EP1072791A2 - Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung - Google Patents

Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung Download PDF

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Publication number
EP1072791A2
EP1072791A2 EP00401985A EP00401985A EP1072791A2 EP 1072791 A2 EP1072791 A2 EP 1072791A2 EP 00401985 A EP00401985 A EP 00401985A EP 00401985 A EP00401985 A EP 00401985A EP 1072791 A2 EP1072791 A2 EP 1072791A2
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EP
European Patent Office
Prior art keywords
cylinder
selector
cylinders
group
communication
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00401985A
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English (en)
French (fr)
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EP1072791A3 (de
EP1072791B1 (de
Inventor
Louis Martin
Jean-Marie Rouillard
Jean-Pierre Souply
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Poclain Hydraulics Industrie
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Poclain Hydraulics Industrie
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Publication of EP1072791A2 publication Critical patent/EP1072791A2/de
Publication of EP1072791A3 publication Critical patent/EP1072791A3/de
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Publication of EP1072791B1 publication Critical patent/EP1072791B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0425—Disconnecting the pistons from the actuated cam

Definitions

  • An engine of this type is known from document FR 2 710 111.
  • all cylinders are periodically supplied with pressurized fluid. he is known to suppress the periodic supply of fluid to all the cylinders to make them inactive so that the engine does deliver no couple. It is also known to not remove fluid supply than some cylinders, other cylinders continuing to be periodically supplied with fluid, so that the engine works in partial displacement.
  • the invention applies equally well to an engine for which all cylinders belong to the first group and are therefore likely to be made all inactive, only to an engine further comprising a second group of cylinders which continue to be active when the cylinders of the first group are made inactive.
  • FR 2 710 111 recommends the use of selection means which include a selector individual for each of the cylinders of the first group, this selector individual being controlled so that it cannot be activated for disengage or engage the sliding piston in the cylinder to which it is associated only when the axis of this cylinder passes, during the relative rotation of the cylinder block and the cam, by one position in which it is close to the top of an undulation of the cam.
  • This system works, but it turns out relatively expensive since it requires the presence of as many individual selectors that the first group of cylinders includes of cylinders. It also requires control means adapted to activate each of these individual selectors at specific times.
  • Document FR 2 677 409 discloses a circuit hydraulic to disengage the pistons of an engine hydraulic.
  • This circuit includes a shuttle valve interposed on the conduits connecting the pump ports to the main ports engine supply and exhaust.
  • This system is external, and it is attached to the engine, which increases its size.
  • the clutch is applied indiscriminately to all engine pistons. Finally, the shock problems when disengaging and re-clutching are not avoided.
  • the object of the present invention is to propose a system simple, arranged inside the engine, to allow disengagement pistons sliding in the cylinders of the first group, substantially avoiding the shock phenomena of these pistons against the cam during the declutching and re-clutch phases of the pistons concerned, even at relatively rotational speeds high, for example of the order of 100 rpm and more.
  • the means of selection include a single clutch selector, integral with the cylinder block with respect to the rotation around the axis of rotation and comprising a communication conduit for each cylinder of the first group of cylinders, this selector being susceptible to occupy a first position, corresponding to said first configuration, in which the communication paths allow connection of cylinder ducts to cylinders from the first group to the distribution ducts, a second position corresponding to said declutching configuration and a transient intermediate position between said first and second positions, in which the cylinder ducts of the cylinders of the first group are linked together by an isolated enclosure.
  • the cylinder the cylinders of the first group are normally connected to the distribution pipes and are therefore alternately connected to the fluid supply and exhaust, so that the pistons sliding in these cylinders are active.
  • the cylinder ducts of the cylinders of the first group are all connected to the enclosure of discharge of fluid, so the pistons sliding in these cylinders are inactive and can be entered into said cylinders, that is to say, they are disengaged.
  • the enclosure of fluid discharge is simply part of the space inside of the motor which is connected to a return duct from leaks.
  • the cylinder of the cylinders of the first group are all interconnected by an isolated enclosure.
  • isolated enclosure is meant a part of the interior space of the motor housing which is isolated from different "functional" engine ducts, that is to say the ducts that are connected to a line outside the engine, such as a supply or exhaust line, or a line auxiliary, connected to the engine boost circuit to ensure an auxiliary function of this motor (brake control, etc.).
  • the isolated enclosure is neither connected to the power supply, neither at the exhaust nor at any auxiliary pressure external to the engine.
  • the pistons of the cylinders of the first group can move in their respective cylinders according to their positions on the cam. In other words, they don't not hang in a given position inside their cylinders, but they can follow the undulations of the cam, the volumes of fluid displaced by the reentry movement of some pistons compensating for the volumes of fluid displaced by the movement out of other pistons, the engine being homokinetic.
  • the invention makes it possible to avoid a direct communication of the fluid discharge enclosure with the engine supply or exhaust, which would adversely affect proper functioning of the latter.
  • the cylinder ducts of the cylinders of the first group are not isolated from each other, which avoids blocking pistons sliding in these cylinders.
  • the clutch selector is formed by a drawer mounted sliding in a bore of the cylinder block, the communication conduits comprising grooves of communication on the surface of this drawer.
  • the conduits cylinder of the cylinders of the first group then have orifices which are open in said bore of the cylinder block and which are each permanently connected to a groove of communication; the cylinder block bore has a groove intercommunication to which the communication grooves are connected in the transient position of the selector.
  • the communication grooves are arranged axially or substantially axially on the surface of the drawer. Their machining is so extremely simple. In the first position of the selector, these communication grooves are used to connect the conduits of cylinder of the cylinders of the first group with the conduits of distribution, so that the pistons of the cylinders of the first group are active. By an axial displacement of the selector towards its second position, this connection of the cylinder ducts of cylinders of the first group with the distribution ducts ceases, and the communication grooves are all connected to the groove interconnection of the cylinder block.
  • the assembly formed by the cylinder ducts of the cylinders of the first group, the communication grooves and the intercommunication groove constitutes the isolated enclosure through which the cylinder ducts of the cylinders of the first group communicate with each other in the transient position of the selector.
  • the motor prefferably has, for each cylinder duct of the cylinders of the first group, one distribution passage formed by a conduit which has a first orifice open in the bore of the cylinder block and a second orifice open on a communication face of the cylinder block in order to be connected to the distribution ducts during the relative rotation of the cylinder block and distributor and, for each cylinder duct cylinders of the first group, the first orifice of the duct forming the distribution passage, the orifice of the cylinder duct and the intercommunication groove are successively arranged in the bore of the cylinder block in the direction of movement of the drawer selector from its first to its second position.
  • the passage of communication is permanently connected to the face of communication from the cylinder block and is therefore likely to be alternately connected with each of the distribution conduits.
  • the communication groove realizes, for each conduit of cylinder of the cylinders of the first group, the communication between the cylinder duct and this distribution passage, this in the first position of the selector. When this selector is moved in its second position, the communication between the passage of distribution and the cylinder conduit stops, while said conduit cylinder is connected to the intercommunication groove, always by the communication groove.
  • the motor includes means for controlling the movement of the selector which include elastic return means capable of urging permanently said selector to one of its first and second positions and counter-force means likely to be commanded to request movement of the selector towards the other of its first and second positions.
  • the elastic return means urge the selector to its first position and the means of counter-force include a control piston cooperating with a control cylinder integral with a stator part of the engine, said control piston being capable of being moved to against the recall effort of said recall means for press the selector to its second position.
  • Disengagement of pistons of cylinders of the first group is then obtained by a positive control of the piston of control, against the elastic return means, this control being in particular hydraulic.
  • control piston cooperates with the selector by means of spherical stop means, or either by means of rolling, or even by through hydrostatic stop means using a fluid confined.
  • the control cylinder is integral with a part of stator of the motor, while the selector is integral in rotation with the cylinder block. Therefore, the part of the selector with which cooperates the control piston rotates relative to the cylinder ordered.
  • the choice of spherical stop means, hydrostatic bearing or stop means avoids a premature wear of parts in relative rotation.
  • the choice of spherical abutment means makes it possible to limit friction between the control piston and the selector at a low area area. This zone is preferably aligned with the axis of rotation of the engine, the bore of the cylinder block in which the clutch selector, as well as the control cylinder, preferably being centered on the axis of the engine. So the speed relative between the fixed part and the rotating part is low, so that at most a very low torque is generated in this area. he as a result, the friction, and therefore the heating of the parts in contact are limited.
  • ball thrust means eliminates substantially this friction, by replacing it with a rolling contact, which also avoids the risk of friction and therefore of wear premature.
  • the counter-force means include a control chamber formed between the selector and a fixed reference part with respect to the cylinder block, as well as a control conduit able to connect said control chamber to a source of fluid.
  • the elastic return means urge the selector to its second position and the means counter-effort are likely to be ordered to solicit the selector to its first position.
  • the clutch configuration is obtained at rest, by the elastic return means.
  • This is advantageous, for example when the engine is used for driving a vehicle.
  • a failure in the control of the counter-force means occurs while the vehicle is traveling in configuration clutched pistons (therefore at low speed and high engine torque)
  • this failure places the selector in configuration of declutching, which decreases the cubic capacity and therefore the engine torque.
  • the driver can then easily control the speed by controlling the pump flow.
  • This variant is also advantageous in the case of a hydraulic motor fitted with a parking and safety brake.
  • the braking torque required to avoid untimely drive of the engine and the vehicle it equips simply be able to overcome the torque developed by the motor in its declutching configuration (therefore small displacement), which is that of rest.
  • This braking torque is lower to that which would be necessary if the selector rest position were its first position (in which the pistons are engaged), this which allows you to choose a less bulky and less expensive brake.
  • a decompression is provided at the end of the selector located on the downstream side of the latter in the direction of its displacement of its first in its second position, and in the second position of said selector, the cylinder ducts are connected to this chamber.
  • the decompression chamber When changing the selector from its first position in in its second position, the decompression chamber is supplied by the fluid in the cylinder ducts of the cylinders from the first group.
  • the decompression chamber is thus "put in pressure ", which opposes a force resistant to the pursuit of movement of movement of the selector to its second position. In other words, moving the selector between its position transient and its second position is slowed down, so that the declutching takes place smoothly.
  • This decompression chamber is advantageously in communication with a leak return line, connected to a tank without pressure. This communication takes place advantageously via at least one passage of low section, which causes, between the decompression and return pipe leakage, loss of load which prevents the selector from moving too quickly from its first position to its second position.
  • passage section of the passage (s) small section determines the pressure drop between the decompression and the fluid return line, which conditions the speed of movement of the selector between its transient position and its second position.
  • the invention can be applied to the motors of which one wishes that all the pistons are disengageable. She can also apply to engines with at least two separate displacements of operation which one wishes to disengage only pistons cylinders that are inactive in small displacement (s).
  • the cylinder block has a second group of cylinders arranged radially with respect to the axis of rotation, each cylinder of this second group being connected to a cylinder duct which is directly connected to a face of communication of the cylinder block cooperating with a face of distribution of the distributor, in order to be connected to the conduits of distribution during the relative rotation of the cylinder block and distributor, regardless of the selector position.
  • This displacement selector can be ordered independently of the clutch selector between two positions corresponding respectively to a larger displacement and to a smaller displacement. We thus obtain four separate displacements of operation depending on whether the selectors are simultaneously in their first positions or in their second positions or that one is in its first position while the other is in its second position.
  • Figure 1 shows a hydraulic piston motor radial, with fixed casing.
  • the housing has several parts, know a first part 1A, called distribution cover, a part 1B, the internal periphery of which is corrugated so as to form a reaction cam, and a part 1C. These different parts are assembled by screws 2.
  • the wavy cam is itself made in two parts, 4A and 4B, juxtaposed axially.
  • the engine comprises a cylinder block 6 which is rotatably mounted relative about an axis of rotation 10 relative to the cam and which has a plurality of radial cylinders within which are sliding mounted radial pistons.
  • the axes 13A of the cylinders 12A (axes arranged radially with respect to the axis of rotation 10) define a first radial plane PA, while the axes 13B of the cylinders of the second group 12B define a second radial plane PB distinct from the plane PA.
  • the pistons 14A which slide in the cylinders 12A of the first group cooperate with the first part 4A of the cam, while the pistons 14B which slide in the cylinders 12B of the second group cooperate with the second part 4B of the cam.
  • the cylinder block 6 rotates a shaft 5 which cooperates with it by grooves 7.
  • the end of the shaft 5 opposite the cover of the distributor 1A carries an outlet flange 9.
  • the shaft 5 is supported relative to the part 1C of the casing by bearing means, for example 8A tapered roller bearings and 8B.
  • the engine also has an internal distributor of fluid 16 which, by a system of pawns and notches 17, is made integral in rotation with the distribution cover 1A.
  • the distributor 16 has an external axial face 18 stepped, cooperating with an internal axial face 19 stepped from distribution cover 1A. Between faces 18 and 19, are formed three gorges, respectively designated by the references 20, 21 and 22.
  • the engine also has two main ducts, at know a main supply duct and a main duct exhaust. These main conduits are not in the section plane of Figure 1 but, to facilitate understanding, we indicated their positions with broken lines. So the first main duct 24 is permanently connected to the first groove 20, while the second main conduit 26 is permanently connected at the third groove 22. As will be seen below, the second groove 21 may, depending on the position of a displacement selector not shown in Figure 1, be connected to one or other of the gorges 20 and 22.
  • the invention also applies to an engine having, as the only group of cylinders, group 12A, and also at a engine for which only two distribution grooves, respectively permanently connected to one and the other of the main conduits, are provided between the distributor and the distribution cover.
  • Distribution ducts are made in the distributor and open into a radial distribution face 28 of the latter, pressing against a radial communication face 30 of the cylinder block.
  • Distribution lines selectively connect the grooves 20, 21 and 22 on the distribution face.
  • a distribution duct 31 has been shown which connects the groove 21 to the distribution face 28, and a conduit distribution 32 which connects the groove 22 to the distribution face.
  • Each cylinder is associated with a cylinder duct, which allows it to be connected to the communication face 30 of the cylinder block, in order to put it in communication alternately with each of the distribution during the relative rotation of the cylinder block by compared to the cam.
  • a cylinder duct 15B directly puts this cylinder in communication with the communication face 30.
  • the communication of cylinder ducts 15A with the communication face 30 operates via a clutch selector 34.
  • the selector 34 is formed by an axially movable drawer in a central bore 36 of the cylinder block.
  • the selector is integral with the cylinder block with respect to the rotation about the axis 10. It has in fact a flange portion 34 'provided with holes in through which the screw rods 38 pass. These rods have, each, a threaded end portion 39A screwed into a thread of the cylinder block, and a smooth intermediate portion 39B, with which cooperates the drilling of the flange 34 'in which the rod is engaged considered.
  • the selector 34 can slide relative to the screws 38.
  • the external cylindrical face 34A of the selector 34 cooperating with the bore 36 of the cylinder block has as many conduits communication in the form of grooves 40 that the first group of cylinders comprises cylinders, each groove 40 being associated with a cylinder duct 15A.
  • Each cylinder conduit 15A has one end connected to cylinder 12A and another end forming an orifice 15'A which is open in the bore 36 of the cylinder block. This orifice 15'A is in permanent communication with the groove of communication 40 associated with the cylinder duct 15A considered.
  • Each 15A cylinder duct is associated with a passage distribution formed by a conduit 42 which has a first orifice 42A open in the bore 36 of the cylinder block and a second orifice 42B open on the communication face 30 of the cylinder block. As seen in Figure 1, this allows connect the distribution passage 42 to the distribution conduits such as conduit 32.
  • the cylinder duct 15A and the distribution passage 42 therefore both open into bore 36 and, as can be seen in FIG. 1, this makes it possible to communicate the conduit of cylinder 15A with the distribution conduits when the selector 34 occupies its first position.
  • the assembly formed by the conduit 15A, the communication groove 40 and the passage of distribution 42 forms a substantially U-shaped duct, connected to the face of communication 30 of the cylinder block.
  • the communication groove 40 extends substantially axially and its length is sufficient to connect the holes 15'A and 42A in the first position of the selector.
  • the end of the distribution passage 42 located on the side of cylinder 12A is closed by a plug 42C.
  • An intercommunication annular groove 44 is made in the bore 36 of the cylinder block 6. Depending on the displacement of the selector, this groove 44 can be placed in communication with the communication grooves 40. Indeed, considered in the sense moving the selector from its first position to its second position, the orifice 42A, the orifice 15'A and the groove 44 are arranged one after another.
  • the engine of FIG. 1 also includes a system of braking 100 including two sets of brake discs respectively secured to the rotor and the stator, as well as a device brake piston 102 controlled between a configuration of braking, in which he presses the discs against each other others, and a brake release configuration.
  • a system of braking 100 including two sets of brake discs respectively secured to the rotor and the stator, as well as a device brake piston 102 controlled between a configuration of braking, in which he presses the discs against each other others, and a brake release configuration.
  • FIG. 2A shows, in partial axial section, the selector drawer 34 in its first position, the openings 15'A and 42A of the cylinder duct 15A and the distribution passage 42 considered being interconnected by the communication groove 40.
  • FIG. 3A shows, in strong lines, part of the developed from bore 36 and, in thin line, a corresponding part of the developed of the external cylindrical face 34A of the drawer 34.
  • the orifice 15'A of the cylinder duct 15A and the first port 42A of the passage of distribution 42 we also see the position of the intercommunication groove 44.
  • the communication grooves 40 respectively associated with each of the cylinder ducts taken into account on the Figure 3A are shown in thin lines.
  • the end face 34B of the drawer 34 next to the groove 44 has axial notches 34C. As it can be seen in FIG. 3A, these notches allow, even in the first position of the selector 34, the communication of the intercommunication groove 44 with a decompression 46 which will be described below.
  • the orifices 15'A and 42A therefore communicate with the communication groove 40, but are isolated from the throat 44.
  • the communication between the passage of distribution 42 and the communication groove 40 is then ensured by a maximum section S1.
  • the drawer 34 has started its moving to its second position.
  • the orifice 42A of distribution passage 42 no longer communicates with the communication groove 40 only by a smaller section S1 while the communication groove 40 begins to communicate with the groove 44 by a section S2.
  • the cylinders of the first group continue to be connected to the conduits of distribution of the distributor, but only through section S1. Through therefore, the pistons of these cylinders only contribute weakly at engine torque.
  • the set of conduits of cylinder 15A of the cylinders of the first group 12A constitutes, with the set of communication grooves 40 and the groove 44, a closed enclosure, isolated, in particular, from supply conduits, exhaust or any conduits carrying pressure control auxiliary.
  • the pistons of the cylinders of the first group can however move according to their positions relative to the cam without being blocked, since the cylinder of the cylinders of the first group are not closed but are all linked to the aforementioned enclosure.
  • this compression chamber constitutes an advantageous variant, but which must also be provided, in the second position of the selector, to communicate the communication grooves 40 directly with a return of leaks or, in general, with a fluid discharge.
  • the graph in Figure 4 shows the evolution of the sections S1, S2 and S3 during the movement of the drawer 34 from its first position (displacement 0) to its second position (displacement X). It can be seen that the passage section S1 decreases regularly until it becomes zero for a displacement X2. The section S2 has started to take a non-zero value from a displacement X1 less than the displacement X2. The Figures 2B and 3B correspond to a displacement value intermediate between the values X1 and X2. Then when the movement continues, section S2 continues to increase, and the section S3 starts to take a non-zero value from a displacement X3 greater than displacement X2.
  • the minimum distance d (see Figure 3A), measured in the direction of movement of the selector 34, between the first orifice 42A of the conduit forming the distribution passage 42 associated with a given cylinder conduit 15A and intercom groove 44 is less than the length L of the communication groove 40 associated with this cylinder duct. This provides the situation Figures 2B and 3B.
  • the invention provides for not allowing this connection only via a calibrated valve 52 located in a connecting pipe between space 50 and the return pipe of leaks 48.
  • the selector 34 is disposed in the bore 36 of the cylinder block and it is preferably coaxial with the axis of rotation 10.
  • Des means for controlling its movement include elastic return means such as a spring 54 able to stress in permanently the selector 34 to its first position.
  • this spring 54 is supported, on the one hand, on the radial face 5A of the shaft 5 which is situated on the side of the distributor 16 and, on the other hand, on a radial surface 34C of the drawer 34 opposite to said radial face 5A.
  • the spring 54 is partially housed in a central recess 56 of drawer 34, one end portion of which forms said surface 34C.
  • Means for controlling the movement of the selector 34 further comprise a control piston 58 cooperating with a control cylinder 60 secured to a stator part of the engine, in this case the distribution cover 1A.
  • the cylinder 60 is formed in the stator of the engine, and the piston 58 is also fixed with respect to rotation about the axis 10.
  • the selector 34 is integral in rotation with the cylinder block.
  • FIGS. 5A to 5B show various variants of production of the zones in contact with the selector piston, such as to limit premature wear, which could however result from this relative rotation.
  • the active head 58A of the piston 58 is equipped with a spherical stop means.
  • a ball 59 set in a recess 59A made at the end of the piston.
  • this ball cooperates directly with the radial face 34'A of the selector facing it.
  • the ball 59 can be replaced by a screw or the like whose head has a surface constituting a portion of a sphere.
  • the spherical surface is formed on the face 34'A of the selector.
  • the control piston 58 ′ has a active head 58'A which is connected to the body of this piston by rolling means 70.
  • the head 58'A cooperates with the selector 34 via a piece of contact 72 formed for example by the head of a screw screwed in this selector 34.
  • the head 58'A and this part 72 may have a hardness superior to that of other parts and / or a coating specific to limit friction.
  • the control piston 58 "cooperates with selector 34 via hydrostatic stop using a confined fluid.
  • the active head 58 "A of the hollow piston 58" is formed by an additional part, held in position by relation to the piston by the fluid pressure prevailing in an enclosure hydrostatic stop valve 74.
  • This enclosure is connected to the control chamber 62 mentioned above by a passage having a restriction 76 produced at the end of the hollow piston 58 "which is opposite the head 58 "A and by a hole 79 made in the head 58 "A which connects the enclosure 74 to the recess of the piston 58".
  • the head 58 "A cooperates with the selector 34 by through an additional contact piece 72 'attached to said selector.
  • the decompression chamber 46 is provided at the end 34B of the selector which is on the downstream side of the latter in the direction of its movement from its first position to its second position. This room is thus provided between the selector 34, the cylinder block 6 and the shaft 5A, the connections between these parts being made substantially waterproof. In the second position of the selector 34, the cylinder ducts 15'A of the cylinders of the first group are connected to this chamber of decompression.
  • the communication grooves 40 are in communication with the chamber 46 in the second position of the selector. So when, during movement of the selector from its first position to its second position, the cylinder ducts 15'A begin to be put in communication with the room 46, this one is supplied by the fluid contained in these conduits. Therefore, the fluid pressure in the chamber 46 increases, and this pressure opposes, to the control of the movement operated by the piston 58, a antagonistic hydraulic force. So from this implementation communication between the conduits 15'A and the chamber 46, the movement of the selector 34 to its second position is slowed down, so that the section S3 increases very gradually, and that the pistons of the cylinders of the first group are disengaged "in sweetness. "
  • the decompression chamber 46 is in communication with the aforementioned leakage return line 48.
  • this communication is carried out through at least one passage of small section.
  • Passage of weak section it is necessary include a passage through which the fluid flow is relatively small, so as to cause a difference in pressure (pressure drop) between chamber 46 and the supply line return of leaks 48.
  • the passage or passages of small section are formed by holes 78 passing axially through the selector 34.
  • the ends of these holes are in the support area of the spring 54 on the bottom of the recess 56, they can be machined without particular precaution as for their section, and it is the presence of springs which decrease their cross section.
  • the passages 78 open into a space 80 of the engine formed between the piston 58 and an internal bore 16A of the distributor, space 80 to which the return line from leaks 48.
  • the decompression chamber 46 is in communication with the interior space 50 of the engine located under the reaction member 4A via a non-return valve 82 which authorizes only the circulation of fluid in the direction of emptying of this bedroom.
  • a non-return valve 82 which authorizes only the circulation of fluid in the direction of emptying of this bedroom.
  • the leak return pipe 48 comprises a first section 48A which is connected to the space 80, and therefore, via passages 78, to the decompression 46, a second section 48B in which is located the non-return valve 82, a third section 48C in which finds the calibrated valve 52 which, when the pressure in the space 50 is higher than its calibration pressure, allows the circulation of the fluid only in the direction from space 50 to line 48.
  • the engine comprises the cylinders 12B belonging to a second group, cylinders in which pistons 14B slide.
  • the conduits cylinder 15B of these cylinders 14B open into the face of communication 30 of the cylinder block 6 to be alternately put in communication with distribution conduits such as conduits 31 and 32, during the relative rotation of the cylinder block and from the distributor.
  • the engine has a displacement selection device separate from the selector 34.
  • This device is located in the distribution cover 1A, in the zone Z indicated in figure 1 but it is not represented in figure 1 insofar as it is not in the section plane of this figure.
  • this selection device displacement does not cooperate with cylinder ducts, but with the distribution grooves 20, 21 and 22. It indeed has a axial bore 88 in which three grooves 90, 91 and 92 which are in permanent communication with each of the three distribution grooves 20, 21 and 22.
  • a drawer 94 is movable inside this bore 88 and has a groove or analog 96. In a first position of the drawer, the groove 96 is communicate the gorges 90 and 91 (so it also communicate between them the grooves 20 and 21) while, in the second position of the drawer, its groove 96 communicates the grooves 91 and 92 (and therefore the gorges 21 and 22).
  • Distribution conduits are divided into three groups respectively connected to each of the three grooves 20, 21 and 22.
  • the number of conduits in the third group, which are connected to groove 22 is equal to the sum of the number of conduits of the first group and the number of conduits of the second group.
  • the first position of the drawer 94 shown in Figure 6 is a large displacement position, in which the ducts of the first and second groups are connected to the duct main 24 and isolated from the ducts of the third group, while the conduits of the third group are connected to the main conduit 26 and isolated from those of the other two groups.
  • the cylinder ducts 15B and the ends 42B of distribution passages 42 pass alternately opposite a distribution duct belonging to the third group then next to a distribution duct belonging to one of the first and second groups.
  • the pistons of the cylinders of the first group are disengaged.
  • the orifices of the cylinder ducts 15B cylinders of the second group continue to be put alternately in communication with a distribution conduit connected to the power supply then with a distribution conduit connected to the fluid exhaust, so that all the pistons of the cylinders of the second group are active.
  • the engine then operates with a partial displacement, equal to the entire cylinder displacement from the second group.
  • the groove 90 In the second position of the drawer 94, the groove 90 is isolated, while the gorges 91 and 92 communicate with each other.
  • the distribution pipes of the second and third groups are all related to driving main 26, by connecting gorges 91 and 92. Therefore, only the cam lobes that correspond to the distribution conduits 20 of the first group are active, since the pistons which, at a given moment, cooperate with these cam lobes are alternately connected to a distribution duct of the first group connected to groove 20, then to a distribution duct of the second to third groups which is connected to the main duct 26.
  • the motor has four separate displacement capacities.
  • the drawer 94 is controlled between its two positions by control means comprising a control chamber 98 capable of being connected to a control conduit by an orifice 100, and a spring 102 of effect antagonistic to that of the increase volume of the room.
  • control means comprising a control chamber 98 capable of being connected to a control conduit by an orifice 100, and a spring 102 of effect antagonistic to that of the increase volume of the room.
  • the chamber 98 is delimited by a closing washer 104 reported in bore 88.
  • the motor according to the invention may include a tachometer 106 comprising a sensor 108 which counts the number of passes, the right of its end, of marks 110 practiced at regular intervals on the radial face of the cylinder block located on the side of the distribution cover 1A.
  • Figure 7 also shows a device for selecting displacement, which is separate from the piston clutch selector and which includes a drawer 124 movable inside a bore 118.
  • the drawer is represented in each of its two positions, respectively on either side of the A118 axis of this bore.
  • the distribution conduits are divided into four groups, respectively connected to each of four grooves 120 to 123 of the distributor 116, themselves respectively in permanent communication with each of four grooves 130 to 133 of bore 118.
  • the drawer 124 has two grooves 125 and 126 which, depending on its position, communication or isolate the gorges 130 to 133 and therefore the conduits of distribution.
  • the grooves 130 and 131 are connected together and isolated from grooves 132 and 133, themselves connected together.
  • the distribution conduits connected to grooves 120 and 121 are connected at the same pressure main (supply or exhaust), while the distribution connected to the gorges 122 and 123 are at the other pressure main (exhaust or supply).
  • the grooves 130 and 133 are each isolated from the other grooves in bore 118, while the grooves 131 and 132 are connected.
  • Distribution pipes connected to grooves 120 and 123 are respectively placed at each of the two main pressures and correspond to an active displacement. In however, the distribution conduits connected to grooves 121 and 122 are at the same pressure and correspond to an inactive displacement.
  • the drawer 124 has an internal bore 134 in which there is a shuttle 135. Holes 136 to 139 of the drawer communicate with this internal bore 134.
  • the shuttle 135 allows to order a communication of these holes 136 to 139 for, in small displacement, automatically connect grooves 131 and 132 (and therefore the grooves 121 and 122 corresponding to an inactive displacement) to that of the gorges 130 or 133 which contains the weakest fluid pressure.
  • This shuttle device and its advantages are described in detail in patent FR 2 481 755.
  • the selector 234 can, depending on whether it occupies one or the other of its first and second positions, put the conduits cylinder 15A in communication with the passages of communication 42 or isolate them from these passages.
  • the selector 234 is formed by a hollow drawer, inside which extends a rod 250 which, in this case, is centered on the axis 10 of the motor on which the selector 234 is also centered.
  • the rod 250 constitutes a "reference part" which is fixed in translation by compared to cylinder block 6. More specifically, a retaining flange 252 is fixed to the cylinder block 6 by screws 253 and the rod 250 crosses this flange and is wedged with respect to it by a shoulder and an elastic wedging ring.
  • the selector 234 is permanently recalled to its second position (visible below axis 10) by a spring 254 which rests on the flange 252. It is biased towards its first position (visible above axis 10) by counter-force means which include a control chamber 262 formed between said selector 234 and the rod 250. More precisely, the rod wears a closure ring 264 at its end opposite the flange 252 and the chamber 262 is formed between a recess 266 of the internal periphery of the selector 234, the rod 250 and the ring 264.
  • the selector movement control duct 234 comprises a first section 268 which is formed in the rod 250 so as to lead into chamber 262, and a second section 270 which is formed in a part 1'A of the motor housing.
  • the sections 268 and 270 are connected by the arrangement of the rod 250 in correspondence with section 270 and are isolated from the rest of the motor by a seal 272 disposed between the 250A tail of the rod and the housing part 1'A, against which this seal is held supported by a spring 274.
  • This seal is of the "rotating joint" type, ensuring a rotary seal between two rotating parts relative.
  • the decompression chamber 46 is connected to the space 280, which is formed between the flange 252 and the housing part 1'A and to which the leakage return pipe 248 is connected.
  • the selector 234 has at least one axial hole 278 which connects the chamber 46 at the end of the selector located on the side of the flange 252 and the latter has at least one bore or slot 282 which opens onto space 280.
  • it is an axial slot 282 which cooperates with a key 284 to guide the movement of the selector 234 between its two positions.
  • selectors 34 and 234 differ in the means of control of their movement. For the rest, their functioning is analogous.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP20000401985 1999-07-27 2000-07-10 Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung Expired - Lifetime EP1072791B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9909714 1999-07-27
FR9909714A FR2796992B1 (fr) 1999-07-27 1999-07-27 Moteur hydraulique a pistons radiaux et a selecteur de debrayage unique

Publications (3)

Publication Number Publication Date
EP1072791A2 true EP1072791A2 (de) 2001-01-31
EP1072791A3 EP1072791A3 (de) 2001-04-11
EP1072791B1 EP1072791B1 (de) 2004-06-09

Family

ID=9548553

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000401985 Expired - Lifetime EP1072791B1 (de) 1999-07-27 2000-07-10 Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung

Country Status (5)

Country Link
US (1) US6347572B1 (de)
EP (1) EP1072791B1 (de)
JP (1) JP4657425B2 (de)
DE (1) DE60011352T2 (de)
FR (1) FR2796992B1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014014984A3 (en) * 2012-07-18 2014-07-31 Eaton Corporation Combined motor and brake with rotating brake-release piston
WO2014014985A3 (en) * 2012-07-18 2014-07-31 Eaton Corporation Freewheel hydraulic motor
US10781816B2 (en) 2017-04-13 2020-09-22 Eaton Intelligent Power Limited Hydraulic motor brake

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2819024B1 (fr) * 2000-12-28 2003-08-15 Poclain Hydraulics Ind Dispositif de moteur hydraulique ayant un selecteur de cylindree et un systeme de freinage
FR2834012B1 (fr) 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR2846381B1 (fr) * 2002-10-29 2005-01-28 Poclain Hydraulics Ind Mecanisme hydraulique ayant des cylindres a communications multiples
FR2891593B1 (fr) * 2005-10-03 2007-12-21 Poclain Hydraulics Ind Soc Par Dispositif de gestion de la cylindree d'un moteur hydraulique
WO2010052743A1 (en) * 2008-11-10 2010-05-14 S.A.I. Società Apparecchiature Idrauliche S.p.A. Hydraulic motor with radial cylinders provided with rotation speed detection
DE102013206730A1 (de) 2012-04-28 2013-10-31 Robert Bosch Gmbh Radialkolbenmotor mit Bremse
JP6074499B2 (ja) * 2012-06-25 2017-02-01 ボルボ ラストバグナー アーベー デュアルクラッチ変速機
WO2016081354A1 (en) * 2014-11-17 2016-05-26 Eaton Corporation Hydraulic device with sleeve insert

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FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation
FR2677409A1 (fr) * 1991-06-10 1992-12-11 Poclain Hydraulics Sa Circuit hydraulique d'alimentation d'au moins un moteur hydraulique a pistons "debrayables".
FR2710111A1 (fr) * 1993-09-15 1995-03-24 Poclain Hydraulics Sa Moteur hydraulique muni d'un dispositif de sélection de sa cylindrée active.
WO1995031641A1 (en) * 1994-05-18 1995-11-23 Valmet Voimansiirto Oy Radial-piston hydraulic motor and method for regulation of a radial-piston hydraulic motor

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GB1603116A (en) * 1977-04-29 1981-11-18 Massey Ferguson Services Nv Hydrostatic transmissions
US4401182A (en) * 1980-12-10 1983-08-30 Sundstrand Corporation Variable displacement hydraulic drive with disconnect
US4461188A (en) * 1981-12-23 1984-07-24 Ford Motor Company Dual clutch multiple countershaft transmission
JP2716543B2 (ja) * 1989-09-18 1998-02-18 株式会社クボタ 車輌の走行駆動構造

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Publication number Priority date Publication date Assignee Title
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation
FR2677409A1 (fr) * 1991-06-10 1992-12-11 Poclain Hydraulics Sa Circuit hydraulique d'alimentation d'au moins un moteur hydraulique a pistons "debrayables".
FR2710111A1 (fr) * 1993-09-15 1995-03-24 Poclain Hydraulics Sa Moteur hydraulique muni d'un dispositif de sélection de sa cylindrée active.
WO1995031641A1 (en) * 1994-05-18 1995-11-23 Valmet Voimansiirto Oy Radial-piston hydraulic motor and method for regulation of a radial-piston hydraulic motor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014014984A3 (en) * 2012-07-18 2014-07-31 Eaton Corporation Combined motor and brake with rotating brake-release piston
WO2014014985A3 (en) * 2012-07-18 2014-07-31 Eaton Corporation Freewheel hydraulic motor
US9175563B2 (en) 2012-07-18 2015-11-03 Eaton Corporation Combined motor and brake with rotating brake-release piston
US9551222B2 (en) 2012-07-18 2017-01-24 Eaton Corporation Freewheel hydraulic motor
US10781816B2 (en) 2017-04-13 2020-09-22 Eaton Intelligent Power Limited Hydraulic motor brake

Also Published As

Publication number Publication date
DE60011352T2 (de) 2005-06-30
DE60011352D1 (de) 2004-07-15
EP1072791A3 (de) 2001-04-11
FR2796992B1 (fr) 2001-10-19
EP1072791B1 (de) 2004-06-09
US6347572B1 (en) 2002-02-19
FR2796992A1 (fr) 2001-02-02
JP2001107836A (ja) 2001-04-17
JP4657425B2 (ja) 2011-03-23

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