• 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:
    The invention proposes an active-chamber motor, comprising at least one piston (2) slidably mounted in a cylinder (1) and operating in a three-phase thermodynamic cycle comprising isobaric and isothermal transfer, polytropic expansion with work and an exhaust at ambient pressure, which is preferably supplied with compressed air contained in a high-pressure storage tank (12), in which the volume of the cylinder (1) swept by the piston is divided into an active chamber (CA) and a detent (CD), and in which the compressed air is used to move the intake valve (9) to open and then close the intake duct for supplying the active chamber of the engine, the compressed air used for these actions is then reused in the engine to produce additional work.
    公开号:FR3021347A1
    申请号:FR1454603
    申请日:2014-05-22
    公开日:2015-11-27
    发明作者:Guy Negre；Cyril Negre
    申请人:MDI Motor Development Internatiolal SA；
    IPC主号:
    专利说明:

    [0001] BACKGROUND OF THE INVENTION The invention relates to an engine operating in particular with compressed air, or any other gas, and using a chamber known as "air chamber". The invention relates to the distribution on admission of such an engine and more particularly for a motor comprising an active chamber included, and in particular for a multi-modal self-expanding motor with active chamber included. STATE OF THE ART The term "distribution" refers to all the means used to supply such a motor with compressed gas. The inventors have filed numerous patents concerning engines and their installations, using gases and more particularly compressed air for a completely clean operation in urban and suburban site: They have filed an international patent application WO-A1- 03/036088 to the content of which we will be able to refer, concerning a group motor-compressor - motorcycle - alternator with additional compressed air injection operating in mono-energy and in multi-energies. In these types of engines operating with compressed air and having a compressed air storage tank, it is necessary to relax the compressed air stored at very high pressure in the tank - but whose pressure decreases as and when as the tank empties - at a stable intermediate pressure called final pressure of use, in a buffer capacity - said working capacity - before its use in the engine cylinder or cylinders of the engine.
    [0002] To solve the problems of the expander, the inventors have also filed a patent application WO-A1-03 / 089764, the content of which we will be able to refer, concerning a dynamic variable flow regulator and a distribution for engines powered with injection of compressed air, comprising a high pressure compressed air tank and a working capacity. In the operation of these "load-relieving" motors, the filling of the expansion chamber always represents a relaxation without work which is detrimental to the overall efficiency of the machine. To solve the problem indicated above, the inventors then filed a patent application WO-A1-2005 / 049968 describing a compressed air motor powered preferentially by compressed air, or by any other compressed gas contained in a high-pressure storage tank, previously expanded to a nominal working pressure in a so-called working capacity buffer.
    [0003] In this type of engine according to the teachings of WO-A1-2005 / 049968: the expansion chamber is constituted by a variable volume equipped with means making it possible to produce a work, it is twinned and in contact by a permanent passage with the space above the main engine piston which is equipped with a piston stop device at its top dead center, - when the engine piston stops at its top dead center, the air or the gas under pressure is admitted into the expansion chamber when the latter is at its smallest volume and, under the pressure, will increase its volume producing a work, - the expansion chamber being maintained substantially at its maximum volume , the compressed air contained therein then relaxes in the engine cylinder thus pushing the engine piston in its downward stroke by providing in turn a work, - during the ascent of the engine piston during the exhaust time, the variable volume of the room of e xpansion is reduced to its smallest volume to start a complete work cycle again. The engine expansion chamber according to this invention actively participates in the work. The engine is thus called "active chamber" engine.
    [0004] The document WO-A1-2005 / 049968 teaches in particular a thermodynamic cycle in four phases during its operation in mono-energy mode with compressed air characterized by: - an isothermal expansion without work; - a transfer - slight relaxation with work said quasi-isothermal; - polytropic relaxation with work; an exhaust at ambient pressure.
    [0005] Document WO-A1-2008 / 028881, which presents a variant of the teachings of document WO-A1-2005 / 049968, teaches the same thermodynamic cycle, but using a traditional crank-rod device, the engine expansion chamber according to the invention actively participating in the work.
    [0006] The engines according to the teachings of documents WO-A1-2005 / 049968 and WO-A1-2008 / 028881 are referred to as "active-chamber motors". Subsequently, the inventors filed a patent application for an enclosed active chamber air or compressed-gas engine which uses the same thermodynamic cycle as the engines according to the teachings of WO-A1-2005 / 049968 and WO-A1-2005 / 049968. A1-2008 / 028881, as well as a conventional crank-and-crank device. According to the teachings of document WO-A1-2012 / 045693, the inventors have proposed an included active-chamber motor comprising at least one piston slidably mounted in a cylinder and driving a crankshaft by means of a conventional and working crank-rod device. according to a four-phase thermodynamic cycle comprising: an isothermal expansion without work; - a transfer - slight relaxation with work said quasi-isothermal; - polytropic relaxation with work; an exhaust at ambient pressure.
    [0007] Fueled preferably by compressed air, or any other compressed gas, contained in a high-pressure storage tank, through a so-called working capacity buffer which is fed with compressed air, or any other compressed gas, contained in a high-pressure storage tank, which is expanded to a mean pressure called working pressure in a working capacity preferably through a dynamic expansion device, in which: - the active chamber is included / incorporated in the engine cylinder ; - The engine cylinder comprises at least one piston slidably mounted in at least one cylinder whose volume swept by the piston is divided into two distinct parts, a first portion constituting the active chamber CA and a second portion constituting the expansion chamber CD; - The cylinder is closed at its upper part by a cylinder head having at least one duct and an intake port, and at least one duct and an exhaust port and which is arranged so that when the piston is at its top dead center, the residual volume between the piston and the cylinder head is, by construction, if not nonexistent, reduced to the minimum clearances allowing operation without contact between the piston and the cylinder head; compressed air or gas under pressure is admitted into the cylinder above the piston when the volume of the active chamber CA is at its smallest volume and which, under the continuous thrust of the compressed air at constant pressure of work, will increase its volume by producing a work representing the quasi-isothermal transfer phase; the admission of the compressed air, or pressurized gas, into the cylinder is closed when the maximum volume of the active chamber CA is reached, and the quantity of compressed air or gas under pressure, included in said active chamber then relaxes by pushing the piston on the second part of its stroke which determines the expansion chamber CD producing a job thus ensuring the relaxation phase; - The piston has reached its bottom dead point, the exhaust port is then open to ensure the exhaust phase during the ascent of the piston over its entire race. The volume of the active chamber CA included and the volume of the expansion chamber CD are dimensioned such that at the nominal operating pressure of the engine, the pressure at the end of expansion at low dead point is close to the ambient pressure, especially atmospheric. The volume of the active chamber is determined by the closing of the admission.
    [0008] Advantageously, and especially in mono-energy operation with compressed air, the active chamber motor included described above comprises a plurality of successive cylinders of increasing displacement. Preferably, the engine is fed, like the teachings of documents WO-A1-2005 / 049968 and WO-A1-2008 / 028881, by compressed air, or by any other compressed gas, contained in a storage tank. at high pressure, previously relaxed, at a nominal working pressure, in a buffer capacity - said working capacity.
    [0009] However, even if it is possible in the case of a multi-stage engine to feed the first of the cylinders at high pressures, it remains necessary to relax the compressed air at very high pressure contained in the high-pressure storage tank. up to a nominal working pressure and this expansion operation, either leads to a loss of efficiency by the use of a conventional expansion valve or, with the use of the teachings of WO-A1-03 / 089764, does not cost energy, but this relaxation does not allow to perform any work of relaxation between the high pressure contained in the tank and the nominal working pressure in the capacity of work at constant volume. The inventors then filed a new patent application WO-A1-2012 / 045694 to the content of which we will be able to refer who claims an active chamber compressed air motor included in which: - the high-pressure compressed air storage tank pressure, or any other gas under pressure, directly feeds the intake of the engine cylinder; the filling of the active chamber CA is effected at a constant intake pressure at each engine revolution, this intake pressure being degressive as the pressure in the storage tank decreases as and when measurement of the progressive emptying of this tank; the volume of the active chamber CA included is variable and is gradually increased as the pressure in the storage tank which determines said intake pressure decreases; the means for opening and closing the admission of compressed air into the active chamber CA not only make it possible to open the orifice and the intake duct substantially at the top dead center of the piston stroke, but they also make it possible to modify the duration and / or the angular sector of the admission, as well as the passage section of the opening; the volume of the active chamber CA included is dimensioned for the maximum storage pressure, then it is gradually increased so that, depending on the inlet pressure, the volume ratio between the active chamber CA included and the chamber relaxation CD, the pressure at the end of relaxation before the opening of the exhaust is close to atmospheric pressure. The engine according to WO-A1-2012 / 045694 also acts as a pressure reducer, the invention thus making it possible to propose an engine called "autodetendeur" which, for the supply of the active chamber CA, does not require any regulator independent of any one type. The multi-modal autodetender motor with active chamber included in accordance with the teachings of document WO-A1-2012 / 045694 notably implements, during its operation in single-energy compressed air mode, a three-phase thermodynamic cycle comprising: an isobaric transfer phase and isothermal - a polytropic relaxation phase with work - an exhaust phase at ambient pressure. In the operation of this engine, the volume, variable depending on the pressure of the high pressure storage tank, the active chamber included determines the amount of compressed air injected. The higher the inlet pressure, the smaller the volume of the active chamber must be. In order to obtain a correct operation in all phases of use of the engine, it is therefore necessary to feed it with great precision according to the various parameters including speed or rotational speed, the supply pressure, the load determined by the position of the accelerator, the temperature. For this purpose, it is necessary to be able to vary: - the moment of opening of the intake as a function of the rotational speed of the engine before or after the top dead center to take into account the inertia of the gases, but also the ratio between the pressure setting times, - the intake closing time, depending on the rotation speed of the engine, but also on the intake pressure, - the raising of the intake valve according to the desired charge. The difficulty lies in the realization of the means 15 for opening and closing the admission of the compressed air into the active chamber included, which not only allow opening of the orifice and the intake duct substantially at the top dead center of the piston stroke, but which also make it possible to modify the duration and / or the angular sector of the intake, as well as the passage section of the opening. The distribution of engines of all types is generally provided by valves whose operation is well known. A valve closes off the intake and / or exhaust duct and has a valve head held by springs resting on a circular valve seat formed around a port communicating the intake duct and or exhaust with the combustion chamber and / or expansion contained in the cylinder. The valve head opens the circuit by penetrating the feed chamber driven by mechanical cam and tappet systems acting on the valve stem or stem which extends the valve head. In other fields of motorization and for other technical reasons, particularly with regard to reducing pollution and in order to control the admission and exhaust of conventional combustion engines, a large number of engine manufacturers work on systems to control the phasing and duration of valve openings during operation and have filed numerous patents for these applications. Complex mechanical systems driven by electric stepper motors have also been developed and marketed, in particular by BMW (Registered Trademark) with the device called "Vamos". The inventors have also filed the patent application WO-A1-03 / 089764 to the content of which we can refer to a distribution by progressive control valve.
    [0010] Many works have been undertaken concerning electromechanical devices, in particular controlled by electromagnets easily controllable to take into account the various operating parameters, but the electrical powers to be implemented to allow acceleration and the speed of movement of the valves require, given the weight and inertia of the latter, considerable powers. The invention, particularly adapted to active chamber compressed air motors, including multi-modal self-expanding motors with active chamber included, proposes to solve all the problems mentioned above while providing additional power. The active intake distribution device according to the invention applied to the compressed air motors uses the compressed air contained in the high-pressure storage tank and / or in the intake circuit to move the intake valve in order to opening and closing the intake duct for supplying the active chamber of the engine, the compressed air used for these actions is then reused in the engine to produce additional work. BRIEF SUMMARY OF THE INVENTION The invention proposes an active chamber motor 35 operating according to a three-phase thermodynamic cycle comprising: an isobaric and isothermal transfer phase; - a polytropic relaxation phase with work; an exhaust phase at ambient pressure; this engine comprising: at least one cylinder fed with a gas under pressure, preferably with compressed air, contained in a high-pressure storage tank, at least one piston which is slidably mounted in this cylinder, a crankshaft; driven by the piston by means of a conventional crank-rod device, - a cylinder head which closes at its upper part the volume of the cylinder, which is swept by the piston, and which comprises at least one intake duct in which s' a flow of pressurized gas for filling the cylinder, an inlet for the gas under pressure above the piston, and at least one exhaust port and an exhaust duct, the cylinder head being arranged in such a way that when the piston is in its top dead position, the residual volume between the piston and the cylinder head is, by construction, reduced to the minimum clearances allowing the non-contact operation between the piston and the cylinder head, - at least an intake valve which cooperates sealingly with a valve seat formed in the cylinder head and which delimits the intake orifice, wherein: the volume of the cylinder swept by the piston is divided into two distinct parts, a first part constituting an active chamber which is included in the cylinder and a second part constituting an expansion chamber, - under the continuous thrust of the pressurized gas admitted into the cylinder, at constant working pressure, the volume of the active chamber increases by producing a work representing the isobaric and isothermal transfer phase, - the admission of the pressurized gas into the cylinder is closed as soon as the maximum volume of the active chamber is reached, the quantity of gas under pressure included in said chamber active then relaxing by pushing the piston on the second part of its course which determines the relaxation chamber by producing a job thus ensuring the phase polytropic relaxation, - the piston having reached its bottom dead point, the exhaust port is then open to ensure the exhaust phase during the ascent of the piston over its entire stroke to its top dead center, the engine torque and speed are controlled by the opening and closing of the intake valve allowing the intake valve to be opened, substantially at the top dead center of the piston stroke, and allowing, by closing the valve, changing the duration and / or the angular sector of the intake, as well as the passage section of the intake opening to, depending on the pressure of the compressed gas contained in the reservoir of storage and pressure at the end of the expansion phase, to determine the quantity of pressurized gas admitted and the volume of the active chamber, characterized in that: a) the inlet valve is mounted movably in axial displacement between a low closing position when it is sealingly resting on its valve seat, and a high opening position, - b) in the direction of its opening, the intake valve moves axially, in the opposite direction to that of the flow (c) in its closed position, the inlet valve 25 is kept autoclave closed on its valve seat by the pressure prevailing in the inlet duct and applying to the intake valve; d) the engine comprises means for controlling the opening of the intake valve, substantially at the top dead center of the piston stroke, to cause the valve to detach from the valve; admission of its seat to allow the establishment of the intake pressure in the active chamber, the valve then traversing its full opening stroke under the action of differential pressure forces exerted by the pressurized gas 35 on the corresponding parts d (e) the engine comprises a pneumatic cylinder for closing the intake valve which comprises a cylinder of cylinder and a closing piston which is connected in axial displacement with the intake valve, and is slidably mounted in the cylinder cylinder inside which it delimits in a sealed manner a control chamber of the jack, said closing chamber, - f) the motor comprises at least one valve opening control channel; an inlet which connects said closure chamber to a source of pressurized gas which is either the upper part of the active chamber of the cylinder, the inlet duct or the pressurized gas tank, g) the engine comprises a channel active dispensing device which connects said closing chamber to the upper part of the active chamber and a shut-off valve for the circulation of the gas in the active distribution channel, called the active dispensing valve, the opening of which is controlled to put the closure chamber in communication with the upper part of the active chamber, close the intake valve and produce a job which is added to the work of the previously admitted pressurized gas charge via the intake duct , in the active room. According to other characteristics of the invention: the active dispensing valve is controlled according to the following cycle: i) opening of the active dispensing valve to put the closure chamber in communication with the active chamber to cause the closure of the intake valve and, during the expansion phase, allow the expansion of the compressed gas, contained in the closure chamber, in the expansion chamber of the cylinder by producing a work which is added to the work of the load of pressurized gas previously admitted, via the intake duct, into the active chamber, ii) at the end of the expansion phase, closing again of the active dispensing valve to keep the pressure chamber inside the closure chamber expanded gas whose value is close to that of atmospheric pressure; said means (d) for controlling the opening of the intake valve comprise: (d) an inlet valve opening control channel which connects the upper part of the active chamber to the inlet duct or pressurized gas tank, - d2) and a controlled shutter valve 5 of the gas flow in the opening control channel, said opening valve; said opening control valve is controlled according to the following cycle: (k1) at the end of the exhaust phase, when the piston is substantially at the top dead center of its travel, opening of said valve, to allow to establish in the chamber activates a pressure identical to that prevailing in the intake duct and cause the detachment of the intake valve of its seat, 15 k2) the intake valve then travels its full opening stroke under the action of differential pressure forces exerted by the pressurized gas on the corresponding parts of the inlet valve, k3) closing of said valve as soon as the inlet valve opens; the engine comprises a channel which connects said closure chamber to the inlet duct and / or the pressurized gas tank, and a shut-off valve for the circulation of the gas in this channel, the opening and closing of which are controlled , to cause the closing of the inlet valve, prior to the communication of the closure chamber with the volume of the cylinder swept by the cylinder. said means for controlling the opening of the intake valve comprise a finger formed in relief on the upper face of the piston which, during the end of stroke of the piston towards its top dead point, acts through the intake port, on a portion facing the intake valve to take off its seat. the active dispensing valve is controlled according to the following cycle: j) opening of the active dispensing valve to put the closure chamber in communication with the active chamber to put the closure chamber in communication with the expansion chamber of the cylinder to allow expansion of the compressed gas, contained in the closure chamber, in the expansion chamber of the cylinder by producing a work which is added to the work of the pressurized gas charge previously admitted to the active chamber, jj) end of the expansion phase, closing again the active dispensing valve to maintain inside the closure chamber a pressure whose value is close to that of the atmospheric pressure; - The maximum open position of the intake valve is defined by an adjustable stop whose axial position, in the direction of movement of the intake valve, is controlled to vary the flow rate of pressurized gas admitted into the cylinder via the intake duct.
    [0011] BRIEF DESCRIPTION OF THE FIGURES Other objects, advantages and characteristics of the invention will become apparent on reading the nonlimiting description of several embodiments with reference to the appended drawings, in which: FIG. schematically a motor according to the invention, active chamber included in the cylinder, which is illustrated in axial section at its bottom dead point, and its device 25 for supplying compressed air; FIGS. 1B to 1D are views similar to that of FIG. 1A on which the motor is illustrated in different successive phases of operation of the motor according to the invention and in which FIG. 1B represents the motor in the course of admission, the intake valve having been opened from the top dead center; - Figure 2 is a view similar to that of Figure 1D which illustrates a second embodiment of an engine according to the invention; FIG. 3 is a view similar to that of FIG. 1B which illustrates a third embodiment of an engine according to the invention; - Figure 4 is a view similar to that of Figure 1D which illustrates a fourth embodiment of an engine according to the invention.
    [0012] DETAILED DESCRIPTION OF THE FIGURES Description of Figs. 1a-1d. Fig. 1A shows an active chamber self-expanding motor equipped with an active intake distribution assembly according to the invention. FIGS. 1A to 1D show an active chamber engine CA operating according to a three-phase thermodynamic cycle comprising: an isobaric and isothermal transfer; - polytropic relaxation with work; an exhaust at ambient pressure. The engine comprises at least one cylinder 1, only one of which is represented, which is fed with a gas under pressure, preferably with compressed air, contained in a high-pressure storage tank 12. The engine comprises a piston 2 which is slidably mounted in this cylinder 1, and a crankshaft 5 which is driven by the piston 2 by means of a conventional device crank-rod 3, 4. The volume of the engine cylinder 1 which is swept by the piston 2 is divided along an imaginary line DD '(corresponding to a plane of division orthogonal to the axis of the cylinder) into two parts: a first part constituting the active chamber CA, which is thus included in the cylinder 1, and a second portion 30 constituting the expansion chamber CD. The engine further comprises a cylinder head 6 which closes at its upper part the volume of the cylinder 1, which is swept by the piston 2. The cylinder head 6 comprises at least one intake duct 8 35 which is connected to the tank 12 and in which s flows the pressurized gas flow filling the cylinder, an inlet 7 for the pressurized gas above the piston 2.
    [0013] The cylinder head further comprises at least one exhaust port and one exhaust duct (not shown). The cylinder head 6 is arranged such that, when the piston 2 is at its top dead point, the residual volume between the piston 2 and the cylinder head 6 is, by construction, reduced to the minimum clearances allowing the operation without contact between the piston 2 and the cylinder head 6. The cylinder head 6 comprises at least one intake valve 9, one of which is illustrated, which cooperates sealingly with a valve seat 20 formed in the cylinder head 6 and which delimits the inlet orifice 7. In a known manner, in such an engine: the volume of the cylinder 1 swept by the piston 2 is divided into two distinct parts, a first portion constituting a chamber called active chamber CA which is included in the cylinder 1, and a second part constituting a CD expansion chamber, - under the continuous thrust of the pressurized gas admitted into the cylinder 1, at constant working pressure, the volume of the active chamber CA increases by producing a work representing the quasi-isothermal transfer phase, the admission of the pressurized gas into the cylinder 1 is closed as soon as the chosen maximum volume of the active chamber CA is reached, the quantity of gas under pressure included in the active chamber CA being relaxed then by pushing the piston 2 on the second part of its stroke which determines the expansion chamber CD producing a work thus ensuring the relaxation phase, - the piston 2 having reached its bottom dead point, the exhaust port 30 is then open to ensure the exhaust phase during the ascent of the piston 2 over its entire stroke to its top dead center, - the engine torque and speed are controlled by controlling the opening and closing of the intake valve 9 by opening the inlet valve 9, substantially at the top dead center of the piston stroke (vertically in the orientation of the figure), and allowing, by closing the valve 9 , to modify the duration and / or the angular sector of the intake, as well as the passage section of the intake opening in order, as a function of the pressure of the gas contained in the storage tank 12 and the pressure at the end of the detent, determine the amount of pressurized gas admitted as well as the volume of the active chamber CA. The intake duct 8 is directly connected to the high pressure reservoir 12 which directly supplies the active chamber CA and is at the same pressure as that of the reservoir. The pressure in the intake duct 8 is identical to that of the storage tank 12, for example of the order of 100 bars, and is greater than that prevailing in the active chamber CA and the expansion chamber CD, for example equal to 1.5 bar at the moment of the cycle corresponding to the bottom dead center of the piston, at the end of expansion, just before the opening of the exhaust valve. According to the invention, the intake valve 9 is mounted to move axially between a low position (considering the general vertical orientation of the figures and without reference to earth gravity) closing - shown in Figure 1A - in which it is in sealing engagement on its valve seat 20, and a high opening position - shown in FIG. 1 B. In the direction of its opening, the intake valve 9 moves axially - upwards, in the opposite direction to that of the flow of the flow F of pressurized cylinder filling gas. Thus, the inlet valve opens in the opposite direction to the flow of air under pressure filling the engine cylinder. In its closed position, the inlet valve 9 is held closed autoclave on its valve seat 20 by the pressure in the intake duct 8 and applied to the intake valve, that is, that is to say on the head of the valve inside the intake duct 8. The engine comprises means for controlling the opening of the intake valve 9, substantially at the top dead center of the piston stroke, to cause the detachment of the intake valve 9 of its seat 20 and allow to establish in the active chamber a pressure to that prevailing in the intake duct 8. During its opening phase, the valve then traverses its complete opening stroke under the action of differential pressure forces exerted by the gas under pressure on the corresponding parts of the intake valve and in particular on the valve head, that is to say on the one hand on the lower surface 22 disc-shaped subject to the pre ssion prevailing in the cylinder 1, and secondly on the upper surface 24 subjected to the pressure prevailing in the intake duct 8, the difference between the areas of these two surfaces substantially corresponding to the area of the section of the stem or tail 26 of the valve 9. In its closed position, the inlet valve 9 is held on its seat 20, autoclave by the pressure of the compressed air contained in the intake circuit, and / or in the storage tank 12 of the compressed air, the pressure in the active chamber CA and the expansion chamber CD of the engine being lower during the expansion and exhaust phases of operation. The engine comprises a pneumatic cylinder V closing the intake valve 9 which, by way of non-limiting example, is here arranged in the cylinder head 6. The cylinder V comprises a cylinder cylinder 100 and a closing piston 102 which is connected in axial displacement with the rod 26 of the intake valve 9, and which is slidably mounted in the cylinder cylinder 100 within which it delimits in a sealed manner an upper chamber 104 of the cylinder, called the closing chamber of the valve 9.
    [0014] The motor comprises an active distribution channel X1 which connects the closing chamber 104 to the upper part of the active chamber CA arranged included in the cylinder 1. The maximum maximum opening position of the intake valve 9 is defined by a adjustable stop 30 which extends in the chamber 104 and whose axial position, in the axial direction of displacement of the valve, is controlled (by means not shown in the figures) to vary the flow rate of pressurized gas admitted into the cylinder via the intake duct. The controlled adjustable stop thus acts as a "throttle" controlled by an accelerator. The displacements of the abutment are for example controlled and caused by means of an electric motor step by step.
    [0015] The adjustable stop 30 makes it possible to stop the upward and automatic upward movement of the intake valve 9 by modifying its lift as a function of the required motor operating parameters. The engine comprises a controlled valve Y closing the flow of gas in the channel X1 active distribution, called Y valve active distribution, whose opening can be controlled to put the chamber 104, closing the intake, in communication with the upper part of the active chamber CA by establishing in the closure chamber 104 a complementary pressure on the upper face of the piston 102 by pushing, by the action of this piston, the intake valve 9 on its seat 20 and thus closing the intake circuit thereby ending the work of the active chamber CA.
    [0016] The active dispensing valve Y is then kept open during the expansion time by allowing the compressed gas contained in the closure chamber 104 to relax together with the gas contained in the expansion chamber, while producing a work which is added in the work of the pressure gas charge previously admitted, via the intake duct, into the active chamber. The engine comprises an X2 channel for controlling the opening of the intake valve 9 which connects the upper part of the active chamber CA to the intake duct 8.
    [0017] The engine comprises a valve Z controlled shutter of the flow of gas in the channel X2, called valve opening of the intake valve, whose opening can be controlled to put the upper part of the active chamber CA in communication with the intake duct 8.
    [0018] When the piston 2 of the engine is close to its top dead point (Figure 1 B), by opening the opening valve Z, the intake circuit is, at the chosen moment, placed in communication with the active chamber CA of the cylinder by allowing the establishment of a pressure identical to that contained in the intake circuit and, because of the difference in areas mentioned above, the pressure, automatically pushes the inlet valve 9 upwards and the valve intake, in its movement, opens the intake circuit. For example, for a valve with a diameter of 20 mm controlled by a 6 mm valve stem, the bottom surface is 3.14 cm2 and the top surface is 2.86 cm2 (3.14 - 0 , 28), a thrust of 28 kg is exerted to automatically open the inlet valve 9 and allow the filling of the active chamber CA. The closing of the intake valve 9 is then ensured by placing the active chamber CA in communication with the closure chamber 104 thus creating a complementary pressure on the upper surface of the piston 102 of the closing cylinder V, which then pushes the valve intake 9 on its seat 20 and closes / closes the admission to allow the relaxation cycle of the active chamber CA in the relaxation room CD ..
    [0019] From the beginning of the expansion (Figure 1 C) the volume of the closure chamber 104 is maintained in communication with the expansion chamber CD of the engine and the compressed air contained in the closure chamber 104 is expanded in the expansion chamber CD engine producing a job that is added to the work of relaxation of the load allowed in the active room. Thus, within the meaning of the invention, the valve Y is an active dispensing valve, and the channel X1 is an active distribution channel. At the end of relaxation, the communication between the active chamber and the expansion chamber of the cylinder and the closure chamber 104 is again sealed by maintaining in the latter a pressure close to atmospheric pressure, allowing the renewal of the cycle. The operation of the so-called active distribution according to the invention is therefore understood in which, advantageously, the energy necessary for the opening and closing of the inlet valve 9 is provided by the pressure prevailing in the storage tank and or the intake circuit for opening, and prevailing in the active chamber for closure, then is reused by producing additional work in the cylinder. The volume of the closure chamber 104 is of reduced value, for example, without limitation, less than 10% of the cylinder capacity of the cylinder 1. The same applies to the channels connecting the inlet and the active chamber, and the closing chamber 104 to the CD relaxation chamber, whose passage sections are calculated to allow sufficient flow for the establishment of pressures in the different rooms. These various channels have reduced diameters for example of the order of 0.5 to 2 millimeters for a diameter of the main intake duct of the order of 20 millimeters.
    [0020] Preferably, Y and Z valves of the electromechanical type, constituted especially in the form of solenoid valves adapted and easily controllable by an electronic management unit (not shown), will be used. In addition, the control by electronic management and pneumatic control allows opening and closing speeds of the valve (s) and control angular phases of high precision. In the operating cycle of the active distribution described above, the expansion of the volume of air contained in the closure chamber is carried out in conjunction with that of the active chamber, and with pressure drops ranging from nominal pressure to exhaust pressure. Description of Figure 2 The following description is made by comparison with the embodiment previously described with reference to Figures 1A-1D. The previous design is completed by an additional channel X3 which connects the intake duct 8 to the closing chamber 104 of the cylinder V. The engine also comprises a valve T controlled closing the flow of gas, air compressed, in the X3 channel, whose opening can be controlled to put the intake duct 8 and / or the tank 12 in communication with the closure chamber 104. Thus, the closure chamber 104 has at least two conduits, X3 and X1 each provided with controlled closure means, T and Y, for putting the closure chamber 104, successively in communication with on the one hand with the intake circuit and / or the high storage tank pressure 12, and secondly with the active and relaxing chamber of the cylinder. Closing of the inlet valve 9 is ensured by placing the intake circuit and / or the storage tank in communication with the closure chamber 104, via the channel X3, and by controlling the opening of the valve T, thereby creating a complementary pressure on the surface of the closing piston 102 which pushes the intake valve 9 back onto its seat 20 and closes the inlet to allow the expansion cycle of the active chamber CA in the expansion chamber CD . Thus, the active relaxation of the closure chamber 104 can be delayed to intervene later in the cycle, by controlling the opening of the valve Y. From the beginning of the relaxation, or during relaxation, the volume of the chamber closure 104 is put into communication with the expansion chamber CD and the compressed air contained in the closure chamber 104 expands in the expansion chamber CD producing a work that is added to the work of relaxation of the load admitted in the active chamber CA. Substantially at the end of expansion, the communication between the active and expansion chamber of the engine and the closure chamber 104 is again sealed by maintaining in the latter a pressure close to atmospheric pressure allowing renewal of the cycle. Description of Figure 3
    [0021] The following description is made by comparison with the first embodiment illustrated in FIGS. 1A to 1 D.
    [0022] According to this embodiment, there are provided mechanical means for causing the release of the intake valve 9 of its seat 20, which act directly on the head of the intake valve 9.
    [0023] In the case of an engine having to operate at substantially constant speeds of rotation, and which therefore does not require variations in the timing of the opening of the intake, the opening of the intake valve 9 is advantageously simplified by the integration of such a mechanical device.
    [0024] For this purpose, said means for controlling the opening of the intake valve 9, are constituted by a finger D, or pusher, which is formed in relief on the upper face of the piston (2) and which extends vertically upwards opposite the head facing the intake valve 9.
    [0025] By its arrangement and its dimensioning, the opening control finger D is able to cooperate mechanically with the lower face 20 of the head of the intake valve 9 to push the latter vertically upwards. It is during the end of stroke of the piston towards its top dead center, that the finger D acts, through the inlet orifice, on the portion facing the lower face 22 of the head of the piston. intake valve 9 to lift it off its seat. The finger D is positioned in line with the lower part of the intake valve head so that it slightly raises the intake valve creating a leak which puts the intake circuit in communication with the active chamber. CA by establishing in the closure chamber 104 a complementary pressure on the upper surface of the piston 102 and, by the action of the piston 102 connected to the tail of the valve, by pushing the intake valve 9 on its seat 20 by closing thus the intake circuit by putting an end to the work of the active chamber CA. The valve then travels its full opening stroke under the action of the differential pressure forces exerted by the pressurized gas on the corresponding parts of the intake valve 9. After opening the inlet valve, and beginning of the relaxation cycle, because of the descent of the piston 2, the finger D no longer acts on the intake valve 9, and the continuation of the cycle is identical to that described with reference to Figures 1A to 1 D, using the valve Y.
    [0026] Description of FIG. 4 The following description is made by comparison with the second embodiment illustrated in FIG. 2. The arrangement of the channel X2 and the associated valve Z controlling the opening of the intake valve is modified. . The jack V is a double-acting cylinder with two sealed chambers separated by the piston 102. The lower chamber 105 is a control chamber opening the inlet valve 9 which, via the channel X2, is connected to the duct. inlet 8 and / or tank 12 of gas under pressure. Thus, the closure chamber 104 has at least two ducts, X3 and X1, each provided with controlled shutter means T, Y for putting the closure chamber 104 in succession in communication with the circuit on the one hand. inlet and / or the high-pressure storage tank 12, and secondly with the active and expansion chamber of the cylinder. The opening of the intake valve 9 is controlled by the valve Z which supplies pressurized gas to the lower chamber 105 of the cylinder V which is an opening chamber. Closing of the inlet valve 9 is ensured by placing the intake circuit and / or the storage tank in communication with the closure chamber 104, via the channel X3 and by controlling the opening of the valve T , thus creating a complementary pressure on the surface of the closing piston 102 which pushes the intake valve 9 on its seat 20 and closes the inlet to allow the expansion cycle of the active chamber CA in the expansion chamber CD .
    [0027] The closure is obtained because of the area of the piston 102 subjected to the pressure, which is greater on the side of the chamber 104, than on the opening chamber 105 side (the difference corresponding substantially to the area of the section of the rod of the intake valve). Thus, the active relaxation of the closure chamber can be delayed to intervene later in the cycle, by controlling the opening of the valve Y. From the beginning of the relaxation, or during relaxation, the volume of the chamber closure 104 is then placed in communication with the expansion chamber CD and the compressed air contained in the closure chamber 104 expands in the expansion chamber producing a work which is added to the work of relaxation of the load admitted into the active room. Substantially at the end of the expansion, the communication between the active and expansion chamber of the engine and the closure chamber 104 is closed again, while maintaining a pressure close to atmospheric pressure in the latter, allowing the cycle to be renewed. According to this design, the piston 102 of the cylinder V successively controls the opening and closing of the intake valve 9. According to a variant, not shown, it is possible, as for the chamber 104, to connect the chamber 105 to the active chamber through a channel X1 'and a valve Y', thus achieving two parallel active distribution circuits. The volumes of the closure chamber 104 and the opening chamber 105 can then be brought into communication with the expansion chamber and the compressed air contained therein is expanded in the expansion chamber to increase the work of relaxation of the load admitted by relaxing in the main engine cylinder. Because of the flexibility of use and the almost unlimited adjustment possibilities, the engine equipped with the "active" intake distribution according to the invention can be used on all land, sea, rail and aeronautical vehicles. The active chamber motor according to the invention can also and advantageously find its application in emergency generator sets, as well as in many domestic cogeneration applications producing electricity, heating and air conditioning.
    [0028] The active chamber motor according to the invention has been described with operation with compressed air. However, it can use any compressed gas / gas at high pressure, without departing from the scope of the claimed invention.
    [0029] The invention is not limited to the embodiments described and shown: the materials, the control means, the devices described may vary within the limit of equivalents, to produce the same results. The number of engine cylinders, their displacements, the maximum volume of the active chamber relative to the displaced volume of the cylinder (s) and the number of expansion stages, can vary.
    权利要求:
    Claims (8)
    [0001]
    REVENDICATIONS1. Active chamber engine operating on a three-phase thermodynamic cycle comprising: - an isobaric and isothermal transfer phase; - a polytropic relaxation phase with work; an exhaust phase at ambient pressure; this engine comprising: at least one cylinder (1) supplied with a gas under pressure, preferably with compressed air, contained in a high pressure storage tank (12), at least one piston (2) which is slidably mounted in this cylinder (1), - a crankshaft (5) driven by the piston by means of a conventional crank-rod device (3,4), - a cylinder head (6) which closes the volume of the cylinder (1), which is swept by the piston (2), and which comprises at least one intake duct (8) in which flows a flow of pressurized cylinder filling gas, an intake port ( 7) gas under pressure above the piston, and at least one exhaust port and an exhaust pipe, the cylinder head being arranged such that when the piston (2) is at its top dead center, the residual volume between the piston (2) and the cylinder head (6) is, by construction, reduced to the minimum clearances allowing the without contact between the piston (2) and the cylinder head (6), - at least one intake valve (9) which cooperates sealingly with a valve seat (20) formed in the cylinder head (6) and which delimits the intake port (7), in which engine: - the volume of the cylinder (1) swept by the piston (2) is divided into two distinct parts including a first portion constituting an active chamber (CA) which is included in the cylinder (1) and a second part forming an expansion chamber (CD), - under the continuous thrust of the pressurized gas admitted into the cylinder, at constant working pressure, the volume of the active chamber (CA) increases by producing a work representing the isobaric and isothermal transfer phase, - the admission of the gas under pressure into the cylinder (1) is closed as soon as the maximum volume of the active chamber (CA) is reached, the quantity of gas under pressure included in said active chamber (CA) then relaxing while pushing the piston (2) on the second part of its course which determines the expansion chamber (CD) by producing a work thus ensuring the polytropic relaxation phase, - the piston (2) having reached its low dead point, the orifice of exhaust is then opened to ensure the exhaust phase (7) during the ascent of the piston over its entire stroke to its top dead center, - the torque and engine speed are controlled by the opening and the closing the inlet valve (9) allowing the inlet valve (9) to be opened, substantially at the top dead point of the piston stroke, and allowing, by closing the valve (9), to altering the duration and / or the angular sector of the intake, as well as the passage section of the intake opening, as a function of the pressure of the compressed gas contained in the storage tank (12) and the pressure at the end of the expansion phase, to determine the quantity of pressurized gas admitted as well as the volum e of the active chamber (CA), characterized in that: - a) the inlet valve (9) is movably mounted in axial displacement between a low closing position in which it is in sealing engagement with its valve seat (20), and a high opening position, - b) in the direction of its opening, the inlet valve (9) moves axially, in the opposite direction to that of the flow of the gas stream under filling pressure of the cylinder (1), - c) in its closed position, the inlet valve (9) is held autoclave closed on its valve seat by the pressure in the intake duct (8) 35 and applying to the intake valve, d) the engine comprises means for controlling the opening of the intake valve (9), substantially at the top dead center of the piston stroke, to cause the detachment of the intake valve (9) from its seat to allow the establishment of the intake pressure in the seat active chamber (CA), the valve then traversing its full opening stroke under the action of the differential pressure forces exerted by the pressurized gas on the corresponding parts of the intake valve, e) the engine comprises a cylinder pneumatic closure of the intake valve (9) which comprises a cylinder of cylinder (100) and a closing piston (102) which is connected in axial displacement with the intake valve, and which is slidably mounted in the cylinder cylinder (100) within which it (102) sealingly delimits a control chamber of the cylinder, said closure chamber (104), - f) the engine comprises at least one control channel (X2) of opening the inlet valve (9) which connects said closing chamber (104) to a source of pressurized gas which is either the upper part of the active chamber (CA) of the cylinder or the inlet duct (8) ), or the pressurized gas tank, - (g) the engine has a active distribution channel (X1) which connects said closure chamber (104) to the upper part of the active chamber (CA) and a valve (Y) for closing the circulation of the gas in the active distribution channel (X1) , said valve (Y) active distribution, whose opening is controlled to put the closure chamber in communication with the upper portion of the active chamber (CA), close the inlet valve (8) and produce a job that is added to the work of the pre-admitted pressure gas charge, via the intake duct, in the active chamber.
    [0002]
    2. Motor according to claim 1, characterized in that the valve (Y) active distribution is controlled according to the following cycle: i) opening of the active dispensing valve to put the closure chamber (104) in communication with the chamber active (CA) to cause the closing of the inlet valve (9) then, during the expansion phase, allow the expansion of the compressed gas, contained in the closure chamber, in the expansion chamber (CD) the cylinder producing a work which is added to the work of the pre-admitted pressure gas charge, via the intake duct, in the active chamber; ii) at the end of the expansion phase, closing again of the active dispensing valve (Y) to maintain inside the closure chamber (104) the pressure of the expanded gas whose value is close to that of the atmospheric pressure.
    [0003]
    3. Engine according to claim 2, characterized in that said means d) for controlling the opening of the intake valve (9) comprise: - dl) a channel (X2) for controlling the opening of the valve d an inlet which connects the upper part of the active chamber (CA) to the inlet duct (8) or the pressurized gas tank (12), - d2) and a valve (Z) controlled closing the circulation of the gas in the opening control channel (X2), said opening valve (Z).
    [0004]
    4. Motor according to claim 3, characterized in that said opening control valve (z) is controlled according to the following cycle: k1) at the end of the exhaust phase, when the piston (2) is substantially in neutral high of its stroke, opening of said valve (Z), to allow to establish in the active chamber (CA) a pressure identical to that prevailing in the intake duct (8) and cause the detachment of the intake valve (9) its seat (20); k2) the inlet valve (9) then runs its full opening stroke under the action of the differential pressure forces exerted by the gas under pressure on the corresponding parts of the intake valve (9); k3) closing said valve (Z) as soon as the inlet valve (9) opens.
    [0005]
    5. Motor according to claim 2, characterized in that it comprises a channel (X3) which connects said closing chamber (104) to the inlet duct and / or the tank (12) of pressurized gas, and a valve (T) closing the flow of gas in this channel (X3) whose opening and closing are controlled, to cause the closing of the admission valve, prior to the communication of the closing chamber (104) ) with the volume of the cylinder (1) swept by the cylinder (2).
    [0006]
    6. Engine according to claim 1, characterized in that said means (d) for controlling the opening of the intake valve (9) comprise a finger (D) formed in relief on the upper face of the piston (2) which, during the end of stroke of the piston (2) towards its top dead point, acts, through the inlet orifice, on a portion facing the valve (22) intake (9) to take off from its seat (20).
    [0007]
    7. Motor according to claim 6, characterized in that the active distribution valve (Y) is controlled according to the following cycle: j) opening of the active dispensing valve (Y) to put the closure chamber (104) in communication with the active chamber (CA) to put the closure chamber (104) in communication with the expansion chamber (CD) of the cylinder, to allow the expansion of the compressed gas, contained in the closure chamber (104), in the chamber detent (CD) of the cylinder by producing a work which is added to the work of the pressure gas charge previously admitted into the active chamber; (jj) at the end of the expansion phase, closing again the valve (Y) active distribution to maintain inside the closure chamber a pressure whose value is close to that of atmospheric pressure.
    [0008]
    Motor according to one of the preceding claims, characterized in that the maximum open position of the intake valve (9) is defined by an adjustable stop (30) whose axial position in the direction the displacement of the intake valve (9) is controlled to vary the flow rate of pressurized gas admitted into the cylinder (1) via the intake duct.
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    同族专利:
    公开号 | 公开日
    WO2015177076A3|2016-01-14|
    CN106414899B|2019-07-05|
    RU2016145407A|2018-06-26|
    AU2015263264A1|2016-11-10|
    FR3021347B1|2016-05-20|
    ZA201608834B|2018-08-29|
    AP2016009621A0|2016-12-31|
    US10371023B2|2019-08-06|
    WO2015177076A2|2015-11-26|
    EP3146167B1|2018-12-12|
    EP3146167A2|2017-03-29|
    KR20170007306A|2017-01-18|
    RU2701784C2|2019-10-01|
    AU2015263264B2|2019-05-16|
    IL248944D0|2017-01-31|
    RU2016145407A3|2018-12-04|
    IL248944A|2020-06-30|
    US20170211435A1|2017-07-27|
    KR102345515B1|2021-12-31|
    CA2946481A1|2015-11-26|
    ES2715515T3|2019-06-04|
    CN106414899A|2017-02-15|
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    法律状态:
    2015-05-21| PLFP| Fee payment|Year of fee payment: 2 |
    2015-11-27| PLSC| Publication of the preliminary search report|Effective date: 20151127 |
    2016-05-30| PLFP| Fee payment|Year of fee payment: 3 |
    2017-05-25| PLFP| Fee payment|Year of fee payment: 4 |
    2018-06-26| PLFP| Fee payment|Year of fee payment: 5 |
    2019-05-31| PLFP| Fee payment|Year of fee payment: 6 |
    2020-05-30| PLFP| Fee payment|Year of fee payment: 7 |
    2021-05-31| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1454603A|FR3021347B1|2014-05-22|2014-05-22|COMPRESSED AIR MOTOR WITH ACTIVE CHAMBER INCLUSIVE AND ACTIVE DISTRIBUTION AT ADMISSION|FR1454603A| FR3021347B1|2014-05-22|2014-05-22|COMPRESSED AIR MOTOR WITH ACTIVE CHAMBER INCLUSIVE AND ACTIVE DISTRIBUTION AT ADMISSION|
    CN201580027044.6A| CN106414899B|2014-05-22|2015-05-18|Active air inlet distributing type compressed air engine with built-in recreation room|
    CA2946481A| CA2946481A1|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    PCT/EP2015/060855| WO2015177076A2|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    ES15726034T| ES2715515T3|2014-05-22|2015-05-18|Compressed air motor with active chamber included and with active distribution on admission|
    KR1020167032335A| KR102345515B1|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    AP2016009621A| AP2016009621A0|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    AU2015263264A| AU2015263264B2|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    EP15726034.0A| EP3146167B1|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    US15/312,828| US10371023B2|2014-05-22|2015-05-18|Compressed-air engine with an integrated active chamber and with active intake distribution|
    RU2016145407A| RU2701784C2|2014-05-22|2015-05-18|Compressed air engine with active chamber and active intake distribution|
    IL248944A| IL248944A|2014-05-22|2016-11-14|Compressed-air engine with included active chamber and with active intake distribution|
    ZA2016/08834A| ZA201608834B|2014-05-22|2016-12-21|Compressed-air engine with an integrated active chamber and with active intake distribution|
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