JP6360701B2 - Hydraulic rotating machine - Google Patents

Description

  The present invention relates to a hydraulic rotating machine.

  Patent Document 1 discloses a rotating shaft, a cylinder block fixed to the rotating shaft and having a plurality of cylinders, a piston disposed in each cylinder, and a shoe rotatably provided at the tip of each piston. In addition, a swash plate type piston pump motor (hydraulic rotating machine) including a swash plate on which a shoe slides as the cylinder block rotates is disclosed.

JP 2010-116813 A

  A cylinder block of such a piston pump / motor (hydraulic rotating machine) has a plurality of supply / discharge ports through which a working fluid can be supplied / discharged to / from the cylinder volume chamber. It is configured as parallel straight passages. In this way, when the supply / discharge port has a linear shape, even if hydraulic oil (working fluid) passes through the supply / discharge port, the force acting on the supply / discharge port from the hydraulic oil affects the rotation of the cylinder block. There is no effect.

  On the other hand, in the piston pump / motor, the cylinder block is rotationally driven by an external force or the like. Therefore, it is desirable to efficiently rotate the cylinder block from the viewpoint of energy efficiency.

  Therefore, the present invention has been made in view of the above-described problems, and an object thereof is to provide a hydraulic rotating machine capable of efficiently rotating a cylinder block.

According to an aspect of the present invention, a cylinder block fixed to a rotation shaft, a plurality of cylinders formed on the cylinder block and arranged at predetermined intervals around the rotation shaft, and sliding on each cylinder A piston that is freely inserted and defines a volume chamber inside the cylinder, and a plurality of supply / discharge ports that are formed in the cylinder block and communicate with the volume chamber, are located on the supply side and the discharge side. The inner wall surface of the supply / exhaust port on the side through which the high-pressure working fluid flows out of the supply / exhaust port has a cylinder shaft in a direction opposite to the rotation direction of the cylinder block when viewed from the flow direction of the high-pressure working fluid. is formed with an inclination with respect to heart, the supply and discharge ports, and opening at one end which opens to the end face of the cylinder block, and the other end side opening that opens to the bottom surface of the cylinder, The one end side opening and the communication path connecting the other end side opening, and the one end side opening and the other end side opening are arranged shifted in the rotation direction of the cylinder block, and the communication path Is provided along a rotation direction of the cylinder block .
According to another aspect of the present invention, a cylinder block fixed to a rotation shaft, a plurality of cylinders formed on the cylinder block and arranged around the rotation shaft at predetermined intervals, and A piston that is slidably inserted and defines a volume chamber inside the cylinder, and a plurality of cylinder blocks, and a supply / discharge port that communicates with the volume chamber, are provided on the supply side and the discharge side. The inner wall surface of the supply / discharge port on the side through which the high-pressure working fluid flows among the supply / exhaust ports positioned is the cylinder in the direction opposite to the rotation direction of the cylinder block as seen from the flow direction of the high-pressure working fluid. The supply / exhaust port is formed with an inclination with respect to the axial center of the cylinder block, and the supply / exhaust port is open to the end surface of the cylinder block, and is open to the bottom surface of the cylinder. A communication passage that connects the one end side opening and the other end side opening, and the one end side opening and the other end side opening are arranged shifted in the rotation direction of the cylinder block, and A hydraulic rotating machine is provided in which the passage is formed as a curved passage that is curved with respect to the rotation direction of the cylinder block.

  According to the present invention, the rotation of the cylinder block can be assisted by utilizing the force acting on the inner wall surface of the supply / discharge port when the working fluid passes through the supply / discharge port, and the cylinder block is efficiently rotated. It becomes possible.

It is sectional drawing of the piston pump motor by embodiment of this invention. It is a bottom view of the cylinder block of a piston pump. It is a partial cross section figure of the cylinder block of a piston pump. It is a partial longitudinal cross-sectional view of the cylinder block of the piston pump by the modification of this embodiment. It is a partial longitudinal cross-sectional view of the cylinder block of the piston motor by the other modification of this embodiment. It is a partial longitudinal cross-sectional view of the cylinder block of the piston motor by the other modification of this embodiment.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a sectional view of a swash plate type piston pump motor according to an embodiment of the present invention.

  The piston pump motor as a hydraulic rotating machine functions as a piston pump 100 that can supply a working fluid by rotating the rotating shaft 1 and reciprocating the piston 2 by external power, and is supplied from the outside. The piston 2 reciprocates due to the fluid pressure of the working fluid and the rotating shaft 1 rotates, thereby functioning as a piston motor 200 that can output a rotational driving force. In such a piston pump 100 and piston motor 200, water, oil, a water-soluble alternative liquid or the like is used as a working fluid.

  Below, the case where a swash plate type piston pump motor is functioned as the piston pump 100 is illustrated.

  Piston pump 100 is mounted on a vehicle such as a construction machine. The piston pump 100 supplies hydraulic oil as a working fluid to an actuator or the like by rotating the rotary shaft 1 with the power of an engine (not shown) installed in the vehicle.

  The piston pump 100 includes a cylindrical case 3, end blocks 4 and 5 provided so as to close openings at both ends of the case 3, and a rotary shaft 1 rotatably supported by the end blocks 4 and 5. And a cylinder block 10 housed in a housing chamber 6 defined by the case 3 and the end blocks 4 and 5. The case 3 and the end block 4 or the case 3 and the end block 5 may be integrally formed.

  The rotating shaft 1 is a shaft member, and is rotationally driven based on the power of the engine or the electric motor. The rotating shaft 1 is provided so as to pass through the insertion hole 5 </ b> A of the end block 5, and the rear end portion of the rotating shaft 1 is inserted into a recess 4 </ b> A formed in the end block 4. The tip of the rotary shaft 1 protrudes from the end block 5 to the outside, and engine power is transmitted to the tip.

  The rotary shaft 1 is rotatably supported by front end side bearings 7A and 7B provided in the insertion hole 5A of the end block 5 and a rear end side bearing 8 provided in the recess 4A of the end block 4. The end block 4 is formed with a suction port 4B for guiding working fluid sucked into the volume chamber 13 described later and a discharge port 4C for guiding working fluid discharged from the volume chamber 13.

  The cylinder block 10 is a bottomed cylindrical member and is rotatably provided in the storage chamber 6. The cylinder block 10 includes an insertion portion 11 having an insertion hole 11A through which the rotation shaft 1 is inserted, and the rotation shaft 1 and the insertion hole 11A of the insertion portion 11 are spline-coupled. Thus, since the cylinder block 10 is fixed to the rotating shaft 1, the cylinder block 10 rotates in synchronization with the rotation of the rotating shaft 1.

  The cylinder block 10 includes a plurality of cylinders 12 extending in parallel with the rotation shaft 1. These cylinders 12 are arranged at a constant interval on the same circumference centered on the axis of the rotary shaft 1. A piston 2 that is a columnar member is inserted into each cylinder 12 so as to be able to reciprocate. By inserting the piston 2 into the cylinder 12, a volume chamber 13 is defined in the cylinder 12. The cylinder block 10 is provided with one supply / discharge port 14 for one cylinder 12, and the supply / discharge port 14 communicates with the volume chamber 13 of the corresponding cylinder 12.

  Further, the piston pump 100 holds a shoe 20 rotatably connected to the tip of each piston 2, a swash plate 30 on which the shoe 20 slides as the rotary shaft 1 rotates, and all the shoes 20. A retainer plate 40 and a retainer holder 50 that is in sliding contact with the retainer plate 40 are provided.

  The shoe 20 includes a circular flat plate portion 21 that slides on the swash plate 30, and a receiving portion 22 that is integrally formed with the flat plate portion 21 and receives the spherical seat 2 </ b> A at the tip of the piston 2. The inner surface of the receiving portion 22 is formed in a spherical shape, and slides with respect to the outer surface of the spherical seat 2 </ b> A of the piston 2. Thus, the shoe 20 is rotatable with respect to the spherical seat 2A of the piston 2.

  The swash plate 30 is fixed to the inner end surface of the end block 4, and has a sliding contact surface 31 that is inclined with respect to a direction orthogonal to the rotation shaft 1. The flat plate portion 21 of the shoe 20 connected to the piston 2 is disposed so as to be in surface contact with the sliding contact surface 31 of the swash plate 30.

  In the piston pump 100, the swash plate 30 is fixed to the end block 5 so that the inclination angle of the swash plate 30 is constant. However, the swash plate 30 is placed in the storage chamber 6 so that the inclination angle can be adjusted. You may arrange | position so that rocking | fluctuation is possible.

  The retainer plate 40 is formed as an annular flat plate member. The retainer plate 40 has a plurality of through holes 41 formed at predetermined intervals in the circumferential direction. The retainer plate 40 holds all the shoes 20 provided at the tip of each piston 2 on the same plane in a state where the receiving portion 22 of the shoe 20 is inserted through the through hole 41.

  The retainer holder 50 is a cylindrical member that is attached to the outer periphery of the axial center position of the rotary shaft 1 and is slidable along the rotary shaft 1. The tip of the retainer holder 50 is formed in a spherical shape, and the retainer holder 50 is disposed so that the tip is in sliding contact with the central portion of the retainer plate 40.

  An annular recess 15 is formed at the distal end portion of the insertion portion 11 of the cylinder block 10 so as to surround the outer periphery of the rotating shaft 1, and the rear end side of the retainer holder 50 is inserted into the annular recess 15. The retainer holder 50 not only slides on the outer peripheral surface of the rotary shaft 1 but also slides on the inner peripheral surface of the annular recess 15.

  A flange portion 51 protruding outward in the radial direction is formed at a substantially central position in the axial direction of the retainer holder 50. The flange portion 51 is provided along the outer periphery of the retainer holder 50. A compressed spring 60 is interposed between the flange portion 51 of the retainer holder 50 and the distal end surface of the insertion portion 11 of the cylinder block 10. The spring 60 is a biasing member that biases the retainer holder 50 toward the retainer plate 40. The retainer holder 50 biased in this manner presses the retainer plate 40 toward the swash plate 30, whereby the shoe 20 is pressed against the sliding contact surface 31 of the swash plate 30.

  A valve plate 70 with which the end face of the cylinder block 10 is in sliding contact is fixed to the end block 4 that closes the open end of the case 3. The valve plate 70 communicates with the suction port 4B of the end block 4 and communicates with the first supply / discharge hole 71 communicated with the volume chamber 13 of the cylinder block 10 and the discharge port 4C of the end block 4 and with the cylinder block 10. A second supply / exhaust hole 72 communicating with the volume chamber 13 is formed.

  With reference to FIG.1 and FIG.2, operation | movement of the piston pump 100 is demonstrated. FIG. 2 is a view of the cylinder block 10 of the piston pump 100 as viewed from the bottom.

  In the piston pump 100, when the rotary shaft 1 is rotationally driven by the power of the engine, the cylinder block 10 rotates counterclockwise as indicated by an arrow A in FIG. When the cylinder block 10 rotates in this way, each shoe 20 slides with respect to the swash plate 30, and each piston 2 reciprocates along the cylinder 12 with a stroke amount corresponding to the inclination angle of the swash plate 30. The volume of each volume chamber 13 is increased or decreased by the reciprocation of each piston 2.

  The hydraulic fluid is sucked into the volume chamber 13 which is expanded by the rotation of the cylinder block 10 through the suction port 4B of the end block 4, the first supply / discharge hole 71 of the valve plate 70, and the supply / discharge port 14 of the cylinder block 10. On the other hand, hydraulic oil is discharged from the volume chamber 13 which is reduced by the rotation of the cylinder block 10 through the supply / discharge port 14 of the cylinder block 10, the second supply / discharge hole 72 of the valve plate 70, and the discharge port 4 </ b> C of the end block 4. Is done. In FIG. 2, a region above the line C passing through the center of the rotating shaft 1 is a feeding region where the hydraulic oil is sucked into the volume chamber 13, and a region below the line C is the hydraulic oil from the volume chamber 13. This is a discharge area to be discharged. As described above, the piston pump 100 continuously sucks and discharges hydraulic oil as the cylinder block 10 rotates.

  In the piston pump 100 according to the present embodiment, the force acting on the supply / discharge port 14 when hydraulic oil passes through the supply / discharge port 14 of the cylinder block 10 is used to efficiently rotate the cylinder block 10. .

  With reference to FIG.2 and FIG.3A, the structure of the supply / discharge port 14 of the cylinder block 10 is demonstrated. 3A is a cross section of the cylinder block 10 and the valve plate 70 along the line D in FIG. 2, and is a view of one supply / exhaust port 14 as seen from the direction of the arrow B. FIG.

  As shown in FIGS. 2 and 3A, a plurality of supply / discharge ports 14 are formed at the bottom of the cylinder block 10. In the present embodiment, five supply / exhaust ports 14 are provided, and these supply / exhaust ports 14 are arranged on the same circumference (line D) centered on the axis of the rotating shaft 1 at a predetermined interval. Note that the number of supply / discharge ports 14 is not limited to five, and is set as necessary.

  The supply / discharge port 14 includes one end side opening 14A that opens to the end surface of the cylinder block 10, the other end side opening 14B that opens to the bottom surface of the cylinder 12, and one end side opening 14A and the other end side opening. 14C which connects the part 14B.

  The one end side opening 14 </ b> A and the other end side opening 14 </ b> B are formed as arc-shaped holes formed along the rotation direction of the cylinder block 10, in other words, arc-shaped holes curved around the axis of the rotating shaft 1. Has been.

  The one end side opening portion 14 </ b> A and the other end side opening portion 14 </ b> B constituting the supply / discharge port 14 are arranged so as to be shifted in the rotation direction of the cylinder block 10. That is, in the piston pump 100, the other end side opening portion 14B is arranged so as to be shifted from the one end side opening portion 14A to the rotation direction side of the cylinder block 10.

  The communication passage 14 </ b> C of the supply / discharge port 14 is formed from the one end side opening 14 </ b> A to the other end side opening 14 </ b> B, and extends along the rotation direction of the cylinder block 10. The communication passage 14 </ b> C of the supply / discharge port 14 is formed as an inclined passage having an inclination with respect to the axis of the cylinder 12. That is, among the supply / discharge ports 14 located on the supply side (above line C in FIG. 2) and the discharge side (below line C), the connection of the discharge side supply / discharge port 14 through which high-pressure working fluid flows. An inner wall surface 14D of the passage 14C is formed with an inclination with respect to the axis of the cylinder 12 in a direction opposite to the rotational direction F1 of the cylinder block 10 when viewed from the flow direction of the high-pressure working fluid.

  As shown in FIG. 3A, in the discharge region, the hydraulic oil in the volume chamber 13 is discharged to the outside of the piston pump 100 through the supply / discharge port 14 of the cylinder block 10 and the second supply / discharge hole 72 of the valve plate 70, and the actuator or the like. To be supplied. Thus, the high-pressure hydraulic fluid flowing out from the volume chamber 13 flows into the communication path 14C from the other end side opening 14B, and is guided from the one end side opening 14A to the second supply / discharge hole 72.

  When high-pressure hydraulic oil discharged from the volume chamber 13 passes through the supply / discharge port 14 in the discharge region, the flow of high-pressure hydraulic oil acts on the inner wall surface 14 </ b> D of the communication passage 14 </ b> C of the supply / discharge port 14. Since the communication path 14C is formed to be inclined with respect to the axis of the cylinder 12 as shown in FIG. 3A, the force acting on the inner wall surface 14D from the hydraulic oil (the force of the cylinder block rotation direction component) is indicated by the arrow F1. As shown in FIG. 4, the force is applied to urge the cylinder block 10 in the rotation direction of the cylinder block.

  On the other hand, the low-pressure hydraulic oil sucked from the suction port 4B flows into the volume chamber 13 in the supply region through the supply / discharge port 14. When the hydraulic oil flowing in in this way passes through the supply / discharge port 14, the force (force of the cylinder block rotation direction component) acting on the inner wall surface 14D of the supply / discharge port 14 from the hydraulic oil is the cylinder block rotation direction. It will be a reverse force.

  However, since the hydraulic pressure on the discharge area side is higher than the hydraulic pressure on the supply area side, the density of the hydraulic oil increases. Therefore, the kinetic energy becomes larger than that of the feeding area side. Therefore, the force acting on the inner wall surface 14D of the supply / discharge port 14 on the discharge area side is larger than that on the supply area side. As a result, the resultant force of the rotational direction component acting on the inner wall surface 14D of each supply / exhaust port 14 becomes a force that urges the cylinder block 10 in the cylinder block rotation direction.

  In the above-described piston pump 100, the supply / discharge port 14 is inclined with respect to the axial center of the cylinder 12 so that the cylinder block 10 is urged in the rotational direction by the force acting on the inner wall surface 14D when the hydraulic oil passes. It is formed with. Therefore, the rotation of the cylinder block 10 can be assisted by utilizing the force acting on the inner wall surface 14D of the supply / discharge port 14 from the hydraulic oil, and the cylinder block 10 can be efficiently rotated.

  As the rotating shaft 1 rotates at a higher speed, the flow rate of the hydraulic oil discharged from the piston pump 100 becomes faster. Therefore, the force acting on the inner wall surface 14D of the supply / discharge port 14 increases as the piston pump 100 operates at a higher speed. Therefore, when the piston pump 100 is operated at high speed, the cylinder block 10 can be driven to rotate more efficiently.

  Further, in the piston pump 100, the one end side opening 14 </ b> A and the other end side opening 14 </ b> B of the supply / discharge port 14 are arranged so as to be shifted in the rotation direction of the cylinder block 10. Accordingly, the communication path 14 </ b> C connecting the one end side opening 14 </ b> A and the other end side opening 14 </ b> B can be easily inclined with respect to the rotation direction of the cylinder block 10. As a result, the direction of the force acting on the inner wall surface 14 </ b> D from the hydraulic oil can be easily matched with the rotation direction of the cylinder block 10.

  Further, in the piston pump 100, the communication passage 14 </ b> C of the supply / discharge port 14 extends along the rotation direction of the cylinder block 10. This also makes it easy to match the direction of the force acting on the inner wall surface 14D from the hydraulic oil in the same direction as the rotation direction of the cylinder block.

  In the piston pump 100, the communication passage 14C of the supply / discharge port 14 is formed as a linear passage as shown in FIG. 3A, but the shape of the communication passage 14C is not limited to this. The communication passage 14C of the supply / exhaust port 14 may have any shape that can be urged so as to assist the rotation of the cylinder block 10 by the force acting on the inner wall surface 14D from the hydraulic oil. For example, as shown in FIG. It may be formed as a passage. In this case, the communication passage 14 </ b> C of the supply / discharge port 14 is configured as a curved passage that is curved with respect to the rotation direction of the cylinder block 10. By configuring the communication passage 14C in a curved shape in this way, the rotation of the cylinder block 10 can be assisted by the force acting on the inner wall surface 14D from the hydraulic oil, and the hydraulic oil can flow more smoothly in the passage. Thus, the occurrence of cavitation can be suppressed.

  The embodiment of the present invention has been described above. However, the above embodiment is merely one example of application of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  In the present embodiment, the case where the swash plate type piston pump / motor is caused to function as the piston pump 100 is illustrated, but the swash plate type piston pump / motor may be caused to function as the piston motor 200 capable of outputting the rotational driving force.

  When the swash plate type piston pump / motor is caused to function as the piston motor 200, the hydraulic pressure of the hydraulic oil flowing into the volume chamber 13 through the first supply / discharge hole 71 and the supply / discharge port 14 is greater. The hydraulic oil flowing out of the volume chamber 13 through the supply / discharge hole 72 is higher than the hydraulic pressure and has a high density, so that the kinetic energy also increases.

  Therefore, as shown in FIG. 4A, the piston motor 200 causes the cylinder block 10 to rotate in the rotational direction by the force acting on the inner wall surface 14D of the supply / discharge port 14 when the hydraulic oil passes through the supply / discharge port 14 in the supply region. Configured to be energized. In such a piston motor 200, the one end side opening 14 </ b> A is shifted from the other end side opening 14 </ b> B toward the rotational direction of the cylinder block 10. The communication passage 14 </ b> C of the supply / discharge port 14 is formed from the one end side opening 14 </ b> A to the other end side opening 14 </ b> B, and extends along the rotation direction of the cylinder block 10. The communication passage 14 </ b> C of the supply / discharge port 14 is formed as an inclined passage having an inclination with respect to the axis of the cylinder 12. That is, the inner wall surface 14D of the communication passage 14C of the supply / discharge port 14 on the supply side through which the high-pressure working fluid flows out of the supply / discharge ports 14 positioned on the supply side and the discharge side, from the flow direction of the high-pressure working fluid. As seen, the cylinder block 10 is formed with an inclination with respect to the axis of the cylinder 12 in the direction opposite to the rotation direction F2 of the cylinder block 10.

  In the piston motor 200, the flow of the high-pressure hydraulic oil acts on the inner wall surface 14 </ b> D of the communication passage 14 </ b> C of the supply / discharge port 14 when the high-pressure hydraulic oil passes through the supply / discharge port 14 in the supply region. Since the communication path 14C is inclined as shown in FIG. 4A, the force acting on the inner wall surface 14D from the hydraulic oil (the force of the cylinder block rotation direction component) is the cylinder block rotation direction as indicated by the arrow F2. This is the force that urges the cylinder block 10. Since the hydraulic pressure on the supply area side is higher than the hydraulic pressure on the discharge area side, the force acting on the inner wall surface 14D of the supply / discharge port 14 on the supply area side is larger than that on the discharge area side. As a result, the resultant force of the rotational direction component acting on the inner wall surface 14D of each supply / exhaust port 14 becomes a force that urges the cylinder block 10 in the cylinder block rotation direction.

  In the piston motor 200, by configuring the supply / discharge port 14 as shown in FIG. 4A, the rotation of the cylinder block 10 can be assisted by utilizing the force acting on the inner wall surface 14D of the supply / discharge port 14. The block 10 can be efficiently rotated.

  In the piston motor 200, the communication passage 14C of the supply / discharge port 14 is formed as a linear passage as shown in FIG. 4A, but the shape of the communication passage 14C is not limited to this. The communication passage 14C of the supply / exhaust port 14 may have any shape that can be urged so as to assist the rotation of the cylinder block 10 by the force acting on the inner wall surface 14D from the hydraulic oil. For example, as shown in FIG. It may be formed as a passage. In this case, the communication passage 14 </ b> C of the supply / discharge port 14 is configured as a curved passage that is curved with respect to the rotation direction of the cylinder block 10. By configuring the communication passage 14C in a curved shape in this way, the rotation of the cylinder block 10 can be assisted by the force acting on the inner wall surface 14D from the hydraulic oil, and the hydraulic oil can flow more smoothly in the passage. Thus, the occurrence of cavitation can be suppressed. As shown in FIGS. 3B and 4B, in the piston motor 100 and the piston motor 200, the flow of the high-pressure hydraulic oil is taken into consideration so that the acting force from the hydraulic oil acts on the inner wall surface 14D efficiently. The curved shape of 14C is varied.

  In the swash plate type piston pump 100 and piston motor 200 described above, the one end side opening 14A and the other end side opening 14B are arranged on the same circumference as shown in FIG. One end of the other end side opening 14 </ b> B may be disposed on the radially inner side of the cylinder block 10 or on the radially outer side of the cylinder block 10.

100 piston pump (hydraulic rotating machine)
200 Piston motor (hydraulic rotating machine)
DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Piston 10 Cylinder block 12 Cylinder 13 Volume chamber 14 Supply / discharge port 14A One end side opening part 14B Other end side opening part 14C Communication path 14D Inner wall surface 20 Shoe 30 Swash plate 70 Valve plate

Claims (6)

A cylinder block fixed to the rotating shaft;
A plurality of cylinders formed in the cylinder block and arranged at predetermined intervals around the axis of the rotation shaft;
A piston that is slidably inserted into each cylinder, and that defines a volume chamber inside the cylinder;
A plurality of cylinder blocks, and a supply / discharge port communicating with the volume chamber,
The inner wall surface of the supply / exhaust port on the side through which the high-pressure working fluid flows among the supply / exhaust ports located on the supply side and the discharge side, as viewed from the flow direction of the high-pressure working fluid, Is formed in an opposite direction with an inclination with respect to the axis of the cylinder ,
The supply / discharge port is
One end side opening that opens to the end face of the cylinder block;
The other end opening that opens to the bottom of the cylinder;
A communication path connecting the one end side opening and the other end side opening,
The one end side opening and the other end side opening are arranged to be shifted in the rotation direction of the cylinder block,
The communication path extends along the rotation direction of the cylinder block.
A hydraulic rotating machine characterized by that. In the communication path, a cross section along the rotation direction of the cylinder is formed as a linear path.
The hydraulic rotating machine according to claim 1. The communication path is formed as a curved path that curves with respect to the rotation direction of the cylinder block.
The hydraulic rotating machine according to claim 1. A cylinder block fixed to the rotating shaft;
A plurality of cylinders formed in the cylinder block and arranged at predetermined intervals around the axis of the rotation shaft;
A piston that is slidably inserted into each cylinder, and that defines a volume chamber inside the cylinder;
A plurality of cylinder blocks, and a supply / discharge port communicating with the volume chamber,
The inner wall surface of the supply / exhaust port on the side through which the high-pressure working fluid flows among the supply / exhaust ports located on the supply side and the discharge side, as viewed from the flow direction of the high-pressure working fluid, Is formed in an opposite direction with an inclination with respect to the axis of the cylinder,
The supply / discharge port is
One end side opening that opens to the end face of the cylinder block;
The other end opening that opens to the bottom of the cylinder;
A communication path connecting the one end side opening and the other end side opening,
The one end side opening and the other end side opening are arranged to be shifted in the rotation direction of the cylinder block,
The communication path is formed as a curved path that curves with respect to the rotation direction of the cylinder block.
A hydraulic rotating machine characterized by that. The hydraulic rotating machine is a piston pump in which the rotating shaft and the cylinder block are driven to rotate by power from outside.
The hydraulic rotating machine according to any one of claims 1 to 4, wherein the hydraulic rotating machine is provided. The hydraulic rotating machine is a piston motor in which the rotating shaft and the cylinder block are rotationally driven by a working fluid supplied from the outside.
The hydraulic rotating machine according to any one of claims 1 to 4, wherein the hydraulic rotating machine is provided.

Images