WO2014156539A1

WO2014156539A1 - Opposed swashplate-type hydraulic rotary machine

Info

Publication number: WO2014156539A1
Application number: PCT/JP2014/055782
Authority: WO
Inventors: 弘毅加藤; 細川　尊
Original assignee: カヤバ工業株式会社
Priority date: 2013-03-29
Filing date: 2014-03-06
Publication date: 2014-10-02
Also published as: KR101743848B1; JP2014196726A; KR20150044940A; US20150240636A1; DE112014000201T5; CN104685208A; JP6114089B2

Abstract

An opposed swashplate-type piston motor in which a first piston and a second piston protruding from both ends of a cylinder block reciprocate in conjunction with a first swashplate and a second swashplate, respectively, said piston motor being equipped with: a first tilting bearing for tiltably supporting the first swashplate; a first tilting drive piston for tilting the first swashplate in a direction which intersects the rotational axis of the cylinder block; a second tilting bearing for tiltably supporting the second swashplate; and a second tilting drive piston for tilting the second swashplate in a direction which intersects the rotational axis of the cylinder block.

Description

Opposite type swash plate type hydraulic rotating machine

The present invention relates to an opposing type swash plate type hydraulic rotating machine in which a first swash plate and a second swash plate are inclined to face both ends of a cylinder block.

In JP2008-231924A, a cylinder block having a plurality of cylinders, a first piston and a second piston protruding from both ends of the cylinder, and a first swash plate and a second swash plate in which the protruding ends of the first and second pistons are in sliding contact with each other. An opposed type swash plate type hydraulic rotating machine is disclosed, comprising: a swash plate.

In a hydraulic rotary machine, the first piston follows the first swash plate to reciprocate in the cylinder as the cylinder block rotates, and the second piston follows the second swash plate to reciprocate in the cylinder. Then, the working fluid is supplied to and discharged from the volume chamber in the cylinder.

A tilt drive piston for tilting the first swash plate is connected to one side of the first swash plate, and the other side of the first swash plate transmits the tilt of the first swash plate to the second swash plate The tilting interlocking mechanism is connected. When the first swash plate is tilted by the tilting drive piston, the second swash plate is also tilted via the tilting interlocking mechanism.

In the opposing type swash plate type hydraulic rotating machine disclosed in JP2008-231924A, the tilting shaft portion of the first swash plate causes the floating phenomenon to separate from the tilting bearing provided on the casing when the first swash plate is driven to tilt. Sometimes.

The floating phenomenon includes the force of the tilting drive piston received on one side of the first swash plate when the first swash plate tilts, the reaction force of the tilting interlocking mechanism received on the other side of the first swash plate, Is a phenomenon in which the first swash plate rotates about the rotation axis of the cylinder block by acting as a torque in the same rotational direction, and the tilting shaft portion of the first swash plate separates from the tilt bearing.

An object of the present invention is to prevent the floating phenomenon in an opposed type swash plate type hydraulic rotating machine.

According to an aspect of the present invention, the opposite type swash plate in which the first piston and the second piston protruding from both ends of the rotating cylinder block reciprocate in the cylinder following the first swash plate and the second swash plate, respectively. Type hydraulic rotary machine, a first tilt bearing for tiltably supporting a first swash plate, and a first tilt drive for causing the first swash plate to tilt in a direction intersecting the rotation axis of the cylinder block A facing comprising a piston, a second tilt bearing which tiltably supports a second swash plate, and a second tilt drive piston which tilts the second swash plate in a direction intersecting with the rotation axis of the cylinder block. A swash plate type hydraulic rotating machine is provided.

FIG. 1 is a cross-sectional view of an opposed type swash plate type piston motor according to an embodiment of the present invention. FIG. 2: is a schematic diagram which shows the structure which tilts a 1st swash plate and a 2nd swash plate. FIG. 3: is a schematic diagram which shows the structure which tilts a 1st swash plate and a 2nd swash plate. FIG. 4 is a hydraulic circuit diagram for tilting the first swash plate and the second swash plate.

An opposing swash plate type piston motor 1 according to an embodiment of the present invention will be described with reference to the drawings.

The opposing type swash plate type piston motor 1 shown in FIG. 1 is applied to a hydrostatic transmission 90 (see FIG. 4; hereinafter simply referred to as “HST 90”) mounted as a continuously variable transmission on a work vehicle or the like.

As shown in FIG. 1, the opposed type swash plate type piston motor 1 is inclined to face both ends of the shaft 2 rotating around the rotation axis O 4, the cylinder block 4 supported by the shaft 2, and the cylinder block 4. The first swash plate 30 and the second swash plate 40 are provided.

The cylinder block 4 is formed in a cylindrical shape having a hollow portion, and the shaft 2 is inserted therein. A plurality of cylinders 3 are formed in the cylinder block 4 side by side in the circumferential direction. The cylinder 3 is formed to extend in the axial direction, and opens at both end faces 4C and 4D of the cylinder block 4.

The first piston 8 and the second piston 9 are respectively inserted into the cylinder 3 from both open ends. The first piston 8 and the second piston 9 have tip portions projecting from the open end of the cylinder 3, and the first shoe 21 and the second shoe 22 are pivotally connected to the respective tip portions.

When the cylinder block 4 rotates, the first piston 8 reciprocates following the end face 30A of the first swash plate 30 via the first shoe 21 and the port plate 16, and the second piston 9 reciprocates the second shoe 22. It reciprocates following the end face 40A of the second swash plate 40 via the same.

In the cylinder 3, a volume chamber 7 is defined between the first piston 8 and the second piston 9. By reciprocating the first piston 8 and the second piston 9 in the cylinder 3, the volume chamber 7 is expanded and contracted, and hydraulic oil is supplied and discharged to the volume chamber 7 through the pair of supply and discharge passages 5, 6 (see FIG. 4). Ru.

The piston motor 1 uses hydraulic fluid (oil) as the hydraulic fluid, but may use a hydraulic fluid such as a water-soluble substitute fluid instead of the hydraulic fluid.

The cylindrical shaft 2 is rotatably supported at both ends by a casing (not shown) via a bearing (not shown).

The casing is provided with a cylindrical case (not shown) and lid-like first and second covers (not shown) that close both open ends of the case. The cylinder block 4 is accommodated in the case, the first swash plate 30 is accommodated in the first cover, and the second swash plate 40 is accommodated in the second cover.

Splines 2A are formed on the outer periphery of the shaft 2. Splines 4 H are formed on the inner periphery of the cylinder block 4. The spline 4H of the cylinder block 4 is slidably fitted to the spline 2A of the shaft 2, whereby the rotation of the cylinder block 4 with respect to the shaft 2 is restricted, and axial movement with respect to the shaft 2 becomes possible.

A first retainer plate 23 and a first retainer holder 25 are interposed between the first swash plate 30 and the cylinder block 4 in the axial direction.

Between the first shoe 21 and the first swash plate 30, a disc-shaped port plate 16 that rotates with the cylinder block 4 is provided. The port plate 16 is connected to the first retainer plate 23 via a plurality of pins 18.

A plurality of center springs 19 are interposed between the first retainer holder 25 and the cylinder block 4 in the circumferential direction. The cylinder block 4 is urged rightward in FIG. 1 by the center spring 19 and pressed against the end face 40A of the second swash plate 40 via the second retainer holder 26, the second retainer plate 24 and the second shoe 22. . As a result, the axial position of the cylinder block 4 with respect to the second swash plate 40 is determined.

Next, a configuration in which the first swash plate 30 and the second swash plate 40 are respectively tilted will be described based on FIGS. 2 and 3.

The first swash plate 30 has a pair of tilting and rotating shaft portions (half log portions) 30B that project to the back side. The tilting shaft portion 30B is tiltably supported by a first tilting bearing 33 formed in a casing (not shown). The first swash plate 30 pivots about the first tilting axis O1. The second swash plate 40 has a pair of tilting and rotating shaft portions (half log portions) 40B projecting to the back side. The tilt shaft portion 40B is tiltably supported by a second tilt bearing 43 formed in the casing. The second swash plate 40 pivots about the second tilting axis O2. The first tilt axis O1 and the second tilt axis O2 are orthogonal to the rotation axis O4 of the cylinder block 4.

The piston motor 1 includes a first tilting drive mechanism 50 for tilting the first swash plate 30 and a second tilting drive mechanism 60 for tilting the second swash plate 40. As the first swash plate 30 tilts, the stroke length at which the first piston 8 reciprocates in the cylinder 3 changes. By tilting the second swash plate 40, the stroke length at which the second piston 9 reciprocates in the cylinder 3 changes. As the stroke length changes, the displacement per revolution of the cylinder block 4 changes, and the output rotational speed of the piston motor 1 changes.

In the first tilt drive mechanism 50, the first tilt drive piston 31 moved by hydraulic pressure and the movement of the first tilt drive piston 31 are centered on the first tilt axis O1. And a conversion mechanism 38 for converting into a rotational movement.

In FIG. 2 and FIG. 3, the line G1 is orthogonal to the rotation axis O4 and to the first tilt axis O1. The first tilting drive piston 31 is arranged to move in a direction parallel to the line G1. Not limited to this, the first tilt drive piston 31 may be arranged to move in a direction intersecting with the line G1 at a slight angle.

The conversion mechanism 38 includes a slide metal 36 slidably engaged with the guide groove 35 of the first tilt drive piston 31, and a slide metal projecting from an end of the first swash plate 30 in the direction of the first tilt axis O1. And a pin 37 slidably inserted into the hole 36. When the first tilt drive piston 31 moves in the axial direction (a direction parallel to the line G1), the slide metal 36 and the pin 37 slide along the guide groove 35 and an arc centered on the first tilt axis O1 Move along. As a result, the first swash plate 30 pivots about the first tilting axis O1.

A first push side piston pressure chamber 53 and a first pull side piston pressure chamber 54 are respectively defined at both ends of the first tilt drive piston 31. A first tilt control valve 70 is provided to switch the hydraulic pressure introduced to the

piston pressure chambers

53, 54. The first tilt drive piston 31 moves due to the hydraulic pressure difference between the

piston pressure chambers

53 and 54.

In the second tilt drive mechanism 60, the second tilt drive piston 41 moved by hydraulic pressure and the movement in which the second tilt drive piston 41 moves are centered on the second tilt axis O2. And a conversion mechanism 48 for converting into a rotational movement.

In FIG. 2 and FIG. 3, the line G2 is orthogonal to the rotation axis O4 and orthogonal to the second tilting axis O2. The second tilting drive piston 41 is arranged to move in a direction parallel to the line G2. Not limited to this, the second tilt drive piston 41 may be arranged to move in a direction intersecting with the line G2 at a slight angle.

The conversion mechanism 48 includes a slide metal 46 slidably engaged with the guide groove 45 of the second tilt drive piston 41, and a slide metal projecting from an end of the second swash plate 40 in the direction of the second tilt axis O2. And a pin 47 slidably inserted into the hole 46. When the second tilt drive piston 41 moves in the axial direction (a direction parallel to the line G2), the slide metal 46 and the pin 47 slide along the guide groove 45 and an arc centered on the second tilt axis O2 Move along. As a result, the second swash plate 40 pivots about the second tilting axis O2.

A second push side piston pressure chamber 63 and a second pull side piston pressure chamber 64 are respectively defined at both ends of the second tilting drive piston 41. A second tilt control valve 80 is provided to switch the hydraulic pressure introduced to the

piston pressure chambers

63, 64. The second tilt drive piston 41 is moved by the hydraulic pressure difference between the

piston pressure chambers

63 and 64.

FIG. 4 is a diagram showing the configuration of the hydraulic circuit and control system provided in the HST 90. As shown in FIG.

The HST 90 includes a piston motor 1, a piston pump 99, and a closed circuit 100 through which hydraulic fluid circulates.

The closed circuit 100 includes a first circulation passage 101 and a second circulation passage 102 that connect the piston motor 1 and the piston pump 99. One end of the first circulation passage 101 is connected to the supply and discharge passage 5 of the piston motor 1, and the other end is connected to the supply and discharge passage 105 of the piston pump 99. One end of the second circulation passage 102 is connected to the supply and discharge passage 6 of the piston motor 1, and the other end is connected to the supply and discharge passage 106 of the piston pump 99.

The hydraulic fluid discharged from the piston pump 99 is fed to the piston motor 1 through the closed circuit 100, whereby the piston motor 1 rotates. The output rotation of the piston motor 1 is transmitted to the left and right wheels via a transmission (gear type transmission), a differential gear, etc. (not shown).

The piston pump 99 is rotationally driven by an engine (not shown). The piston pump 99 has two supply and discharge

passages

105 and 106 for supplying and discharging the hydraulic oil to the volume chamber, and the discharge direction of the hydraulic oil to the supply and discharge

passages

105 and 106 by switching the tilt direction of the swash plate 107. Will change. By changing the discharge direction of the piston pump 99, the traveling direction (forward or reverse) of the vehicle is switched.

The fluid pressure source 110 is provided with a fixed displacement charge pump 111 which is rotationally driven by the engine, and a charge passage 113 which leads hydraulic oil discharged from the charge pump 111. An oil filter 114, an oil filter 116, and a relief valve 119 are interposed in the charge passage 113. The hydraulic oil that has passed through the relief valve 119 returns to the tank 109.

Charge passage 113 is connected to first circulation passage 101 and second circulation passage 102 via

check valves

117 and 118. When the pressure in the first circulation passage 101 drops below the pressure in the charge passage 113, the check valve 117 opens to fill the first circulation passage 101 with the hydraulic oil from the charge passage 113. On the other hand, when the pressure in the second circulation passage 102 is lower than the pressure in the charge passage 113, the check valve 118 opens to fill the second circulation passage 102 with the hydraulic oil from the charge passage 113. For this reason, the pressures of the first circulation passage 101 and the second circulation passage 102 are maintained at or above a predetermined value.

Relief valves

121 and 122 are interposed in the charge passage 113 in parallel with the

check valves

117 and 118. When the pressure in the first circulation passage 101 rises above the predetermined value with respect to the pressure in the charge passage 113, the relief valve 121 opens and the hydraulic pressure in the first circulation passage 101 is released to the charge passage 113. On the other hand, when the pressure in the second circulation passage 102 rises above the predetermined value with respect to the pressure in the charge passage 113, the relief valve 122 opens and the hydraulic pressure in the second circulation passage 102 is released to the charge passage 113. For this reason, it is suppressed that the pressure of the 1st circulation passage 101 and the 2nd circulation passage 102 exceeds predetermined value.

A high pressure selection valve 149 is provided between the first circulation passage 101 and the second circulation passage 102. The hydraulic pressure extracted through the high pressure selection valve 149 is led to the first tilt control valve 70 and the second tilt control valve 80.

The first tilt control valve 70 includes an inlet port 71 communicating with the high pressure selection valve 149, an outlet port 72 communicating with the tank 109, and a first push side port 73 communicating with the first push side piston pressure chamber 53; And a first pull side port 74 in communication with the first pull side piston pressure chamber 54.

As shown in FIGS. 2 and 3, the first tilt control valve 70 includes a valve housing 76 inserted in the casing, a spool valve 79 slidably accommodated in the valve housing 76, and a spool valve 79. In one axial direction, and a solenoid 77 which moves the spool valve 79 in the axial direction against the spring 78.

As the spool valve 79 moves to a position where the thrust of the solenoid 77 and the biasing force of the spring 78 are balanced, the first tilt control valve 70 is switched to three

positions

70A, 70B, 70C.

When a predetermined thrust is generated in the solenoid 77 by the excitation current sent from the controller 170, the spool valve 79 is moved upward in FIG. 2 against the biasing force of the spring 78 by the thrust and the first tilt control valve 70 is switched to the push side position 70A.

In the push side position 70A, the hydraulic oil from the high pressure selection valve 149 is supplied to the first push side piston pressure chamber 53 through the

ports

71, 73, and the hydraulic oil of the first pull side piston pressure chamber 54 is the

hydraulic pressure port

74, 72. Is returned to the tank 109. As the pressure in the first push side piston pressure chamber 53 becomes higher, the first tilting drive piston 31 moves in the direction (downward direction) indicated by arrow A in FIG. 2 and the first swash plate 30 is indicated by arrow B As such, it pivots in the direction in which the tilt angle increases. As a result, the displacement volume of the piston motor 1 increases, and the traveling speed of the vehicle decreases.

When the excitation current sent from the controller 170 is stopped, the thrust of the solenoid 77 disappears, and the spool valve 79 moves in the direction (downward) shown in FIG. Is switched to the pull side position 70B.

In the pull side position 70B, the hydraulic oil from the high pressure selection valve 149 is supplied to the first pull side piston pressure chamber 54 through the

ports

71 and 74, and the hydraulic oil of the first push side piston pressure chamber 53 is tanked through the

ports

73 and 72. It is returned to 109. As the pressure in the first pulling side piston pressure chamber 54 becomes higher, the first tilting drive piston 31 moves in the direction (upward direction) indicated by the arrow C in FIG. 3 and the first swash plate 30 is indicated by the arrow D As such, it pivots in the direction in which the tilt angle decreases. As a result, the displacement of the piston motor 1 is reduced, and the traveling speed of the vehicle is increased.

In the neutral position 70C, the ports 71 to 74 are closed, and the movement of the first tilting drive piston 31 is stopped. Therefore, the first swash plate 30 is held at the tilt angle at that time.

The controller 170 adjusts the flow rate of the hydraulic oil supplied to and discharged from the first tilt drive mechanism 50 by switching the

positions

70A, 70B, 70C of the first tilt control valve 70, and continuously changes the transmission ratio of the HST 90. Control.

The second tilt control valve 80 has an inlet port 81 communicating with the high pressure selection valve 149, an outlet port 82 communicating with the tank 109, and a second push side port 83 communicating with the second push side piston pressure chamber 63; And a second pull-side port 84 communicating with the second pull-side piston pressure chamber 64.

As shown in FIGS. 2 and 3, the second tilt control valve 80 includes a valve housing 86 installed in the casing, a spool valve 89 slidably accommodated in the valve housing 86, and a spool valve 89. And the solenoid 87 which moves the spool valve 89 in the axial direction against the spring 88.

As the spool valve 89 moves to a position where the thrust of the solenoid 87 and the biasing force of the spring 88 balance, the second tilt control valve 80 switches to three

positions

80A, 80B, 80C.

When a predetermined magnetic force is generated in the solenoid 87 by the excitation current sent from the controller 170, the spool valve 89 moves upward in FIG. 2 against the biasing force of the spring 88 by the magnetic force, and the second tilt control valve The position 80 is switched to the pulling position 80B.

In the pull side position 80B, the hydraulic oil from the high pressure selection valve 149 is supplied to the second pull side piston pressure chamber 64 through the

ports

81 and 84, and the hydraulic oil of the second push side piston pressure chamber 63 is the

hydraulic pressure ports

83 and 82. Is returned to the tank 109. As the pressure in the second pulling piston pressure chamber 64 increases, the second tilting drive piston 41 moves in the direction (upward direction) indicated by arrow E in FIG. 2, and the second swash plate 40 is indicated by arrow F. As such, it pivots in the direction in which the tilt angle decreases. As a result, the displacement of the piston motor 1 is reduced, and the traveling speed of the vehicle is increased.

When the excitation current sent from the controller 170 is stopped, the magnetic force of the solenoid 87 disappears, and the spool valve 89 moves in the direction (downward) shown in FIG. Is switched to the push side position 80A.

In the push side position 80A, the hydraulic oil from the high pressure selection valve 149 is supplied to the second push side piston pressure chamber 63 through the

ports

81 and 83, and the hydraulic oil of the second pulling side piston pressure chamber 64 is tanked through the

ports

84 and 82. It is returned to 109. When the pressure of the second push side piston pressure chamber 63 becomes high, the second tilting drive piston 41 moves in the direction shown by the arrow H in FIG. 3 (downward), and the second swash plate 40 is shown by the arrow I As such, it pivots in the direction in which the tilt angle increases. As a result, the displacement volume of the piston motor 1 increases and the speed of the vehicle decreases.

In the neutral position 80C, the ports 81 to 84 are closed, and the movement of the second tilting drive piston 41 is stopped. Therefore, the second swash plate 40 is held at the tilt angle at that time.

The controller 170 adjusts the flow rate of the hydraulic oil supplied to and discharged from the second tilt drive mechanism 60 by switching the

positions

80A, 80B, 80C of the second tilt control valve 80 to continuously change the transmission ratio of the HST 90. Control.

Numerals

171 and 172 are potentiometers for reading the tilt angles of the first swash plate 30 and the second swash plate 40, respectively. The controller 170 performs feedback control of the open / close timing of the first tilt control valve 70 and the second tilt control valve 80 in accordance with the detection values of the

potentiometers

171 and 172.

As shown in FIG. 3, when energization of the solenoid 77 of the first tilt control valve 70 is stopped and energization of the solenoid 87 of the second tilt control valve 80 is stopped, the tilt angle of the first swash plate 30 is obtained. Is minimized and the tilt angle of the second swash plate 40 is maximized. At this time, the gear ratio of the piston motor 1 becomes an intermediate value.

When the solenoid 77 of the first tilt control valve 70 is energized as shown in FIG. 2 and the energization of the solenoid 87 of the second tilt control valve 80 is stopped as shown in FIG. The tilt angle of the second swash plate 40 is maximized. At this time, the displacement of the piston motor 1 is maximized, and the gear ratio of the piston motor 1 is minimized.

When the solenoid 77 of the first tilt control valve 70 is deenergized as shown in FIG. 3 and the solenoid 87 of the second tilt control valve 80 is energized as shown in FIG. The tilt angle of the second swash plate 40 is both minimized. At this time, the displacement of the piston motor 1 is minimized, and the gear ratio of the piston motor 1 is maximized.

As described above, the first tilt drive piston 31 pushes the end of the first swash plate 30 in the direction orthogonal to the tilt axis O1 to tilt the first swash plate 30, and the second tilt drive piston The tilting of the second swash plate 40 by pressing the end of the second swash plate 40 in the direction orthogonal to the tilting axis O2 is performed independently of each other.

Further, the flow rate of the working fluid supplied to and discharged from the first tilt drive mechanism 50 is adjusted by the first tilt control valve 70, and the flow rate of the working fluid supplied to and discharged from the second tilt drive mechanism 60 is It is adjusted by a second tilt control valve 80 different from the single tilt control valve 70.

According to the above embodiment, the following effects are obtained.

The first swash plate 30 and the second swash plate 40 are tilted by being pushed by the first tilt drive piston 31 and the second tilt drive piston 41 in the direction intersecting the tilt axes O1 and O2, respectively. Therefore, since the torque for rotating around the central axis O4 does not act on the first swash plate 30 and the second swash plate 40, the tilt shaft portion 30B and the tilt shaft portion 40B are the first tilt bearing 33 and the first tilt bearing 33 and The floating phenomenon away from the second tilting bearing 43 can be prevented.

In addition, the actuation strokes of the first tilt drive mechanism 50 and the second tilt drive mechanism 60 are continuously adjusted by the operation of the first tilt control valve 70 and the second tilt control valve 80, respectively. The tilt angles of the first swash plate 30 and the second swash plate 40 can be controlled to any level.

Further, the flow rate of the working fluid supplied to and discharged from the first tilt drive mechanism 50 and the flow rate of the working fluid supplied to and discharged from the second tilt drive mechanism 60 correspond to the first tilt control valve 70 and the second tilt control valve. The first tilt drive mechanism 50 can adjust the tilt angle of the first swash plate 30 in a responsive manner because the control valve 80 respectively adjusts the tilt angle of the first swash plate 30. The tilt angle can be adjusted responsively.

As mentioned above, although the embodiment of the present invention was described, the above-mentioned embodiment showed only a part of application example of the present invention, and in the meaning of limiting the technical scope of the present invention to the concrete composition of the above-mentioned embodiment. Absent.

For example, although the present embodiment is the piston motor 1 in which the cylinder block is rotated by supplying and discharging the hydraulic oil, the piston pump 111 to which the hydraulic oil is supplied and discharged by rotating the cylinder block is used. The invention may be applied.

Furthermore, in the present embodiment, the piston motor constitutes the hydrostatic transmission (HST), but it may constitute another machine or facility.

The present application claims priority based on Japanese Patent Application No. 2013-73454 filed on March 29, 2013, to the Japan Patent Office, and the entire contents of this application are incorporated herein by reference.

Claims

A facing type swash plate type hydraulic rotary machine in which a first piston and a second piston protruding from both ends of a rotating cylinder block follow a first swash plate and a second swash plate to reciprocate in the cylinder,
A first tilt bearing that tiltably supports the first swash plate;
A first tilting drive piston that tilts the first swash plate in a direction intersecting the rotation axis of the cylinder block;
A second tilt bearing that tiltably supports the second swash plate;
An opposite type swash plate type hydraulic rotating machine comprising: a second tilt drive piston which tilts the second swash plate in a direction intersecting with the rotation axis of the cylinder block.
The counter-type swash plate type hydraulic rotating machine according to claim 1, wherein
A first push side piston pressure chamber and a first pull side piston pressure chamber defined at both ends of the first tilt drive piston;
A first tilt control valve that switches the flow of working fluid supplied and discharged from the high pressure selection valve to the first push side piston pressure chamber and the first pull side piston pressure chamber;
A second pushing piston pressure chamber and a second pulling piston pressure chamber defined at both ends of the second tilting drive piston;
A second tilt control valve for switching the flow of the working fluid supplied to / discharged from the high pressure selection valve to the second push side piston pressure chamber and the first pulling side piston pressure chamber; Machine.