WO1999020899A1 - Pompe ou moteur hydraulique - Google Patents

Pompe ou moteur hydraulique Download PDF

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Publication number
WO1999020899A1
WO1999020899A1 PCT/JP1998/004732 JP9804732W WO9920899A1 WO 1999020899 A1 WO1999020899 A1 WO 1999020899A1 JP 9804732 W JP9804732 W JP 9804732W WO 9920899 A1 WO9920899 A1 WO 9920899A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
shoe
cylinder block
hydraulic pump
contact
Prior art date
Application number
PCT/JP1998/004732
Other languages
English (en)
Japanese (ja)
Inventor
Jun Inoue
Takashi Teraoka
Takashi Itou
Eizou Urata
Original Assignee
Kayaba Kogyo Kabushiki Kaisha
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kayaba Kogyo Kabushiki Kaisha filed Critical Kayaba Kogyo Kabushiki Kaisha
Priority to DE69838260T priority Critical patent/DE69838260T2/de
Priority to EP98947948A priority patent/EP1030057B1/fr
Priority to DK98947948T priority patent/DK1030057T3/da
Publication of WO1999020899A1 publication Critical patent/WO1999020899A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis

Definitions

  • the present invention relates to a hydraulic rick axial piston pump or motor, and more particularly to an improvement in a mounting structure of a piston and a shoe. Background of the Invention
  • a component force in the direction perpendicular to the piston axis that is, a lateral force (lateral force) acts on the piston as a reaction force in accordance with the inclination of the swash plate. Large frictional force is generated on the sliding surface.
  • No. 8-1519975 proposes a structure in which a piston and a shoe are in contact with each other on a plane perpendicular to the axis of the piston.
  • the shoe when the shoe is held by the relatively weak spring force as described above, the following problem may occur. For example, if there is poor lubrication or foreign matter between the rotary table member and the shaft that supports the shaft, the pressing force of the piston against the shaft will be weak, especially when the cylinder pressure is low on the suction side. . For this reason, the shoe cannot be pressed firmly, and the shoe floats up, causing a one-sided contact with the piston. At this time, the contact surface of the shoe may be damaged. Also, when the cylinder pressure rises to the discharge side, the shoe is pushed strongly by the piston, so that the one-sided contact state returns to the normal surface contact, but at this time, a collision noise is generated.
  • an object of the present invention is to allow a slight sliding on the contact surface between the piston and the shoe, and to reliably prevent such separation. Disclosure of the invention
  • a hydraulic pump or a motor includes a rotating disk member rotatably supported with respect to a housing, and a rotating shaft tilted with respect to a rotating shaft of the rotating disk member.
  • a cylinder block rotatably supported in space.
  • a plurality of cylinder bores are arranged on a concentric circle centered on the rotation axis of the cylinder block, and a piston is slidably accommodated in each of the cylinder bores.
  • a hemispherical shoe having a smooth surface in contact with the rotating plate member through a spherical surface and in contact with the piston on the opposite side is provided.
  • a valve plate fixed to the housing that slides into and out of each cylinder bore in accordance with the rotation of the cylinder block is provided on the bottom surface of the cylinder block.
  • a joint is provided for connecting the rotary disk member and the cylinder block to each other and rotating them synchronously, and the rotary disk member or the cylinder block is connected to a drive shaft.
  • a coupling means is provided for connecting the piston and the shoe so as to be slidable in a direction along the contact surface of each other and so as not to relatively move in a direction in which the piston and the shoe are separated from each other.
  • an urging means for urging the contact surfaces of the piston and the shoe in a direction in which the contact surfaces are in close contact with each other.
  • the connecting means is constituted by a connecting rod for connecting the shoe and the piston, and a flange portion at a distal end of the connecting rod penetrating a through hole provided in the piston is locked inside the piston, and a connecting rod base end is connected to the connecting rod.
  • a predetermined gap is provided between the inner periphery of the through hole and the outer periphery of the connecting rod.
  • the urging means is preferably configured by a panel member or a ring-shaped elastic member interposed between the flange at the tip of the connecting rod and the inside of the piston.
  • the coupling means includes a storage space formed in the shoe, and a large-diameter portion provided in a piston housed in the storage space, and is provided between an inner periphery of the storage space and an outer periphery of the large-diameter portion. A predetermined gap is formed.
  • the urging means is preferably configured by a spring member or a ring-shaped elastic member interposed between the storage space and the large diameter portion.
  • the coupling means is a rod extending integrally from the shoe and penetrating through a through hole formed in the piston, a screw portion provided at the tip of the rod, and a nut screwed into the screw portion.
  • the urging means forming a predetermined gap between the inner periphery of the through hole and the outer periphery of the rod is preferably constituted by an elastic member interposed between the nut and the inside of the piston.
  • a force in the axial direction of the piston acts on the piston as a reaction force from the shoe according to the inclination between the turntable member and the cylinder block and the internal pressure of the cylinder at that time.
  • Shuichi is in contact with the piston on a smooth surface orthogonal to its axis, no force is generated in the direction parallel to the contact surface, and little lateral force acts on the piston. .
  • the friction between the piston and the cylinder bore becomes very small, and wear on the piston sliding surface can be reduced.
  • the rotation axis of the cylinder block is tilted from the rotation axis of the turntable member, the circular orbit drawn by the shoe around the drive shaft slightly deviates from the circular orbit drawn by the cylinder block, that is, the piston.
  • smooth operation can be maintained.
  • the shoe is connected to the piston via a connecting means, and is securely connected to the piston even on the suction side where the pressing force from the piston is weak, so that the shoe does not float up and the piston is connected to the piston.
  • the contact surface does not wear due to one-sided contact, and no collision noise is generated when it moves to the discharge side.
  • FIG. 1 is an overall sectional view showing a first embodiment of the present invention.
  • FIG. 2 is an enlarged cross-sectional view showing a part thereof in detail.
  • FIG. 3 is a sectional view showing a part of the second embodiment.
  • FIG. 4 is a sectional view showing a part of the third embodiment.
  • FIG. 5 is a sectional view showing a part of the fourth embodiment.
  • FIG. 6 is a sectional view showing a part of the fifth embodiment.
  • FIG. 7 is a sectional view showing a part of the sixth embodiment.
  • FIG. 8 is a sectional view showing a part of the seventh embodiment.
  • FIG. 9 is a sectional view showing a part of the eighth embodiment.
  • FIG. 10 is a sectional view showing a part of the ninth embodiment.
  • FIG. 11 is a sectional view showing a part of the tenth embodiment. Preferred embodiment
  • the present invention is applied to an axial piston pump.
  • a pump housing 11 is formed between a side block 11A on both sides and a port block 11B. Case 1 1 C is sandwiched.
  • a pump drive shaft 12 penetrating through the side block 11 A is rotatably supported by a bearing 13.
  • a cylinder block 14 is arranged in the internal space of the pump housing 11. Centered on cylinder block 14, supported by port block 1 1B The rotating shaft 15 thus inserted is inserted via the bearing 16, whereby the cylinder block 14 rotates around the rotating shaft 15.
  • the cylinder block 14 is inclined at a certain angle with respect to the drive shaft 12 so that the pump drive shaft 12 and the rotary shaft 15 intersect each other.
  • the drive shaft 12 and the cylinder block 14 are connected via a joint 17.
  • the joint 17 has a spline hole 17 A formed in the end face of the drive shaft 12 and a spline hole 17 B also formed in the center of the end face of the cylinder block 14, and spline heads at both ends of the joint 17. 17 C is in spline engagement.
  • the outer periphery of the spline head 17C is formed as a spherical surface, so that even if the axis of the spline hole 1778 and the axis of 17B intersect, good engagement is always maintained, and the drive shaft 12 and cylinder Rotation can be transmitted to block 14.
  • a plurality of cylinder pores 18 are formed in the cylinder block 14 on a concentric circle centered on the rotation axis 15 so as to be equidistant from each other and the axis is parallel to the rotation axis 15. .
  • the pistons 20 are slidably housed in the cylinder bores 18, respectively.
  • Each piston 20 is urged in the extension direction by a coil spring 21 arranged in a cylinder pore 18.
  • a spring support 22 is arranged inside the spring 21 to prevent the spring 21 from bending.
  • the spring supporter 22 is located inside the hollow piston 20 and has an end fixed to prevent buckling of the spring 21 and prevent the spring 21 from contacting the inner periphery of the piston 20.
  • the spring supporter 22 is formed of a material having low friction.
  • a tubular piston cap 23 made of a synthetic resin (engineering plastic) is fitted around the outer periphery of the piston 20 and fixed by bonding or the like. As a result, the friction of the sliding surface with the cylinder bore 18 is reduced.
  • the piston cap 23 has at least the length of the effective stroke range of the piston 20, and the flange 23 A at the tip engages the inside of the hollow piston 20.
  • the piston cap 23 is made of a polymer material having a small coefficient of friction, and a reinforcing material such as carbon fiber may be added as necessary.
  • the valve plate 25 that contacts the bottom of the cylinder block 14 is fixed to the port block 11B.
  • the valve plate 25 is provided with a pair of kidney ports (not shown) on the suction side and the discharge side, and is provided through the cylinder block 14 from the bottom of each cylinder bore 18 by rotation of the cylinder block 14. Port 18 A is connected sequentially.
  • a discharge passage and a suction passage (not shown) connected to these kidney ports are formed inside the port block 11B.
  • the tip of the piston 20 is formed with a plane 2 OA perpendicular to the axis, into which a pad 27 made of a synthetic resin having a small coefficient of friction is fitted. ing.
  • a convex portion 27A is provided on the back surface of the pad 27, and the convex portion 27A fits into a hole of the piston 20.
  • a through hole 27B is formed at the center of the projection 27A, and communicates with the inside of the piston.
  • a pocket 27D is formed in the flat support surface 27C of the pad 27, and the internal pressure of the cylinder is guided through the interior of the piston.
  • a hemispherical shoe 29 that is in contact with the pad 27 is provided.
  • the shoe 29 is supported on the side block 11 A side by a socket 32 fitted to a torque plate 31 as a rotating disk member disposed around the pump drive shaft 12.
  • Each of the sockets 32 is formed of a synthetic resin having a small coefficient of friction as described above, and is fitted into a recess 31 A formed in the torque plate 31.
  • the socket 32 is provided with a hemispherical recess 32A, and the spherical surface 29B of the shoe 29 is rotatably accommodated in the recess 32A.
  • the diameter of the smooth surface 29 A of the shoe 29 is slightly larger than or substantially equal to the diameter of the support surface 27 C of the pad 27, and these smooth surface 29 A and the support surface 27 C Are in surface contact with each other.
  • This contact surface has a pocket 27D inside the piston as described above.
  • the fluid pressure in the section is guided, and a hydrostatic bearing is formed between the shoe 29 and the pad 27 by fluid, receiving a load by the fluid pressure and minimizing mutual wear.
  • a through hole 29C is formed in the shower 29 from the smooth surface 29A to the spherical surface 29B, and a pocket 29D formed in a part of the spherical surface 29B is provided with the pad 27
  • the fluid is guided from the pocket 27D to form a fluid bearing in the same manner as above, reducing friction between the contact surfaces.
  • a connecting rod 40 for connecting the piston 20 and the shoe 29 is provided.
  • the connecting rod 40 allows a slight movement in the direction of the contact surface between the piston 20 and the shoe 29, and connects the piston 20 and the shoe 29 so as not to move in the separating direction. It is inserted into the through hole 29 B of the pad 27 fitted in the through hole 29 C of the hole 29 and the through hole 20 B of the piston 20.
  • a flange portion 41 is formed at the distal end of the connecting rod 40, and the flange portion 41 abuts on the springer sheet 42 inside the piston 20, while the flange portion 41 is provided at a base end of the connecting rod 40.
  • the screw portion 43 is screwed into a screw hole formed on the inner periphery of the through hole 29 of the screw 29.
  • the spring seat 42 is formed in a part of the spring supporter 22.
  • a stepped portion 45 is formed in the middle of the connecting rod 40, and the connecting rod 40 is screwed until the stepped portion 45 comes into contact with the shoe 29, thereby positioning the connecting rod 40.
  • a small gap is formed between the inside of the flange portion 41 and the spring seat 42.
  • a predetermined gap is provided between the outer periphery of the connecting rod 40 and the inner periphery of the through hole 27 B of the pad 27, whereby the shoe 29 and the piston 20 move in the direction of the contact surface. It is possible, and it can hardly move in the axial direction of the piston.
  • a fluid passage 46 penetrates the axis of the connecting rod 40, and a branch passage 47 extending in the radial direction is provided in the middle of the passage.
  • the working fluid from the hollow portion of the piston is guided to the contact surface with the shoe 29 via the fluid passage 46.
  • it is also guided to the contact surface between the shell 29 and the spherical recess 32A of the socket 32, lubricating the contact surface, and further guiding the fluid to the hydrostatic bearing.
  • the torque plate 31 engages with a spline portion 12 A provided on the outer periphery of the pump drive shaft 12 with a central spline hole 3 1 B, whereby the torque plate 31 is integrated with the drive shaft 12. Rotate. Therefore, in the end, the torque plate 31 rotates in the same direction as the cylinder block 14 in the same direction. Therefore, the shaft 29 supported by the socket 32 of the torque plate 31 and the piston 20 contacting the pad 29 via the pad 27 always maintain the same positional relationship with each other while the drive shaft 1 2 Around the same circumference.
  • the torque plate 31 is housed in a circular recess 33 provided around the drive shaft 12 provided in the side block 11A.
  • a disc-shaped thrust plate 35 is disposed on the bottom surface of the torque plate 31.
  • the thrust plate 35 which is also formed of a synthetic resin having a small friction coefficient, is fixed to the side block 11A.
  • a pocket 31 C is formed on the sliding surface with the thrust plate 35, and the fluid pressure is guided to this. This fluid pressure is applied to the pocket 31 from a portion of the fluid bearing of the shoe 29 through a through hole 32 C provided in the socket 32 and a through hole 31 D provided in the torque plate 31. Guided to C.
  • the contact surface between the torque plate 31 and the thrust plate 35 is supported by the fluid bearing, and sliding friction is reduced.
  • a bush 36 made of a synthetic resin having a small coefficient of friction is arranged on the outer periphery of the torque plate 31, and a pressurized fluid is provided on a sliding surface between the outer periphery of the torque plate 31 and the inner periphery of the bush 36.
  • a pressure introduction passage 37 communicating with the pump discharge passage is formed inside the side block 11 A, and is applied to the pocket 36 A provided on the sliding surface of the bush 36 and the torque plate 31. Guide the pressurized fluid.
  • the piston 20 In the process of moving away from the position where the mutual distance is the closest, the piston 20 is pushed and extended by the spring 21 while maintaining contact with the shoe 29, and operates through the port 18A to the cylinder bore 18 Inhale fluid.
  • the piston 20 In the process of approaching from the farthest position, the piston 20 is pushed in by the shoe 29, and discharges the fluid inside the cylinder bore 18 from the port 18A. These fluids are sucked from the suction passage by the action of the valve plate 25 and discharged to the discharge passage. In this way, the rotation of the cylinder block 14 causes the piston 20 to be held in the torque plate 31. It expands and contracts while making contact with 29 and repeatedly sucks and discharges working fluid into the cylinder bore 18 to function as an axial piston pump.
  • an axial force acts on the piston 20 in accordance with the pressure of the fluid in the cylinder pore 18, and this force is received by the torque plate 31 via the screw 29.
  • the torque plate 31 is not at a right angle to the axis of the piston 20 but is inclined at a certain angle, the reaction force from the shaft 29 causes a component force in a direction orthogonal to the axis of the piston 20.
  • the piston 20 and the shroud 29 are always in a plane perpendicular to the axis.
  • the support surface 27 C of the pad 27 fitted to the piston 20 and the smooth surface 29 A of the shoe 29 are fitted. Therefore, almost no force is generated from the cylinder 29 in the direction perpendicular to the axis of the piston 20, which is parallel to these contact surfaces. For this reason, the lateral force in the direction orthogonal to the axis is hardly applied to the piston 20, and the surface pressure of the sliding surface of the cylinder bore 18 becomes extremely small.
  • the rotation torque of the pump drive shaft 12 is transmitted to the cylinder block 14 via the joint 17, and the torque torque of the drive shaft 12 is similarly transmitted to the torque plate 31 via the spline portion 12 B.
  • the cylinder block 14 rotates the same as the torque plate 31, so that the piston 20 and the shoe 29 maintain the substantially same positional relationship around the pump drive shaft 12. Therefore, there is no relative torque difference in the circumferential direction due to this rotation, and no large lateral force acts on the piston 20 even by this.
  • the friction on the sliding surface between the piston 20 and the cylinder pore 18 mainly depends on the lateral force acting on the piston 20.Therefore, when the lateral force is reduced, the sliding friction force can be reduced accordingly. it can. Further, a cap 23 made of a synthetic resin is fitted around the outer periphery of the piston 20 to reduce the sliding resistance on the contact surface with the cylinder bore 18.
  • a pad 27 made of a synthetic resin having a small friction is interposed between the piston 20 and the bush 29 to avoid metal contact between the piston 20 and the bush 29.
  • a pad 27D is formed in the pad 27, in which the internal pressure of the cylinder bore 18 is guided through the interior of the piston 20, and a hydrostatic bearing is provided between the contact surface of the pad 27 and the shoe 29. Is composed. For this reason, the contact pressure of each other can be reduced by the fluid pressure, and the wear thereof can be reduced.
  • the contact pressure between the pad 27 and the shoe 29 is high when the piston 20 is in the discharge stroke, and is low when it is in the suction stroke. Therefore, the pressure required for the hydrostatic bearing is high during the discharge stroke and low during the suction stroke. Since the internal pressure of the cylinder pore 18 is directly guided to the pocket 27 D through the piston 20, the internal pressure of the cylinder matches the fluid pressure of the pressure characteristic required for the hydrostatic bearing. Can function as a bearing it can.
  • a synthetic resin socket 32 is provided between the shoe 29 and the torque plate 31 so that the shoe 29 and the torque plate 31 are not directly in contact with each other as described above. Avoiding metal contact with each other. Further, the fluid pressure is guided to the spherical contact surface between the socket 32 and the shoe 29 via the pocket 27B, and a hydrostatic bearing is formed between the contact surfaces. Therefore, the mechanical contact of this sliding surface is reduced, and the wear is reduced.
  • the reaction force from the piston 20 acts on the torque plate 31 that rotates the same as the pump drive shaft 12, and the thrust is applied to the recess of the side block 11 A according to the inclination of the piston 20. Pressed radially and radially.
  • the torque plate 31 contacts the synthetic resin thrust plate 35 in the same direction as the rotation axis, that is, the thrust direction, and the synthetic resin bush 36 in the rotational radius direction, that is, the radial direction. Since they are in contact, metal contact on the sliding surface is avoided in any case. Furthermore, the fluid pressure is guided to the contact surface with the thrust plate 35 and the contact surface with the bush 36 to form a hydrostatic bearing, so that the mechanical contact force is reduced. As a result, the wear of the torque plate 31 is reduced, and its durability is enhanced.
  • the axis of the cylinder block 14 is inclined with respect to the axis of the torque plate 31, and the pistons 20 arranged in the cylinder block 14 form a circular orbit drawn by a shaft 29 rotating together with the torque plate 31. Therefore, the contact surface between the piston 20 and the shoe 29 slides with each other in order to draw an elliptical orbit slightly shifted. This sliding is allowed by the gap between the connecting rod 40 and the through hole 27B, and smooth operation is maintained.
  • the piston 20 and the shoe 29 are mutually connected by the connecting rod 40, and hardly move in the axial direction. For this reason, even when the pressing force between the cylinder 209 and the piston 20 on the cylinder suction side is weak, the cylinder 129 does not separate from the piston 20. did As a result, no noise is generated due to the collision.
  • FIG. 3 shows a second embodiment
  • the clearance between the flange portion 41 of the connecting rod 40 and the spring seat 42 is made slightly larger, and a disc spring 51 is interposed between the flange portion 41 and the spring seat 42. I am wearing it.
  • an annular step portion 42A is formed in the spring seat 42, and the flat panel 51 is fitted into the annular step portion 42A.
  • FIG. 4 shows a third embodiment.
  • a ring-shaped elastic member 52 is sandwiched between the flange portion 41 of the connecting rod 40 and the springer seat 42 of the piston 20 instead of the disc spring 51. It is.
  • the elastic member 52 for example, rubber or resin material is used.
  • FIG. 5 shows a fourth embodiment.
  • a coil spring 53 is interposed between the flange portion 41 and a receiving seat 20D on the inner wall of the piston 20. This also urges the shoe 29 so as to be in close contact with the piston 20 and reliably suppresses movement in the separating direction.
  • FIG. 6 shows a fifth embodiment.
  • This embodiment is provided with another connecting means instead of using the connecting rod 40 as in the above embodiments.
  • a cylindrical portion 54 extending in the axial direction is provided on the outer periphery of the shell 29 so as to be extended, and this cylindrical portion 54 is bent inward at a right angle to form a flange 54A, and a circular storage space is formed inside. 55 is formed, and the large-diameter portion 20C at the tip of the piston 20 is housed therein.
  • a predetermined gap is provided between the outer circumference of the piston large diameter portion 20 C and the inner circumference of the storage space 55, and the thickness of the large diameter portion 20 C and the height of the storage space 55 in the axial direction. A predetermined gap is also provided between them.
  • the large-diameter portion 20C of the piston 20 is accommodated in the storage space 55, and is prevented from being pulled out by the collar portion 54A. Therefore, the sleeve 29 does not separate from the piston 20. Moreover, it is possible to move slightly in the direction of the contact surfaces.
  • FIG. 7 shows a sixth embodiment.
  • a disc spring 56 is interposed between the large-diameter portion 20C of the piston 20 and the bent flange portion 54A, and the piston 20 and the shoe 29 are brought into close contact with each other.
  • an annular elastic member 57 is interposed in place of the disc spring 56, and the piston 20 and the shroud 29 are also brought into close contact with each other.
  • the present invention is not limited to the dishpane and the annular elastic member, and it is a matter of course that other elastic means such as a web bushing may be interposed.
  • FIG. 9 shows still another embodiment.
  • a rod 58 is provided at the center of the shoe 29 at the center thereof, a screw portion 58A is formed at the tip of the rod 58, and a through hole 20B of the piston 20 is formed.
  • the nut 60 is screwed into the tip of the rod 58 inserted through the washer 59.
  • a predetermined gap is provided between the inner periphery of the through hole 20B and the outer periphery of the rod 58, and the pusher 59 contacts the step 58B of the rod 58, and the pusher 59 and the piston 20
  • a minute gap is formed between the sheet and the spreader sheet 42.
  • the sleeves 29 are slidable relative to each other on the contact surface with respect to the piston 20 and are hardly separated in the axial direction. As a result, it is possible to prevent a one-sided hit and a collision noise while ensuring smooth movement between the piston 20 and the shoe 29. In this case, the structure is simpler and the processing cost can be reduced as compared with providing a connecting rod.
  • FIG. 10 shows a ninth embodiment.
  • two nuts 60A and 60B are combined to position the washer 59, and a lock mechanism using a so-called double nut is formed, and a minute gap between the washer 59 and the spring seat 42 is formed. It is set correctly.
  • FIG. 11 shows a tenth embodiment.
  • an elastic member 62 is interposed between the washer 59 and the spring seat 42, and the elastic force of the elastic member 62 separates the shoe 29 from the piston 20. Has been prevented.
  • an elastic material such as rubber or resin, or a spring member such as a coil spring, a wave washer, or a flat panel can be used as the elastic member 62.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention porte sur une pompe hydraulique ou un moteur hydraulique étudiés pour empêcher systématiquement les surfaces de contact d'un piston et d'un patin de se désolidariser tout en autorisant un léger coulissement de ces pièces. La pompe ou le moteur hydraulique comprend un patin hémisphérique en contact, via une surface sphérique, avec un plateau tournant. Sur le côté opposé de cette surface se trouve une surface plane et lisse en contact avec un piston, et un dispositif permettant tout à la fois de régler le coulissement du piston et du patin parallèlement aux surfaces de contact et d'empêcher ces deux pièces de s'écarter l'une de l'autre, une glace de distribution qui laisse le fluide hydraulique alternativement pénétrer dans les alésages de piston et en sortir au fur et à mesure que le barillet tourne, qui est fixée à un carter et qui coulisse contre le fond du barillet, un joint articulé qui relie le plateau tournant et le barillet, lesquels tournent de façon synchrone, le plateau tournant ou le barillet étant relié à un arbre d'entraînement.
PCT/JP1998/004732 1997-10-20 1998-10-20 Pompe ou moteur hydraulique WO1999020899A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE69838260T DE69838260T2 (de) 1997-10-20 1998-10-20 Hydraulische pumpe oder motor
EP98947948A EP1030057B1 (fr) 1997-10-20 1998-10-20 Pompe ou moteur hydraulique
DK98947948T DK1030057T3 (da) 1997-10-20 1998-10-20 Hydraulisk pumpe eller motor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP9/286964 1997-10-20
JP28696497A JP3894463B2 (ja) 1997-10-20 1997-10-20 アキシャルピストンポンプまたはモータ

Publications (1)

Publication Number Publication Date
WO1999020899A1 true WO1999020899A1 (fr) 1999-04-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1998/004732 WO1999020899A1 (fr) 1997-10-20 1998-10-20 Pompe ou moteur hydraulique

Country Status (5)

Country Link
EP (1) EP1030057B1 (fr)
JP (1) JP3894463B2 (fr)
DE (1) DE69838260T2 (fr)
DK (1) DK1030057T3 (fr)
WO (1) WO1999020899A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007001794A1 (de) 2007-01-05 2008-07-10 Robert Bosch Gmbh Hydraulische Kolbenmaschine
US8316995B2 (en) 2009-12-22 2012-11-27 Parker-Hannifin Corporation Hydraulic machine with oil dams
DE102012016061A1 (de) * 2012-08-14 2014-02-20 Robert Bosch Gmbh Gehäuseteil für eine hydrostatische Maschine und hydrostatische Maschine
CN103075316B (zh) * 2012-12-24 2015-08-05 北京工业大学 缸内轴承支撑半轴式纯水液压轴向柱塞泵
DE102017200244A1 (de) * 2017-01-10 2018-07-12 Robert Bosch Gmbh Hydrostatischer Axialkolbenmotor in Schrägachsenbauweise
FR3063325B1 (fr) * 2017-02-27 2019-03-29 Vianney Rabhi Attelage articule pour dispositif d'etancheite pour piston

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4855229U (fr) * 1971-10-30 1973-07-16
JPS4868204U (fr) * 1971-11-30 1973-08-30
JPH08151975A (ja) * 1994-09-30 1996-06-11 Kayaba Ind Co Ltd アキシャルピストンポンプ・モータ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4855229U (fr) * 1971-10-30 1973-07-16
JPS4868204U (fr) * 1971-11-30 1973-08-30
JPH08151975A (ja) * 1994-09-30 1996-06-11 Kayaba Ind Co Ltd アキシャルピストンポンプ・モータ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1030057A4 *

Also Published As

Publication number Publication date
JP3894463B2 (ja) 2007-03-22
EP1030057A1 (fr) 2000-08-23
DE69838260T2 (de) 2007-12-20
EP1030057B1 (fr) 2007-08-15
DK1030057T3 (da) 2007-12-03
EP1030057A4 (fr) 2004-06-30
DE69838260D1 (de) 2007-09-27
JPH11117856A (ja) 1999-04-27

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