• 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 relates to a machine (4) for axial expansion with pistons comprising: - a cylinder head (10) for the admission of pressurized vapor comprising a steam inlet (100), - an expansion zone comprising a plurality of cylinders (110), wherein a piston sliding in each respective cylinder is connected to a shaft (40) by an inclined plate (20), each piston being parallel to said shaft, - a plurality of stem valves (12) arranged in the cylinder head (10) for admitting steam alternately into said cylinders (110), each valve (12) being controlled by a cam (21) arranged on the shaft (40), - a mechanism (13) ) of the lifting of each valve cooperating with the cam, - a mechanism for returning each valve, said machine being characterized in that the cylinder head (10) comprises: - a central zone (10A) closed and lubricated comprising the cam and mechanisms for raising and returning the valves, - a peripheral zone (10B) into which the inlet orifice (100) opens, extending around the central zone (10A).
    公开号:FR3031135A1
    申请号:FR1463443
    申请日:2014-12-30
    公开日:2016-07-01
    发明作者:Antoine Debaise；Edouard Davin；Yohann Routaboul
    申请人:Exoes SAS；
    IPC主号:
    专利说明:

    [0001] FIELD OF THE INVENTION The present invention relates to an axial expansion machine with pistons. BACKGROUND OF THE INVENTION Systems for converting heat from an engine into mechanical energy are known. Such assemblies are in particular known for the conversion of heat emitted by internal combustion engines, which is notably dissipated during the expulsion of the exhaust gases and is therefore lost. Such assemblies are subject to demanding weight and size constraints. They tend to become more and more compact. These systems operate with a working fluid that is subjected to a Rankine thermodynamic cycle including compression, evaporation supplemented by possible overheating, expansion in an expansion machine, and condensation. The expansion within the expansion machine makes it possible to actuate movable members such as pistons in order to obtain mechanical energy. Of particular interest are systems comprising an expansion machine which comprises a pressurized steam inlet yoke comprising a steam inlet and an expansion zone comprising a plurality of cylinders, wherein a sliding piston in each respective cylinder is connected to a shaft by an inclined plate, each piston being parallel to said shaft. A plurality of valves arranged in the intake yoke allow the admission of steam alternately in said cylinders, each valve being controlled by a cam arranged on the shaft and cooperating with a mechanism for raising and returning each valve. In this type of machine, the pistons can be single-effect, that is to say, to benefit from mechanical work by expansion of the steam only one side, or double-effect, that is to say ie enjoy mechanical work by relaxing the steam on both sides. The document WO 2005/073511 describes, with reference to FIGS. 1 and 6, expansion machines comprising single-acting pistons. In these machines, the connection between the valve stem and the cam is well lubricated because it is in a housing also containing the inclined plate. However, this configuration has the disadvantage of requiring very long valve stems, which increase their mass and consequently the inertial forces. The valve return mechanism - usually a spring - must therefore be dimensioned accordingly, which further increases the mass and overall size of the machine. Moreover, this construction of the valves is hardly compatible with the use of double-acting pistons. Indeed, in the case of Figure 1, the shaft would interfere with the valves and, to prevent the passage of lubricant into the cylinder head containing the high pressure steam, it would be necessary to provide special seals, which are expensive and unreliable at the operating temperatures of the machine. In the case of Figure 6, the arrangement of the valves at the periphery of the machine is more favorable to the use of double-acting pistons, but would require an increase in the outer diameter of the machine. US 4,262,579 discloses another piston axial expansion machine. This document does not show any confinement of the zone extending from the cam to the cylinder in which each piston slides. As a result, any vapor leakage from the valve stem guides is lost. On the other hand, the inlet angles of the steam engines are generally very low, which results in extremely steep valve lifts and requires, for machines rotating at high speed, very stiff valve return springs. These springs being bulky in particular in the axial direction, they penalize the compactness of the machine. However, in applications to embark such a conversion system on a vehicle, it is necessary to minimize the size and mass of the various components of the system.
    [0002] BRIEF DESCRIPTION OF THE INVENTION An object of the invention is to overcome the disadvantages of existing expansion machines and to design a piston axial expansion machine which is more compact while providing good lubrication and avoiding losses. 25 steam caused by possible leaks. According to the invention, there is provided an axial piston expansion machine comprising: - a pressurized steam inlet yoke comprising a steam inlet, - an expansion zone comprising a plurality of cylinders wherein a piston sliding in each respective cylinder is connected to a shaft by an inclined plate, each piston being parallel to said shaft, - a plurality of stem valves disposed in the intake yoke allowing the admission of steam alternately in said cylinders, each valve being controlled by a cam arranged on the shaft, - a lifting mechanism of each valve cooperating with the cam, - a return mechanism of each valve, said machine being characterized in that the cylinder head comprises: a closed and lubricated central zone comprising the cam and the mechanisms for raising and returning the valves, a peripheral zone in which e opens the intake port, extending around the central area. .
    [0003] By "upper" or "lower" is meant a position relative to the position of the expander during normal use. By "longitudinal" is meant a direction parallel to the axis of the shaft. Particularly advantageously, said peripheral zone extends only around an upper part of the central zone.
    [0004] Preferably, said peripheral zone has no common wall with the lower part of the central zone. According to one embodiment, the machine further comprises a lubrication circuit of the central zone, said circuit comprising: a channel arranged in the shaft and opening into the central zone through a lubricant inlet orifice, and a lubricant outlet orifice arranged in a wall of the lower part of the central zone. Furthermore, the central zone advantageously comprises, in its upper part, a steam passage opening in fluid connection with an exhaust zone of the machine. According to a preferred embodiment, the return mechanism of each valve comprises a torsion bar and a return pawl extending between said torsion bar and the stem of a respective valve so as to exert a plating force of the valve head vis-à-vis the seat of said valve.
    [0005] Preferably, the torsion bar is parallel to the shaft. According to an advantageous embodiment, the return pawl is secured to the stem of the valve by a fork. Preferably, said fork is in contact with the tail of the valve by two points of contact whose axis is not parallel to the axis of rotation of the return pawl, so that the fork induces a rotation of the rod about the axis of said rod. Furthermore, the lifting mechanism of each valve comprises a pivoting latch integral with a respective valve, said pawl, called "cam follower latch", cooperating with the cam so as to move the head of said valve from the seat of said valve .
    [0006] According to one embodiment, the pistons are double acting.
    [0007] BRIEF DESCRIPTION OF THE DRAWINGS Other features and advantages of the invention will become apparent from the following detailed description, with reference to the accompanying drawings, in which: FIG. 1 is a block diagram of a Rankine circuit; FIG. 2 is a perspective view of the outside of an expansion machine according to one embodiment of the invention, FIG. 3 is a cross-sectional view at the level of the cylinder head of the expansion machine of FIG. FIG. 2 is a longitudinal sectional view of the expansion machine of FIG. 2; FIGS. 5 and 6 are perspective views of the mechanisms for raising and returning a valve in a manner; FIG. FIG. 7 is a perspective view of a particular embodiment of the return latch, FIG. 8 is a cross-sectional view at the level of the bolt of a machine of FIG. relaxation according to another embodiment of the invention 'invention. DETAILED DESCRIPTION OF THE INVENTION FIG. 1 represents a circuit operating a Rankine thermodynamic cycle.
    [0008] This figure shows a circuit 1 containing a working fluid, the circuit 1 comprising: - a pump 2, typically a pump adapted to deliver a flow of working fluid which establishes a pressure of 40 bars at its discharge; a first heat exchanger 3 which will be referred to in the rest of the text as "evaporator"; an expansion machine 4; a second heat exchanger 5, which will be referred to in the rest of the text as "condenser"; - a bypass device 6.
    [0009] The pump 2 supplies the evaporator 3 with working fluid in the liquid state under pressure, typically of the order of 40 bar. The evaporator 3 is placed in a medium at high temperature, and thus carries out a heat transfer between the medium at high temperature and the working fluid so that the latter is vaporized and goes into the gaseous state.
    [0010] The working fluid leaving the evaporator 3 is thus in the gaseous state and under pressure. The working fluid then passes through the expansion machine 4, in which a relaxation occurs.
    [0011] The expansion of the working fluid in the expansion machine 4 drives moving means such as a rotating mechanical shaft, thereby recovering the energy of the expansion of the working fluid. The moving means are advantageously coupled to the shaft of the internal combustion engine, so as to reinject a mechanical torque. The mobile means may also be coupled to energy conversion means such as an electric generator, so as to allow a conversion of the energy resulting from the expansion into electrical energy. The working fluid at the outlet of the expansion machine 4 is therefore in the gaseous state, and at low pressure, typically of the order of 2.2 bars. The working fluid then passes through the condenser 5, which is arranged in a medium at a low temperature in order to achieve a heat exchange between the working fluid and this medium at a low temperature to lower the temperature of the working fluid and bring it back to the temperature. liquid state.
    [0012] The working fluid at the outlet of the condenser 5 is therefore in the liquid state and at a low pressure, of the order of 2.2 bars. It is then re-injected into the circuit 1 by the pump 2 and carries out the cycle described above again. The circuit 1 presented further comprises a bypass device 6 adapted to allow all or part of the working fluid to be withdrawn upstream of the expansion machine 4 and reinject it into the circuit 1 downstream of the expansion machine 4. thus realizing a short circuit function of the relaxation machine 4. It is commonly called such a device according to the English name "bypass". Such a bypass device 6 is advantageously used in the initiation phase of the circuit 1 in order to allow the establishment of the temperature and pressure conditions in the circuit 1 and / or to achieve a temperature increase of the casing 17, or if it is necessary to modulate the operation of the circuit 1. FIG. 2 is a perspective view of the outside of an expansion machine according to one embodiment of the invention. In this embodiment, the machine contains double-acting pistons, pressurized steam being admitted into two yokes 10 located on either side of the machine. Although preferred, this configuration is not limiting and a construction with single-acting pistons can be implemented without departing from the scope of the present invention. The machine 4 comprises an inlet 100 for the admission of pressurized steam into each cylinder head 10, as well as two exhaust ports 200. FIG. 3 is a cross-sectional view at a cylinder head of the expansion machine of Figure 2, in its normal position of use. Figure 4 is a longitudinal sectional view of said machine.
    [0013] The cylinder head 10 has a port 100 for admitting steam under pressure. The yoke further comprises a central zone 10A and a peripheral zone 10B. For reasons explained in detail below, the peripheral zone 10B partially surrounds the central zone 10A. Specifically, the peripheral zone 10B extends only around the upper portion of the central zone 10A. The orifice 100 opens into the peripheral zone 10B of the cylinder head. The machine 4 comprises cylinders 110 (three in number on each side of the machine in Figure 4) which are arranged in an expansion zone, within which slides a respective piston 111 (see Figure 4). As indicated above, in this figure, the pistons are double acting, although this configuration is not limiting. Each piston 111 is connected to a shaft 40 by an inclined plate 20 (see FIG. 4), each piston being parallel to the shaft 40. In the normal position of use, the shaft 40 extends in a substantially horizontal plane . The tray is arranged in a housing 14 containing a lubricant which is in the liquid state under the operating conditions of the machine. The connection between each piston and the inclined plate is lubricated. Each cylinder is in fluid connection with an exhaust zone which opens out of the machine through an exhaust port 200, for the exhaust of the working fluid in the relaxed state.
    [0014] In a region extending in the yoke 10, the shaft 40 carries a cam 21. Said cam may form an integral part of the shaft or may be manufactured separately from the shaft and then made rigidly secured thereto. Said cam 21 controls a plurality of valves 12 (three in the embodiment of FIG. 3, this number being purely indicative) so as to allow pressurized steam to be admitted from the peripheral zone 10B into a cylinder 110 respective. Valves 12 are stem valves (commonly referred to as "poppet valves" in the manner known per se, such valves include: - a circular head 120 fulfilling a shutter function between the intake cylinder and each cylinder When the valve is in the closed position, it is supported on a valve seat 101 arranged in the cylinder head to seal the cylinder - a cylindrical rod 121 whose diameter is substantially less than that of the head, which vertically guides the valve by sliding in a valve guide 102 formed in the cylinder head; - a collar 122 connecting the head 120 to the rod 121 with a large radius of curvature, 3031135 7 - a shank 123 located at the end of the rod opposite the head, coupled to the lever mechanism 13 of the valve which cooperates with the cam 21. An advantage of the stem valves is that they present They are smaller in size, which makes it possible to minimize the forces of inertia, thus favoring the compactness of the machine. In addition, the stem valves are an intake system requiring good lubrication only in the contact between the rod and the guide. The contact between the head and the seat which is the hottest contact of this mechanism, can be satisfied with low lubrication, for example a supply of lubricant flowing with the working fluid of the expansion machine. Mass proportions of lubricant in the working fluid less than or equal to 5% are sufficient. As can be seen in FIG. 3, the cam and the mechanisms for raising and returning the valves are located in the central zone 10A of the cylinder head. This zone 10A is closed and lubricated, which ensures proper operation of the mechanical connections involved while avoiding losses of steam in the event of leaks occurring at the level of the valve guides. Indeed, the zone 10A advantageously comprises a drain hole 103 of these possible steam leaks to the exhaust zone of the rolls. Thus, the steam is reinjected into the steam circuit. Furthermore, the lubricant is fed into the central zone 10A from the housing via a bore 22 formed in the shaft 40. Said bore extends longitudinally inside the shaft 40 and opens by a radial bore 23 in the zone 10A. For this purpose, the lubricant is pumped from the casing 14 through channels 150 by an oil pump 15 located at one end of the shaft 40.
    [0015] The lubricant thus introduced into the central zone 10A makes it possible to lubricate the various mechanical connections and then falls by gravity into the lower part of said zone 10A. The central zone 10A furthermore comprises a lubricant outlet orifice 104 arranged in a wall of the lower part of said zone. Said orifice is in fluid connection with the housing 14, so as to allow the return of the lubricant to the housing. Insofar as the lower part of the central zone 10A does not have a common wall with the peripheral zone 10B which is subjected to a high temperature, the lubricant is not heated unnecessarily before it is removed from the central zone 10A, which avoid degrading it.
    [0016] Furthermore, since the oil pump 15 is situated at the end of the expansion machine, conduits can thus be arranged in the lower part of the central zone for supplying the oil pump with lubricant from the crankcase. and feeding, from the oil pump, certain areas of the expansion machine.
    [0017] Thus, ducts (not shown) can also be arranged in this lower part for the removal of the lubricant supplying the rotary joint of the shaft. In the embodiment illustrated in Figures 2 to 4, the pistons are double acting and the expansion machine comprises two intake heads 10 on either side of the machine. The longitudinal bore 22 formed in the shaft supplies lubricant to the central zone of each of the two intake heads. Alternatively or additionally, a conduit 103 may be arranged between the exhaust zone of one or more cylinders and the central zone 10A so as to allow flow of the exhaust vapor after expansion towards the central zone 10A. This configuration makes it possible, in the case where the working fluid is loaded with lubricant, to lubricate the mechanical connections involved in the control of the valves by the lubricant present in the steam, alone or in addition to the lubrication coming from the shaft. . A preferred embodiment of the valve lift and return mechanisms will now be described in greater detail with reference to FIGS. 5 and 6. The mechanism for lifting a valve comprises a latch 130, which is called the "follower latch". cam "pivoting along an axis parallel to the shaft and having a zone 131 of contact with the cam. Said pawl is coupled, by an area opposite the zone 131, to the tail 123 of the valve 12 so as to exert a thrust force on the valve 20 when the zone 131 cooperates with the cam 21. This thrust force has for effect of spreading the head 120 of the valve seat 101, thus allowing the admission of steam in the corresponding cylinder. The machine further comprises a return means of the valve for exerting a plating force of the valve head against its seat.
    [0018] In the embodiment illustrated in FIGS. 5 and 6, this biasing means comprises a torsion bar 132 arranged longitudinally in the machine. At one of its ends, the torsion bar is rigidly secured to a latch 133, called "return latch". At its opposite end, the torsion bar is rigidly secured to a tube 134 inside which it is arranged. Said tube 134 is itself fixed to the yoke. The valve lift slightly twists the bar 132, this twist inducing in the bar a moment of recall. The return latch 133 is integral with the stem 121 of the valve in the vicinity of the tail. The connection between the return latch 133 and the rod 121 is formed by a fork 1330 extending at the end of the return latch opposite the torsion bar.
    [0019] The fork 1330 has two parallel arms surrounding the rod 121, the distance between the arms being equal to the diameter of the rod. The speed of rotation of the cam is indeed high and the opening angle of the valve is very low. Thus the movement of the valve generates extremely important inertia efforts. It is necessary to reduce the mass of the valve and to fight against the inertia thanks to a force of important recall. However, it is not possible with a compact spring to have a sufficient restoring force for the low lifting heights used, without using a significant pre-stress of a spring. This pre-stress permanently rubs the cam follower latch on said cam which increases the friction of the motor and the wear. A torsion bar provides a very high stiffness which avoids the use of a significant pre-stress. Whatever the mode of implementation of the torsion bar, this return mechanism is particularly advantageous in that it has a high compactness. In fact, at equal stiffness, the torsion bar has a much smaller footprint than a spiral spring conventionally used as a return means. FIG. 7 is a perspective view of an advantageous embodiment of the return latch, said latch 133 being capable of being used in the return mechanisms shown in FIGS. 5 and 6.
    [0020] The contacts C1, C2 between the arms of the fork 1330 and the tail 123 of the valve allow rotation of the rod about its axis. This rotation is induced by a small angle formed between the axis X of rotation of the return latch and the axis X 'of the contact points C1, C2 of the fork, which generates a different effort at each of the two contacts . This allows the valve head to be continuously honed over its seat and thus to limit leakage throughout the life of the machine. Figure 8 is a cross-sectional view at the yoke of another embodiment of the axial expansion machine according to the invention. The reference signs identical to those of the preceding figures designate elements fulfilling the same functions as in the previous embodiment, and which are therefore not described again. In this embodiment, the return function is not filled by torsion bars but by springs 140 each arranged between a valve guide and the tail of the respective valve. The springs 140 thus exert a return force of the valve to press against its seat.
    [0021] This embodiment is however less preferred because the springs 140 must be very stiff and consequently bulky, which penalizes the compactness of the machine. In addition, the valve lift laws are very steep because each valve is open only over a very small angular range (of the order of 70-80 °) compared to an internal combustion engine. The lift height of the valves is also low (of the order of 2 mm) compared to an internal combustion engine. If the lift speed is too high, the valve is catapulted out of its seat and its inertia makes it difficult for the return mechanism to keep it in contact with the cam or, if necessary, on the cam follower as on Figure 8. In this case (called "valve release"), the opening time of the valve is no longer controlled (ballistic operation) and shocks during the resumption of contact lead to the eventual failure of the system .
    [0022] Finally, it goes without saying that the examples which have just been given are only particular illustrations that are in no way limiting as to the fields of application of the invention. REFERENCES 10 VVO 2005/073511 US 4,262,579
    权利要求:
    Claims (11)
    [0001]
    REVENDICATIONS1. A piston axial expansion machine (4) comprising: - a pressurized vapor inlet yoke (10) having a steam inlet (100); - an expansion zone comprising a plurality of cylinders (110); ), wherein a piston (111) sliding in each respective cylinder is connected to a shaft (40) by an inclined plate (20), each piston being parallel to said shaft, - a plurality of stem valves (12) disposed in the a cylinder head (10) for admitting steam alternately into said cylinders (110), each valve (12) being controlled by a cam (21) arranged on the shaft (40), - a mechanism (13) for lifting of each valve cooperating with the cam, - a mechanism for returning each valve, said machine being characterized in that the cylinder head (10) comprises: - a central zone (10A) closed and lubricated comprising the cam and the mechanisms for raising and returning the valves, - a peripheral zone 10B) into which the inlet (100) opens, extending around the central zone (10A).
    [0002]
    2. Machine according to claim 1, wherein said peripheral zone (10B) extends only around an upper part of the central zone (10A).
    [0003]
    3. Machine according to claim 2, wherein said peripheral zone (10B) has no common wall with the lower part of the central zone (10A). 25
    [0004]
    4. Machine according to one of claims 1 to 3, further comprising a lubrication circuit of the central zone (10A), said circuit comprising: - a channel (22) arranged in the shaft and opening into the central zone ( 10A) through a lubricant inlet port (23), and a lubricant outlet port (104) provided in a wall of the lower portion of the central zone (10A).
    [0005]
    5. Machine according to one of claims 1 to 4, wherein the central zone (10A) comprises, in its upper part, a hole (103) for the passage of steam in fluid connection with an exhaust zone of the machine.
    [0006]
    6. Machine according to one of claims 1 to 5, wherein the return mechanism of each valve comprises a torsion bar (132) and a return latch 3031135 12 (133) extending between said torsion bar (132). ) and the rod (121) of a respective valve so as to exert a plating force of the valve head (120) vis-à-vis the seat (101) of said valve. 5
    [0007]
    7. Machine according to claim 6, wherein the torsion bar (132) is parallel to the shaft (40).
    [0008]
    8. Machine according to one of claims 6 or 7, wherein said return latch (133) is secured to the stem (121) of the valve by a fork (1330).
    [0009]
    9. Machine according to claim 8, wherein the fork (1330) is in contact with the tail of the valve by two points of contact whose axis (X ') is not parallel to the axis of rotation (X ) of the return latch (133), so that the fork (1330) induces a rotation of the rod (121) about the axis of said rod.
    [0010]
    10. Machine according to one of claims 1 to 9, wherein the mechanism (13) for lifting each valve comprises a pivoting pawl (130) integral with a respective valve, said pawl, said "follower cam follower", cooperating with the cam (21) to move the head (120) away from said seat valve (101) of said valve.
    [0011]
    11. Machine according to one of claims 1 to 10, wherein the pistons (111) are double-acting. 10 15 20
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    同族专利:
    公开号 | 公开日
    FR3031135B1|2019-09-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB610669A|1946-04-13|1948-10-19|Salter & Co Ltd G|Improvements relating to valve mechanism of internal combustion engines|
    US4167894A|1977-02-04|1979-09-18|Harris Marion K|Steam engine in which the cylinder inlet valves are actuated by the operation of the power conversion means|
    US4308719A|1979-08-09|1982-01-05|Abrahamson Daniel P|Fluid power system|
    GB2134977A|1983-01-29|1984-08-22|Bothwell P W|Internal combustion engine and cylinder head therefor|
    WO2005073511A1|2004-01-29|2005-08-11|Enginion Ag|Valve-controlled expansion machine|IT201600080081A1|2016-07-29|2018-01-29|Star Engine Srl|VOLUMETRIC EXPANDER, CLOSED CYCLE SYSTEM USING THE EXPANDER AND PROCESS OF CONVERSION OF THERMAL ENERGY IN ELECTRICAL ENERGY BY MEANS OF THIS SYSTEM.|
    IT201600080087A1|2016-07-29|2018-01-29|Star Engine Srl|VOLUMETRIC EXPANDER, SYSTEM WITH CLOSED CYCLE USED AS THE EXPANDER, PROCEDURE FOR STARTING THE VOLUMETRIC EXPANDER AND PROCEDURE FOR THE CONVERSION OF THERMAL ENERGY IN ELECTRICAL ENERGY BY MEANS OF THIS SYSTEM|
    FR3067386A1|2017-06-13|2018-12-14|Exoes|RELAXATION MACHINE|
    法律状态:
    2016-01-22| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-01| PLSC| Search report ready|Effective date: 20160701 |
    2016-12-07| PLFP| Fee payment|Year of fee payment: 3 |
    2017-12-13| PLFP| Fee payment|Year of fee payment: 4 |
    2018-12-07| PLFP| Fee payment|Year of fee payment: 5 |
    2019-12-12| PLFP| Fee payment|Year of fee payment: 6 |
    2021-09-10| ST| Notification of lapse|Effective date: 20210806 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1463443|2014-12-30|
    FR1463443A|FR3031135B1|2014-12-30|2014-12-30|AXIAL PISTON RELIEF MACHINE|FR1463443A| FR3031135B1|2014-12-30|2014-12-30|AXIAL PISTON RELIEF MACHINE|
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