rod penetrating the working piston, the movement of the displacement piston also changes the cavity volume of the chamber due to the piston rod immersing in the cavity of the chamber or emerging from the cavity of the chamber, this change in the cavity volume resulting from the change in the cavity volume is subordinate to the working piston. On the other hand, the area of the working piston which is acted upon by the working pressure caused by the working medium is reduced by the said piston rod connected to the displacement piston, which does not damage the primary tasks of the working piston and displacement piston. Due to the primary task of a working piston, this also transmits the largest part of the power exchanged with the working medium, whereby enormous resulting gas forces are exerted on the working piston and the actuating means interacting with the working piston.
    A disadvantage of the machine described in EP000002986837B1 is that all the actuating means interact exclusively with the working piston, as a result of which high forces and high rolling friction occur between the described rollers and cam disks and large losses are caused. The efficiency which is reduced as a result is now only in the order of magnitude of Stirling engines according to the prior art
    From DE000019534379A1 it is known that two displacer pistons or displacer plates and a working piston are arranged in a housing in order to remove the working gas provided in the individual chambers by the movement of the
    To bring displacement plates alternately only in contact with warm or cold chamber walls, the displacement plates moving in opposite directions in adjacent work cells, resulting in two separate displacement stacks.
    In construction and mode of operation, however, the thermodynamic machine described in DE000019534379A1 differs greatly from the machine disclosed here, since, for example, the machine described in DE000019534379A1 is absolutely essential for achieving the Carnot efficiency specified there
    6/37 requires a regenerator, which is evidenced, among other things, by the statement there that the amounts of heat involved during the isochoric changes in state are mutually compensated for. In addition, the Stirling cycle is striven for with the machine described there, whereas the machine disclosed here follows the Carnot cycle and not only does not require a regenerator, but this would even be detrimental to the efficiency. Furthermore, in the machine described there, it is impossible for the two displacement pistons to touch because a chamber wall is always arranged between them. In addition, the displacement pistons cannot move synchronously with one another, which additionally underlines the completely different functions of the machine described there and the machine disclosed here.
    As a further distinguishing feature, the design of the inner shape of the half-chamber or the housing there should also be mentioned. In the machine disclosed here, the half-chamber is tubular on the inside, whereas in the machine described in DE000019534379A1 at the point where the stroke ranges of displacers and
    Working piston come together, a substantial cross-sectional change is formed, which is why the housing disclosed in DE000019534379A1 is in no way tubular on the inside.
    An important advantage of the internally tubular half-chamber is that, with regard to the geometric specification, the section of the half-chamber traversed by the piston seal of the working piston or a comparable element can also be traversed by one of the displacer pistons or at least a section by one of the displacer pistons.
    If this important advantage is given, there is still a half-chamber which is tubular on the inside, even if the half-chamber is somewhat slightly conical on the inside and / or if the half-chamber is approximately slightly stepped on the inside, and / or if the half-chamber has approximately local bulges on the inside has, it also does not matter whether the half-chamber is closed at one end or not.
    The prime example of an internally tubular half-chamber is a purely cylindrical half-chamber on the inside, the cylinder shape not only meaning a circular cylinder shape, but the cylinder on which it is based can also have an oval base area, for example.
    7/37
    In any case, this important advantage gives the pistons the greatest possible freedom of movement. If, for example, the displacer piston can follow the working piston very closely into certain sections of the half-chamber during its stroke movement, it can be achieved that, for example, during the Carnot cycle, certain space between the displacer and working piston can be efficiently avoided during certain work cycles or phases. In the machine described in DE000019534379A1, it is not possible, but also not necessary, that a displacement piston can follow the working piston because the machine there has both a different mode of operation and a different construction than the machine disclosed here.
    It can be seen that the above-mentioned prior art machines are either not suitable for emulating the Carnot process, or that a good approximation of the Carnot process due to the high mechanical losses of the proposed design does not lead to a higher overall efficiency than that known from Stirling engines.
    Accordingly, it is an object of the present invention to provide a piston machine which can implement an approximately ideal Carnot process with good mechanical efficiency by reducing flow losses of the working medium as much as possible for the implementation of several different ones, particularly those required for the Carnot process , Changes in the state of the working medium are suitable, certain areas for optimal heat transfer, which can be low or high, for example, depending on the requirements - between the working medium and the surfaces that come into contact with it, mechanical losses are largely minimized and the ideal state changes of the Carnot process adapted movements of the pistons.
    This object is achieved in a piston machine of the type mentioned at the outset in that two displacement pistons are arranged in the cavity of the half-chamber, the two displacement pistons being referred to individually below as the first displacement piston and as the second displacement piston, the first displacement piston essentially between the at least partially closed end of the half-chamber and the second displacement piston and the second displacement piston are arranged essentially between the first displacement piston and the working piston, and that the chamber has three regions, which are referred to below as the first region, as the second region and as the third area can be designated.
    8/37
    As a result, the working medium can be shifted to several regions of the chamber which are adapted to the respective different changes in state, and it is possible for an isothermal change in state at the upper process temperature as well as for isentropic changes in state and for an isothermal change in state at the lower process temperature Requirements of the concerned
    State changes corresponding area are provided, the area volume of the first area essentially between the at least partially closed end of the half-chamber and the first
    Displacement piston extends and the first region comprises the first displacement piston at least in sections and the half-chamber at least in sections, and wherein the
    Area volume of the second area essentially extends between the first displacement piston and the second displacement piston and the second area comprises the first displacement piston at least in sections and the second displacement piston at least in sections and the half-chamber at least in sections and wherein the area volume of the third area essentially extends between the second displacement piston and the working piston and the third area comprises the second displacement piston at least in sections and the working piston at least in sections and the half chamber at least in sections.
    Accordingly, in a method of the type mentioned, in particular in a method for
    Operating a piston machine according to the invention, the object achieved in that two displacement pistons are arranged in the cavity of the half-chamber and the two displacement pistons and the working piston are moved such that both of the two displacement pistons and the working piston are essentially synchronous in the stroke direction during a synchronous phase run as well as during two partially synchronous phases, only one of the two displacement pistons runs essentially synchronously with the working piston in the stroke direction, and during an asynchronous phase each of the two displacement pistons runs essentially not synchronously with the working piston in the stroke direction, at least the four phases mentioned being repeated be carried out.
    In order to better approximate an isentropic change in state of the working medium in a certain area of the chamber than in another area of the chamber and also to achieve the important short flow paths of the working medium within the chamber, which are particularly adapted to the sequence of changes in state of a Carnot cycle
    9/37 to minimize undesired heat transfer between areas with different temperature levels, it is advantageous if the second area, due to its shape in the arithmetic mean, has a larger, in particular an at least 1.5 times larger distance between a point of a set of any number, according to a uniform distribution in its area volume distributed over a reference volume and its inner boundary than each of the other of the areas, the reference volume being the smaller of the two maximum area volumes achieved by the compared areas in the operating mode and the distance being the length The shortest connecting line is defined and the inner boundary of the area is defined by the physical inner surfaces of the area which limit the area volume and the virtual passage areas for the working medium into the connecting channels s neighboring of the areas, and in the case of different results obtained for this distance, which are influenced by the respective number of points in the set, the statistically most reliable result is used.
    In order to minimize undesired heat transport between areas with mutually different temperature levels, it is useful if an area for a change in state with a changing temperature of the working medium, for example an area for an isentropic change of state, is arranged between the two areas with mutually different temperature levels, because this means that in between placed area receives a moderate temperature level.
    In addition, it is expedient for the expansion and / or compression in the isentropic changes in state to be carried out quickly by rapid piston movements in comparison to the other changes in state, in order to minimize undesired heat transfer between the working medium and the second region.
    If, due to their designs, the displacer actuating means and the working actuating means at least define both a synchronous phase in which each of the two displacer pistons and the working piston run essentially synchronously in the stroke direction, and two partially synchronous phases in which only one of the two displacer pistons coexists the working piston runs essentially synchronously in the stroke direction, as well as an asynchronous phase in which each of the two displacement pistons is essentially not synchronized with the working piston in the stroke direction, with at least the four phases mentioned being carried out repeatedly, a predominant part can expediently of the working medium in a single area of the
    10/37
    Chamber are transported to carry out a change of state adapted to the area in each case.
    In order to carry out the working actuating means, which is exposed to the high load from the working piston, with as little friction as possible, and at the same time, highly dynamic movements of the
    To implement displacement pistons, it makes sense if the working actuation means are designed as a crankshaft and the displacer actuation means are designed as electromagnetic actuators including control units.
    Furthermore, it is advantageous if, due to the configurations of the working actuating means and the displacer actuating means in the operating mode of the piston machine during a cycle of the cycle, the maximum area volume reached by the second area is greater than the maximum area volume reached by one of the other areas, because this means that for the isentropic change of state, which is preferably carried out in the area volume of the second area, is required and in comparison to another of the areas larger volumes are available.
    For thermal protection of the sealing element of the
    It makes sense for the working piston if the area with the lowest of the mutually different temperature levels in the operating mode comprises the working piston at least in sections.
    Because it corresponds to the natural temperature profile from one to the other of the areas with different temperature levels and thus losses are minimized, it makes sense if three of the areas have different temperature levels in the operating mode, the temperature level of the second area between the temperature levels of the first area and The third area lies because at least a predominant portion of a heat output supplied to the piston engine in the operating mode is conducted into one of the areas with the most opposite temperature levels by appropriately arranged thermally conductive elements, and at least a predominant portion of a heat output given off by the piston engine in the operating mode is diverted away is guided by the other of the areas with the most opposite temperature levels, the K. with regard to the heat outputs supplied and given to the outside olbenmaschine can be seen as a thermodynamic system.
    11/37
    If the two approximately isentropic changes in the state of a Carnot cycle are carried out faster overall, in particular at least twice faster than the two approximately isothermal changes in state associated with the Carnot cycle, then advantageously enough time can be given to the heat transfer during the isothermal change of state, is counteracted during a change in entropy in the short time during the faster isentropic state changes.
    An adjustment of the stroke volume swept by the working piston in the operating mode of the piston machine by the working actuating means interacting with the working piston and an adaptation of the movement sequences of the displacer pistons by those interacting with the displacer pistons
    Displacement actuators can advantageously bring about a better adaptation to changing boundary conditions, such as the available heat output. This means that circular processes carried out one after the other can be different with regard to their state points.
    In order to allow escaping working medium to flow back into the cavity volume and / or to replace it, an overflow channel open to a working medium storage volume can be arranged in a certain position of the working piston.
    The present invention is explained in more detail below on the basis of particularly preferred exemplary embodiments, to which it is not restricted, however, and with reference to the drawings.
    The drawings show in detail:
    Figure 1 is a perspective view of a piston machine according to the invention with two displacement pistons, which are each coupled with rotatable cam tracks, and with a working piston, which is coupled to a crankshaft.
    FIG. 2 is a perspective side view of the piston machine shown in FIG. 1; and
    Fig. 3 is a qualitative diagram of the preferred movements in the stroke direction of the working piston and the displacer of the piston machine shown in Figs. 1 and 2.
    With the figures 1 to 3, a piston machine for
    Conversion of heat into work or for heating or cooling explained by expenditure of work, wherein the piston engine is described as an example as a heat engine according to an approximate Carnot cycle.
    Π
    12/37
    If the piston machine is viewed as a heat pump, the movement sequences and the heat flow are reversed, among other things, but the local temperature levels are essentially retained.
    In the following, for easier understanding, both certain individual parts or assemblies of the piston machine to be identified as well as certain sections of individual parts or assemblies of the piston machine to be identified as well as directional information with regard to their vertical position or direction corresponding to FIGS for example, "upper", "lower," middle, "upward and" downward "more precisely.
    The reference numerals used are neither as the exemplary character of those described
    Embodiments still to be regarded as restricting the embodiments themselves, and they are not to be understood as restricting the scope of the object or method protected by the claims; they only serve the purpose of making the explanations and claims easier to understand.
    The piston machine 1 shown in FIG. 1 has an internally tubular half-chamber 2, which on its closed end has serrations on the inside as heat transfer surfaces for maximum heat transfer.
    Outside, the half-chamber 2 also has heat transfer surfaces at its two ends, the heating fins 3 for heat absorption from the outside, that is to say from outside the thermodynamic system represented by the piston machine 1, and the cooling fins 4 for heat dissipation to the outside being provided at the top.
    It is favorable if the half-chamber 2 has a thermal insulation 5 in the section between these outer heat transfer surfaces, which can be applied to the outside and / or inside of the half-chamber 2, and / or if the half-chamber 2 in this section is made of a material with a poor quality Thermal conductivity and / or low heat capacity is made. The half-chamber 2 can also be made in several parts and / or have different materials in sections, for example in order to adapt to zones of different temperature levels.
    Both a working piston 6 and two displacement pistons 7, 8 are movably arranged in the half chamber 2, the working piston 6 enclosing the two displacement pistons 7, 8 in the half chamber 2. The working piston 6 has an annular groove in which a piston seal 9 is arranged. The
    13/37
    Working piston 6, the half-chamber 2 and the two
    Displacement pistons 7, 8 are essential components of a
    Chamber 10.
    The cavity formed by the chamber 10, which is intended for receiving the working medium required for the intended operation of the piston machine 1, represents the cavity volume of the chamber 10, the extent of which is varied primarily by the stroke movement of the working piston 6.
    Each of the displacement pistons 7, 8 divides the cavity volume of the chamber 10 into area volumes, and each of the area volumes is surrounded by a specific area II, 12, 13 of the chamber 10, the areas 11, 12, 13 of the chamber 10 being characterized in that in the operating mode in the area volumes of two adjacent areas 11, 12, 13 different thermodynamic state changes of the working medium contained in the operating mode in each of the area volumes of an at least approximate thermodynamic cyclic process are carried out, and furthermore the displacement pistons 7, 8 are characterized in that they The operating mode of the piston machine 1 repetitively moves the working medium or at least a portion of the working medium from one region 11, 12, 13 of the chamber 10 to another region 11, 12, 13 of the chamber 10.
    The machine shown here has three areas 11, 12, 13: In the state shown in FIG. 1, the upper area 11 has an area volume of approximately zero volume units and essentially comprises the jagged section of the upper displacer 7 and the upper section of the half-chamber 2 together with the closed, serrated end of the half chamber 2, the serrations of the upper displacer 7 and the inner serrations of the half chamber 2 being complementary.
    The central region 12 essentially comprises the flat section and the approximately central section of the half-chamber 2 of the two displacement pistons 7, 8 and is designed as the region in the region volume of which approximate isentropic changes in state of the working medium are preferably carried out.
    The lower region 13 essentially contains the upper serrations of the working piston 6, the serrated section of the lower displacer 8 and the lower section of the half-chamber 2. Each of the displacers 7, 8 can flow through and / or flow around the working medium via a connecting channel 14, 15 be, whereby the working medium during the movement of a displacement piston 7, 8 from the smaller
    14/37
    Area volume of an area 11, 12, 13 reaches the increasing area volume of another area 11, 12, 13, it being of secondary importance whether the respective connecting channel 14, 15, for example, in the displacement piston 7, 8 in question and / or in or on the half-chamber 2 is arranged.
    In one embodiment, the upper displacer piston 7 has, in its upper section, tines complementarily shaped to the inner tines of the half-chamber 2 as heat transfer surfaces for maximum heat transfer. In phases in which the upper displacement piston 7 has reached its top dead center, its prongs absorb heat from the inner prongs of the half-chamber 2 in order to subsequently apply it to it
    To deliver downward movement to the working medium. The interlocking and complementary serrations ensure that the relevant area volume is virtually zero
    Volume units can be reduced and that the surfaces forming the serrations differ only slightly from one another in relation to the stroke distance with respect to their perpendicular distances to their corresponding surfaces when the upper displacement piston 7 is directed downwards, as a result of which the working medium is always close to those formed by the serrations
    Heat transfer surfaces remain and therefore a particularly good one due to their very low thermal resistance
    Heat transfer between the teeth and the working medium can take place. In addition, the teeth provide the largest possible area for heat transfer. The upper region 11 is therefore designed, in particular in comparison to the central region 12, for isothermal changes in the state of the working medium.
    In the illustrated embodiment, the upper one
    Displacement piston 7 in its lower section as well as the upper section of the lower displacement piston 8 have a smooth, flat surface, which is a heat exchange with the
    Working medium severely limits, since the atoms or molecules of the working medium on average have a maximum distance from the inner boundary of the central region 12. The central region 12 is therefore designed, in particular in comparison to the upper region 11 and the lower region 13, for isentropic changes in the state of the working medium.
    The prongs of the lower displacer 8 and the prongs of the upper section of the working piston 6 function in principle in the same way as the inner prongs of the half-chamber 2 and the prongs of the upper displacer 7, whereby in phases in which the lower displacer 8 and the working piston 6 abut one another, a heat transfer between the teeth of the lower displacer 8 and the teeth of the upper
    15/37
    Section of the working piston 6 can take place. The lower region 13 is therefore likewise designed, in particular in comparison to the central region 12, for isothermal changes in the state of the working medium.
    In the embodiment shown, the working piston 6 additionally has jagged cooling fins 16 in its lower section, via which the piston machine 1 also emits heat to the outside.
    The jagged sections of the displacers 7, 8 and the working piston 6 can advantageously be made of a material with good thermal conductivity and / or high heat capacity, in particular aluminum, whereas the sections of the displacers 7, 8 with the smooth, flat surfaces are advantageously made of one Material with poor thermal conductivity and / or low heat capacity, for example made of cellular ceramic with closed porosity, can be produced.
    An axis 17 is connected to the working piston 6 at its lower end, a connecting rod eye of a connecting rod 18, 18a being rotatably mounted on both ends of this axis 17. A total of two connecting rods 18, 18a are arranged.
    Furthermore, the axle 17 is coupled on both sides at its end faces to a straight guide 19, which is not shown in FIG. 1, which is why the connecting rods 18,
    18a caused lateral forces are absorbed by the straight guide 19, whereby the piston raceway of the
    Working piston 6 and the working piston 6 themselves are relieved and also a rotation of the working piston 6 about its longitudinal axis is avoided.
    In the area of the piston seal 9, the working piston 6 has its running surface and its largest diameter, whereas the working piston 6 tapers slightly on both sides in the direction of its prong tips. The running surface of the working piston 6 is made very short, so that the piston play is sufficient to compensate for any inaccuracies in the alignment of the path of the straight guide 19 to the piston raceway, in that the working piston 6 thus constructed permits slight tilting movements. Such
    Compensation could also be provided, for example, by taking suitable degrees of freedom into account in the connection between the axis 17 and the working piston 6.
    To the displacement piston 7, 8 and the associated
    Piston rods 20, 21 in terms of their guidance no undesirable overdetermination is between the
    16/37
    Half chamber 2 and the displacer 7, 8 provided sufficient play.
    In the example shown in FIG. 1, the two displacement pistons 7, 8 are each rigidly connected to a piston rod 20, 21, a rolling element 22, 22a being attached to the ends of the piston rods 20, 21 facing away from the displacement pistons 7, 8, whose rollers 23, 23a, 23b, 23c in the groove-shaped, only in Fig. 2 with their
    Interfacing cam tracks 24, 25, 26, 27 of a rotatably mounted flywheel 28 engage.
    By means of the rolling elements 22, 22a and the piston rods 20, 21, during the operation of the piston machine 1 with a rotating flywheel 28, there are interactions between the cam tracks 24, 25, 26, 27 and the displacer pistons 7, 8, which result in different shapes Guide cam tracks 24, 25, 26, 27 derived movements of the displacers 7, 8. The
    Flywheel 28 is composed of two halves 29, 30, and a pair of mirror-image, groove-shaped cam tracks 24, 25, 26, 27, the cam tracks 24, 25, 26, 27 of a pair being arranged in different halves 29, 30 of the flywheel 28 , sets a motion sequence of a
    Displacement piston 7, 8 fixed. As is already common practice with the so-called free-piston Stirling machines, the displacement pistons 7, 8 in particular could also be actuated by electromagnetic actuators, as a result of which the piston rods 20, 21 together with the rolling elements 22, 22a would be dispensed with. In this case, it would be particularly advantageous that the displacement pistons 7, 8 and the inside of the half-chamber 2, viewed in the stroke direction, were oval and the
    Displacement pistons 7, 8 can be provided with a smaller piston clearance in the half-chamber 2, because twisting of the displacement pistons 7, 8 about their longitudinal axis can also be avoided in this way
    In the example of a piston machine 1 shown in FIG. 1, the piston rod 20 of the upper displacer piston 7 penetrates the lower displacer piston 8 and its tubular piston rod 21, whereby it makes sense to insert the piston rod 20 of the upper displacer piston 7 by means of balls of a recirculating ball guide which engage in longitudinal grooves to guide the piston rod 21 of the lower displacement piston 8, whereby reduced friction is achieved and twisting of the piston rods 20, 21 against one another is avoided.
    Furthermore, the piston rod 21 of the lower displacement piston 8, which is penetrated by the piston rod 20 of the upper displacement piston 7, penetrates the working piston 6, it also being advantageous here, analogously as described above, to one
    Ball recirculation guide to be provided, which becomes a problem
    17/37
    Interlocking of the jagged heat transfer surfaces leads.
    The two bushings of the piston rods 20, 21 are each sealed in a zone with a low local working temperature of the piston machine 1 by rod seals 31, 32.
    A crank pin 33, 33a is rigidly connected to each half 29, 30 of the flywheel 28, the crank pin 33, 33a being arranged coaxially. The lower connecting rod eyes of the two connecting rods 18, 18a are rotatably mounted on the crank pin 33, 33a. The crank pin 33, 33a are further rigidly connected at their ends opposite the flywheel 28 to a crank arm 34, 34a with a stub shaft 35, 35a. The stub shafts 35, 35a, the crank webs 34, 34a, the crank pins 33, 33a and the flywheel 28 having the cam tracks 24, 25, 26 essentially form a rigid crankshaft 36 which is rotatably mounted in a frame 37 and for mechanical work can be removed.
    The already mentioned straight guide 19, which is designed as an inverse of Peaucellier, is indicated in FIG. 2. Furthermore, the curved tracks 24, 25, 26, 27 provided as displacement actuating means are clearly visible. By means of the two connecting rods 18, 18a, during operation of the piston machine 1, there is an interaction between the crankshaft 36 provided as working actuating means in the embodiment shown and the working piston 6, which leads to the sinusoidal or sinusoidal movement of the working piston 6 and to the rotational movement of the rotationally inert Flywheel 28 comprehensive crankshaft 36 leads. The half-chamber 2 is not shown in FIG. 2 as a sectional view, as a result of which the heating fins 3 and cooling fins 4 arranged around the half-chamber 2 are clearly visible.
    3 shows a qualitative diagram 50 of the movement sequences of the three pistons (6, 7, 8) of the piston machine illustrated in FIGS. 1 and 2, namely the working piston 6 and the two displacement pistons 7, 8.
    Time is plotted on the abscissa axis 51; the
    Diagram curves 53, 54, 55 extend over the duration of a work cycle.
    The strokes, i.e. the paths in the stroke direction, of these three pistons (6, 7, 8) are plotted on the ordinate axis 52, a downward movement along a diagram curve 53, 54, 55 a downward movement and an upward movement along a diagram curve 53 , 54, 55 an upward movement of one shown in FIG. 1 or 2
    18/37
    Piston (6, 7, 8) means.
    The diagram curves 53, 54, 55 are also shifted along the ordinate axis 52 in such a way that sections of the diagram curves 53, 54 which are congruent or approximately congruent identify pistons (6, 7, 8) which are in contact or at least at a close distance. If, in addition, the diagram curve 54 corresponding to the upper displacement piston 7, which is shown in dashed lines, that is to say similarly to the national edition of the ISO 128-20 standard, is shown as a broken line, the
    The abscissa axis 51, that is to say the time axis, touches or runs along it, then the upper displacement piston 7 is in its uppermost position, which means that the upper region volume is zero or almost zero volume units.
    Correspondingly, the diagram curve 55 touching the time axis and corresponding to the lower displacement piston 8 and shown as a dash-dot line similar to the national edition of the standard ISO 128-20 means that both are
    Displacement pistons 7, 8 are in their uppermost positions, which means that the lower displacement piston 8 lies completely or almost against the upper displacement piston 7 located in its uppermost position, and the upper and middle area volumes are zero or almost zero volume units.
    The diagram curve 53 corresponding to the working piston 6 and shown as a solid line, thus similar to the national edition of the standard ISO 128-20 as a solid line, has a high due to the coupling of the working piston 6 with the
    Crankshaft 36 having moment of inertia has a sinusoidal or sinusoidal shape and shows that a minimum amount of the void volume is not undershot during the entire working cycle, since the diagram curve 53 for the working piston 6 never touches the time axis.
    The vertical distance between the graph curves 53, 54, 55 is a measure of the distance between the pistons (6, 7, 8} and can be interpreted as the extent of the area volume between the pistons (6, 7, 8).
    So essentially the upper area volume with the vertical distance between time axis and dash line, the middle area volume with the distance between dash line and dash-dotted line, the lower area volume with the distance between dash-dotted line and solid line and the void volume, apart from the volumes of
    Connection channels 14, 15, with the distance between the solid line and the time axis in relation. These considerations will
    19/37 makes it easier if one imagines temporarily that the pistons {6, 7, 8) have no extension or a length of zero length units in the stroke direction.
    The work cycle is divided into four temporal phases 56, 57,
    58, 59 and has, inter alia, four displacement cycles 60, 61, 62, 63 which shift the working medium from one to another of the regions 11, 12, 13. For the sake of simplicity, it should be stipulated that the working cycle is understood to begin with the beginning of one of the four phases 56, 57, 58, 59.
    The upper region 11 of the chamber 10 is heated from the outside during operation and has a relatively high temperature level which is customary for a heat engine. Due to the heat transfer, in particular the heat conduction, the inner teeth of the upper region 11 also have a high temperature level.
    At the beginning of the synchronous phase 56, which starts where the ordinate axis 52 intersects the abscissa axis 51, the working medium has approximately the smallest working volume during the passage of the Carnot cycle process approximated with the piston machine 1 and is located - as can be seen in FIG. 3 - essentially in the area volume of the upper area 11, which has hot and complementary jagged heat transfer surfaces facing its area volume. Smaller portions of the working medium are located in the connecting channels 14, 15, but this will not be discussed in more detail below.
    Because the working medium in the upper region 11 is constantly very close to the heat transfer surfaces during the expansion taking place in this synchronous phase 56, its temperature hardly changes. On the other hand, the working pressure drops. With this approximate isothermal expansion of the desired Carnot cycle, the two displacement pistons 7, 8 and the working piston 6 move downward in the stroke direction essentially synchronously; the working medium absorbs heat from the upper area 11.
    At the beginning of the partially synchronous phase 57, the upper phase changes
    Displacement piston 7 its direction of movement to then move upwards, whereby the working medium is displaced from the upper region 11 to the central region 12, the lower displacement piston 8 and the working piston 6 moving further downward.
    At the end of this displacement cycle 60, which is part of the partially synchronous phase 57, the upper displacement piston 7 is in its uppermost position, where it is initially
    20/37 remains, and the working medium, regardless of the proportions in the connecting channels 14, 15, in the area volume of the central area 12, which has no intentionally arranged heat transfer surfaces.
    During the expansion of the working medium taking place in this partially synchronous phase 57, heat transfer is largely prevented between the central region 12 and the working medium, as a result of which the entropy of the working medium remains approximately the same, the temperature of the working medium drops approximately to the lower process temperature and the working pressure continues, about to its lowest value, drops. During the partially synchronous phase 57, only one of the two displacement pistons 7, 8 moves essentially synchronously with the working piston 6 in the stroke direction.
    At the end of the partially synchronous phase 57, the approximate isentropic expansion of the desired Carnot cycle has essentially ended.
    At the very beginning of the asynchronous phase 58 takes place
    Displacement 61 instead, in which the lower
    Displacement piston 8 moves upwards after changing its direction until it rests against the upper displacement piston 7 and remains in this position until further notice. The working piston 6 meanwhile passes its bottom dead center, the void volume changing only insignificantly. After the displacement cycle 61, the working medium is now essentially in the area volume of the lower area 13, which also has complementary jagged heat transfer surfaces facing its area volume and a relatively low temperature level that is customary for a heat engine, because waste heat generated due to the heat transfer, in particular the heat conduction, is transported from the inner teeth of the lower region 13 to its cooling fins 4, where it is subsequently released to the outside.
    Because the working medium in the lower region 13 is constantly very close to the heat transfer surfaces during the compression taking place in this asynchronous phase 58 due to the upward movement of the working piston 6, its temperature hardly changes. On the other hand, the working pressure increases somewhat.
    Towards the end of the asynchronous phase 58, a displacement cycle 62 takes place again, in which the lower displacement piston 8 moves downward until it approaches the working piston 6 and bears against it. As a result, the working medium is moved back to the central region 12.
    21/37
    In the approximate isothermal compression of the desired Carnot cycle, which is essentially characterized by the asynchronous phase 58, each of the two displacement pistons 7, 8 essentially does not move synchronously with the working piston 6 in the stroke direction, and the working medium gives heat to the lower region 13 from.
    At the beginning of the partially synchronous phase 59, the working medium is located in the central area 12, which, as already explained, is optimized for an isentropic change of state. During the upward movement of the working piston 6 and the lower one applied to the working piston 6
    Displacement piston 8, the working medium is compressed approximately isentropically and thereby reaches about the upper process temperature, the minimum working volume and the highest working pressure during the working cycle.
    Towards the end of the partially synchronous phase 59, during the displacement cycle 63, the upper displacer 7 moves downwards until it ideally rests against the lower displacer 8, as a result of which the working medium is shifted back to the upper region 11.
    During the partially synchronous phase 59, only one of the two displacement pistons 7, 8 moves essentially synchronously with the working piston 6 in the stroke direction.
    At the end of the partially synchronous phase 59, the approximate isentropic compression of the desired Carnot cycle is essentially complete and the work cycle or cycle can begin again.
    It goes without saying that the entire working medium cannot always be equally involved in a change in state because, for example, a part of the working medium is also in the connecting channels and thus this part will not assume the same temperature as the rest of the working medium.
    Furthermore, it should be clarified that in practice a thermodynamic cycle process will not always appear as a result of sharply delimited, different thermodynamic changes in the state of a working medium because, for example, there are practically no sudden changes
    There are movements of the displacement pistons and the working medium has to be temporarily in two areas with different conditions for a change of state, which leads to overlaps
    State changes are coming. These circumstances, given only as examples, should not, however, damage the distinction between individual changes in state.
    22/37
    Furthermore, it goes without saying that, in practice, state changes can often only be approximated due to flow losses, which results in a deviation of the curves describing the ideal state changes from the curves describing the real state changes in corresponding diagrams, which is interpreted in accordance with the often idealized ones theoretical fundamentals of thermodynamics should not necessarily harm.
    The areas of application of the invention, i. H. the piston machine and the method according to the invention are diverse. In particular, depending on the design and operating mode of the piston machine, uses come as a drive for a generator for generating electrical energy or as a heat pump, e.g. B. for a family home, or as a chiller for industrial applications.
    23/37
    List of signs
    Koibenms machine 2nd Half chamber 3rd Helical ribs 4, 16 Cow 1 rip 5 thermal insulation 6 Piston 7, 8 Displacement baskets 9 Piston seal 10th chamber 11, 12, 13 Area 14, 15 Connection channels i 17th axis 18, 18a Connecting rod 18th Straight guidance 20, 21 Piston rod 22, 22a Roll element 23, 23a, 23b 23c Running route 1le 24, 25, 26, 27 Cam track 28 flywheel 29, 30 half 31, 32 Rod seal 33, 33a Pin Kurbe1 34, 34a Crank arm 35, 35a Wave stump 36 Spa commands 37 Gestei 1 50 diagram 51 Abs axis axis 52 Ordinate axis
    24/37
    ηΊ 54 55 Di agr arrro curve Οθ. 57, 58, 59 phase 60, 6 :, 62, 63 Displacement act
    25/37
    权利要求:
    Claims (8)
    [1]
    1. piston machine (1) for converting heat into work or for heating or cooling by applying work with an internally tubular and with an at least partially closed end formed half-chamber (2), with a movably arranged in a cavity of the half-chamber (2) Working piston (6), with a chamber (10) comprising at least sections of the half-chamber (2) and the working piston (6) at least in sections, which surrounds a cavity volume that is primarily variable in size and can be taken up by a working medium, whereby the working piston (6) the working piston (6) with the
    Working piston (6} is associated with interactive working actuating means for movement of the working piston (6), with at least one displacement piston (7, 8) enclosed by the working piston (6) in the cavity of the half-chamber (2) and movably arranged in the cavity of the half-chamber (2) ), which is also at least partially covered by the chamber (10) and which repeats the working medium or at least a portion of the working medium from one region (11, 12, 13) of the chamber (10) to one in an operating mode of the piston machine (1) displaces another area (11, 12 13} of the chamber (10), the chamber (10) having at least these two areas (11, 12, 13) and the areas (11, 12, 13) each referred to below as area volume Surround part of the cavity volume, and with at least one connecting channel (14, 15) for connecting at least two of the area volumes, with at least two of the areas (11, 12, 13} in the operating mode have different temperature levels and the areas (11, 12, 13) of the chamber (10) are characterized in that, in the operating mode, the area volumes of two adjacent areas (11, 12,
    13} different thermodynamic changes of state of the working medium contained in the operating mode in the respective of the area volumes of an at least approximate thermodynamic cycle are carried out and the displacement piston (7, 8) essentially between the area volumes of two adjacent areas (11,
    12, 13) is arranged and the displacer (7, 8) is provided with a displacer actuating means that can interact with the displacer (7, 8) for a movement of the displacer (7, 8).
    8} is assigned, characterized in that
    26/37 that two displacement pistons (7, 8) are arranged in the cavity of the half-chamber (2), the two displacement pistons (7, 8) being referred to below as the first displacement piston (7) and the second displacement piston (8) the first displacement piston (7) essentially between the at least partially closed end of the half-chamber (2) and the second displacement piston (8) and the second displacement piston (8) essentially between the first displacement piston (7) and the working piston (6 ) are arranged, and that the chamber (10) has three regions (11, 12, 13), which are referred to individually below as the first region (11), as the second region (12) and as the third region (13) , The area volume of the first area (11) extends essentially between the at least partially closed end of the half chamber (2) and the first displacement piston (7) and the first area (11) extends the first
    Displacement piston (7) at least in sections and the
    Half chamber (2) comprises at least in sections and the area volume of the second area (12) extends essentially between the first displacement piston (7) and the second displacement piston (8) and the second area (12) the first displacement piston (7) at least in sections and the second displacement piston (8) at least in sections and the half chamber (2) at least in sections and the area volume of the third area (13) extends essentially between the second displacement piston (8) and the working piston (6) and the third area ( 13) the second displacement piston (8) at least in sections and the working piston (6) at least in sections and the half-chamber (2) at least in sections.
    [2]
    2. Piston machine (1) according to claim 1, characterized in that the second region (12) due to its shape in the arithmetic mean a larger, in particular an at least 1.5 times larger distance between a point of an amount of any number, according to a uniform distribution in its area volume extended over a reference volume and its inner boundary than any of the other areas (11, 12, 13), the reference volume reaching the smaller of the two of the compared areas (11, 12, 13) in the operating mode is the maximum area volume and the distance is defined as the length of the shortest connecting line and the inner boundary of the area (11, 12, 13) is determined by the physical inner area that limits the area volume
    27/37
    Surfaces of the area (11, 12, 13) and from the virtual passage areas for the working medium into the connecting channels (14, 15) to the adjacent ones of the areas (11, 12, 13), and in the case of different results obtained for this distance, which are influenced by the respective number of points in the set, the most statistically reliable result is used.
    [3]
    3. Piston machine (1) according to claim 1 or 2, characterized in that the displacement actuating means and the. Working actuating means due to their configurations at least for defining both a synchronous phase (56) in which each of the two displacement pistons (7, 8th ) and the
    Working pistons (6) run essentially synchronously in the stroke direction, as well as two partially synchronous phases (57, 59), in each of which only one of the two displacement pistons (7, 8) runs essentially synchronously with the working piston (6) in the stroke direction, as well an asynchronous phase (58) in which each of the two displacement pistons (7, 8) runs essentially out of synchronization with the working piston (6) in the stroke direction, at least the four phases (56, 57, 58,
    59) are repeated.
    [4]
    4. Piston machine (1) according to one of claims 1 to 3, characterized in that the working actuating means are designed as a crankshaft (36) and the displacement actuating means as electromagnetic actuators including control units.
    [5]
    5. Piston machine (1) according to one of claims 1 to 4, characterized in that due to the configurations of the working actuating means and the displacement actuating means in the operating mode of the piston machine (1) during a cycle of the cycle the maximum area volume reached by the second area (12) is greater than the maximum area volume reached by one of the other areas (11, 12, 13).
    [6]
    6. Piston machine (1) according to one of claims 1 to 5, characterized in that the region (11, 12, 13) with the lowest of the mutually different temperature levels in the operating mode comprises the working piston (6) at least in sections.
    28/37
    [7]
    7. Piston machine (1} according to one of claims 1 to 6, characterized in that in the operating mode three of the areas (11, 12, 13) have different temperature levels from one another, the temperature level of the second area (12) between the temperature levels of the first area (11) and the third region (13), because at least a predominant portion of a heat output supplied to the piston engine (1) in the operating mode from the outside is conducted into one of the regions (11, 12, 13) with the most opposite temperature levels by correspondingly arranged thermally conductive elements and at least a predominant portion of a thermal output given off by the piston engine (1) in the operating mode is conducted away from the other of the regions (11, 12, 13) with the most opposite temperature levels, with regard to the external and external thermal outputs the piston engine (1) as a thermodynamic system see is.
    [8]
    8. A method, in particular for operating a piston machine (1) according to the preamble of claim 1, using a working piston (6) movably arranged in a cavity of a half chamber (2), in particular a half chamber (2) ), in particular a working piston (6) according to the preamble of claim 1, and at least one displacement piston (7, 8) enclosed by the working piston (6) in the cavity of the half-chamber (2) and movably arranged in the cavity, in particular a displacement piston (7 , 8) according to the preamble of claim 1, characterized in that two displacement pistons (7, 8) are arranged in the cavity of the half-chamber (2) and the two displacement pistons (7, 8) and the working piston (6) are moved in such a way, that both during a synchronous phase (56) each of the two displacement pistons (7, 8) and the working piston (6) run essentially synchronously in the stroke direction as well as during two partially synchronous oner phases (57, 59} each only one of the two displacement pistons (7, 8) with the working piston (6) runs essentially synchronously in the stroke direction and also during an asynchronous phase (58) each of the two displacement pistons (7, 8) with the Working piston (6) runs essentially out of synchronization in the stroke direction, at least the four phases (56, 57, 58, 59) mentioned being carried out repeatedly. ,
    Vienna, December 20, 2017
    类似技术:
    公开号 | 公开日 | 专利标题
    DE849326C|1952-09-15|Hot gas engine with more than one cycle
    DE2148842A1|1973-08-09|THERMAL ENGINE OR PUMP
    EP2986837B1|2016-08-31|Piston machine and method for the operation thereof
    DE112010004335B4|2019-11-14|Gamma-type free-piston Stirling engines configuration
    AT520778B1|2020-01-15|piston engine
    DE3049993T1|1982-03-18|CRYOGENIC APPARATUS
    WO2014187558A2|2014-11-27|Method and heat engine for utilising waste heat or geothermal heat
    EP3146190B1|2018-11-28|Two-cylinder stirling engine, multiple-cylinder stirling engine and electric energy generation system
    DE2055738A1|1971-05-19|Balanced free piston machine
    EP1509690B1|2005-10-05|Method and device for converting thermal energy into kinetic energy
    DE3408480A1|1985-09-12|HOT GAS ENGINE ACCORDING TO THE PRINCIPLE OF THE STIRLING ENGINE
    DE102009017493B4|2014-08-21|Heat engine
    DE202008010508U1|2008-10-09|Hot gas engine according to the Stirling principle
    DE102006028561B3|2008-02-14|Hydro-Stirling motor has two-cylinders linked by pipe with hydraulic motor power take-off
    DE102012107064B4|2014-05-22|Stirling engine
    DE3939779A1|1991-06-06|Heat-energy conversion process - uses fluids with low boiling point as working medium
    DE102020109743A1|2021-10-07|Method for operating a free-piston linear generator and a free-piston linear generator
    DE102009049870B3|2011-03-24|Thermal engine comprises two working chambers, and transfer port, which connects former working chamber with latter working chamber, where transfer port receives process gas, particularly carbon dioxide
    DE102011053146A1|2013-02-28|Heat engine for use in thermal power station, has heat chamber to heat working gas transmitted from compression chamber to expansion chamber, and cooler to cool working gas transmitted from expansion chamber to compression chamber
    DE19752996C2|1999-07-22|Regeneratorless Stirling engine
    DE102016117942A1|2018-03-29|Methods and apparatus for using thermal energy and creating temperature level differences
    DE102006050914A1|2008-04-30|Hot gas engine
    DE4123665C2|1993-04-29|
    DE4206958A1|1993-09-16|Refrigerator-heat=pump using Vuilleumier cycle - has two pistons inside pressure-tight cylinder with movement of piston rods controlled by electromagnets and springs
    DE102013227017B4|2015-07-16|Compressor device and method and apparatus for operating a left or right-handed circular process, in particular using such a compressor device
    同族专利:
    公开号 | 公开日
    AT520778B1|2020-01-15|
    DE102018132048A1|2019-06-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE19945679C1|1999-09-24|2000-11-30|Albert Koch|Thermodynamic machine uses at least three rotary pistons within stationary cylinder for cyclic transfer of light working gas to edge of cylinder head and from edge of cylinder head to center of cylinder head|
    DE2617971C2|1976-04-24|1983-05-26|Karlheinz Dipl.-Phys. Dr. 3300 Braunschweig Raetz|Heat pump based on the Stirling principle|
    DE19534379A1|1995-09-15|1997-03-20|Fraunhofer Ges Forschung|Stirling-type thermodynamic machine|
    US6698200B1|2001-05-11|2004-03-02|Cool Engines, Inc.|Efficiency thermodynamic engine|
    AT514226B1|2013-04-16|2015-02-15|Alfred Spiesberger|Piston engine and method for its operation|DE102020000141A1|2020-02-17|2021-08-19|Rudolf Placht|Circular groove crankshaft drive for reciprocating piston engines|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA490/2017A|AT520778B1|2017-12-20|2017-12-20|piston engine|ATA490/2017A| AT520778B1|2017-12-20|2017-12-20|piston engine|
    DE102018132048.5A| DE102018132048A1|2017-12-20|2018-12-13|piston engine|
    [返回顶部]