Axial piston device

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to an axial piston device such as a pump unit or a motor unit.

2. Related Art

An axial piston device comprising a cylinder block rotated about an axis and a piston accommodated in a slidable manner in an axial direction with respect to the cylinder block while being rotated about the axis together with the cylinder block has been widely utilized as a pump unit to be used as a hydraulic source with respect to hydraulic equipment such as a hydraulic motor or as a motor unit to be hydraulically driven by a hydraulic source such as a hydraulic pump.

Hereinafter, description will be given of a conventional axial piston device by way of a pump unit.

A conventional pump unit comprises, for example, a housing which has a housing body opened at a first end thereof and a plate attached to the first end of the housing body, a pump shaft which is supported by the housing and is driven by a drive source, and a pump body which is accommodated inside the housing and is rotatably driven by the pump shaft, wherein each of a discharge port and a suction port of the pump body is hydraulically connected in circulation to a corresponding hydraulic device such as a hydraulic motor.

That is to say, a pair of oil passages communicating with the discharge port and the suction port of the pump body, respectively, is formed at the plate. Thus, pressurized oil is supplied from the pump body to the hydraulic device via one of the oil passages, and further, return oil is returned to the pump body from the hydraulic device via the other one of the oil passages.

In the pump unit after assembly, air is mixed inside the pair of oil passages; therefore, the pair of oil passages is required to be deaerated.

In other words, the pump unit and the hydraulic device are connected via the pair of oil passages, thereby forming a circulation circuit, wherein the circulation circuit is required to be sufficiently deaerated upon filling oil into the circulation circuit.

In regard to this point, in the conventional pump unit, a drain oil passage for allowing the pair of oil passages to communicate with an oil sump is formed at the plate, and further, a shutoff valve is disposed inside the drain oil passage in such a manner as to be positionally adjusted in an axial direction (see U.S. Pat. No. 6,332,393).

In particular, a valve seat is provided at the drain oil passage. The position of the shutoff valve in the axial direction can be adjusted in such a manner that the shutoff valve can take a shutoff position at which the shutoff valve is in contact with the valve seat so as to have the drain oil passage shut off and a communication position at which the shutoff valve is apart from the valve seat in the axial direction so as to have the drain oil passage communicated.

In this conventional pump unit, the pair of oil passages can communicate with or can be cut out of the oil sump by operating the shutoff valve, with an attendant problem of impossibility of speedy switching between the communication and shutoff.

Namely, in the conventional pump unit, the position of the shutoff valve in the axial direction can be adjusted with respect to the plate owing to screw connection. Consequently, in order to move the shutoff valve from the shutoff position to the communication position at which a sufficient opening width is secured, the shutoff valve must be rotated on an axis many times.

The present invention has been accomplished in view of the above prior art.

One object of the present invention is to provide an axial piston device in which an oil passage can be reliably and rapidly deaerated, and in which the rotary valve can be prevented from being pushed and moved toward the direction of exiting from a disposing hole, into which the rotary valve is inserted, during deaeration.

Another object of the present invention is to provide an axial piston device in which an oil passage can be reliably and rapidly deaerated, and in which an oil passage structure for deaerating could be simplified.

SUMMARY OF THE INVENTION

According to the present invention, there is provided an axial piston device including: a rotary shaft rotating about its axis; a cylinder block supported on the rotary shaft in a relatively non-rotatable manner; a plurality of pistons accommodated within the cylinder block in a slidable manner in the axial direction; a swash plate engaging directly or indirectly free ends of the pistons; a plate having a contact surface which is brought into contact with discharge/suction ports of the cylinder block, the plate being provided with a pair of first oil passages having first ends opened to the contact surface so as to fluidly connect with the discharge/suction ports of the cylinder block and second ends opened to a surface of the plate, and a drain oil passage for allowing at least one of the first oil passages to communicate with an oil sump; and a rotary valve operated and rotated around its axis so as to take a shutoff position at which the drain oil passage is shut off and a communication position at which the drain oil passage is communicated.

The drain oil passage includes an upstream-side drain oil passage fluidly connected to at least one of the pair of first oil passages; a downstream-side drain oil passage fluidly connected to the oil sump; and a disposing hole that intersects both the upstream-side drain oil passage and the downstream-side drain oil passage and that has a base end opened to the outer surface of the plate so that the rotary valve is inserted into the disposing hole through the base end.

The rotary valve includes a main body that has an outer peripheral surface liquid tightly contacting the inner peripheral surface of the disposing hole at an upstream-side connecting point where the upstream-side drain oil passage and the disposing hole intersect to each other; a small-diameter portion that is contracted with a step from the main body and that is extended towards the distal end side of the disposing hole from the main body, the small-diameter portion defining a space between the inner peripheral surface of the disposing hole and the outer peripheral surface of the small-diameter portion; a flange portion that is enlarged from the small-diameter portion with a step and is positioned at the distal end side of the disposing hole from a downstream-side connecting point where the downstream-side drain oil passage and the disposing hole intersect to each other, the flange portion having an outer peripheral surface that liquid tightly contacts the inner peripheral surface of the disposing hole; and a communication groove formed on the outer peripheral surface of the main body so as to extend from the position in the axial direction corresponding to the upstream-side connecting point to the space.

The communication groove is formed at the position in the circumferential direction so as to be fluidly shutoff with respect to the upstream-side drain oil passage when the rotary valve is positioned at the shutoff position, and fluidly connected to the upstream-side drain oil passage when the rotary valve is positioned at the communication position.

According to the configuration, since the rotary valve switches the communicating state and the shutoff state of the drain oil passage, the pair of first oil passages can be deaerated reliably and rapidly as much as possible.

Furthermore, according to the configuration, even if the oil pressure is increased in the space when the rotary valve is positioned at the communication position so that the pressure oil in the first oil passages is discharged into the oil sump, the pushing force produced by the oil pressure to push the rotary valve towards the base end side of the disposing hole is canceled out by the pushing force produced by the oil pressure to push the rotary valve towards the distal end side of the disposing hole. Therefore, it could be effectively prevented that the rotary valve is pushed and moved towards the direction of exiting from the disposing hole (i.e. the rotary valve is floated from the disposing hole) when the rotary valve is positioned at the communication position.

According to the present invention, there is still provided an axial piston device including: a rotary shaft rotating about its axis; a cylinder block supported on the rotary shaft in a relatively non-rotatable manner; a plurality of pistons accommodated within the cylinder block in a slidable manner in the axial direction; a swash plate engaging directly or indirectly free ends of the pistons; a plate having a contact surface which is brought into contact with discharge/suction ports of the cylinder block, the plate being provided with a pair of first oil passages having first ends opened to the contact surface so as to fluidly connect with the discharge/suction ports of the cylinder block and second ends opened to a surface of the plate, and a drain oil passage for allowing at least one of the first oil passages to communicate with an oil sump; and a rotary valve operated and rotated around its axis so as to take a shutoff position at which the drain oil passage is shut off and a communication position at which the drain oil passage is communicated.

The rotary valve includes a main body having an outer peripheral surface that liquid tightly contacting the inner peripheral surface of the disposing hole at an upstream-side connecting point where the upstream-side drain oil passage and the disposing hole intersect to each other and at a downstream-side connecting point where the downstream-side drain oil passage and the disposing intersect to each other; and a communication oil passage formed at the main body so as to have a first end and a second end respectively opened to the outer peripheral surface at the positions in the axial direction respectively corresponding to the upstream-side connecting point and the downstream-side connecting point.

The first end of the communication oil passage is opened to the outer peripheral surface at the position in the circumferential direction so as to be fluidly shutoff with respect to the upstream-side drain oil passage when the rotary valve is positioned at the shutoff position and fluidly connected to the upstream-side drain oil passage when the rotary valve is positioned at the communication position.

The second end of the communication oil passage is opened to the outer peripheral surface at the position in the circumferential direction so as to be fluidly connected to the downstream-side drain oil passage when the rotary valve is positioned at the communication position.

In the above various configurations, the axial piston device preferably further includes a housing surrounding the cylinder block. The housing is configured such that an inside space thereof is used as the oil sump.

More preferably, the housing may be configured in such a manner as to surround the plate in addition to the cylinder block, and the second ends of the pair of first oil passages may be fluid-connected to conduit members supported by the housing astride inward and outward of the housing.

Alternatively, the axial piston device may further include a housing body having an opening formed at a first end thereof. The housing body surrounds the cylinder block. The plate is configured in such a manner as to be connected to the housing body so as to close the opening formed at the first end of the housing body. In the configuration, the housing body and the plate form the housing.

According to the present invention, there is still provided an axial piston device including: a rotary shaft rotating about its axis; a cylinder block supported on the rotary shaft in a relatively non-rotatable manner; a plurality of pistons accommodated in the cylinder block in a slidable manner in the axial direction; a swash plate engaging directly or indirectly free ends of the pistons; a plate having a contact surface which is brought into contact with discharge/suction ports of the cylinder block, the plate being provided with a pair of first oil passages having first ends opened to the contact surface so as to fluidly connect with the discharge/suction ports of the cylinder block and second ends opened to a surface of the plate, and a drain oil passage for allowing at least one of the first oil passages to communicate with an oil sump; and a rotary valve operated and rotated around its axis so as to take a shutoff position at which the drain oil passage is shut off and a communication position at which the drain oil passage is communicated.

The pair of oil passages are substantially parallel to each other with the rotary shaft sandwiched therebetween and extended in a direction orthogonal to the axis of the rotary shaft.

The rotary valve is inserted in a rotatable manner around an axis into a disposing hole formed at the plate so as to be substantially parallel to the pair of oil passages between the pair of oil passages.

According to the configuration, the drain oil passage could be formed without enlarging the plate. Furthermore, both of the pair of first oil passages could be fluidly connected to the oil sump without a complicated oil passage structure.

BRIEF DESCRIPTION OF THE DRAWINGS

The above, and other objects, features and advantages of the present invention will become apparent from the detailed description thereof in conjunction with the accompanying drawings wherein.

FIG. 1 is a longitudinal cross-sectional view showing an axial piston unit according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along a line II-II of FIG. 1.

FIG. 3 is a cross-sectional view taken along a line III-III of FIG. 1.

FIG. 4 is a view as viewed from an arrow IV of FIG. 2.

FIG. 5 is a view as viewed from an arrow V of FIG. 4.

FIG. 6 is a diagram illustrating a hydraulic circuit of the axial piston unit shown in FIGS. 1-5.

FIG. 7 is a perspective view showing a plate of the axial piston unit shown in FIGS. 1-6, as viewed from the inner surface.

FIG. 8 is a cross-sectional view taken along a line VIII-VIII of FIG. 1.

FIG. 9 is a longitudinal cross-sectional view showing an axial piston unit according to a second embodiment of the present invention.

FIG. 10 is a cross-sectional view taken along a line X-X of FIG. 9.

FIG. 11 is a cross-sectional view taken along a line XI-XI of FIG. 9.

FIG. 12 is a view as viewed from an arrow XII of FIG. 10.

FIG. 13 is a cross-sectional view of a plate of a modified axial piston unit shown in FIGS. 9-13.

FIG. 14 is a laterally partial plan view showing an axial piston device according to a third embodiment of the present invention.

FIG. 15 is a cross-sectional view taken along a line XV-XV of FIG. 14.

FIG. 16 is a cross-sectional view taken along a line XVI-XVI of FIG. 14.

FIG. 17 is a vertical cross-sectional rear view of an axial piston device according to a fourth embodiment of the present invention.

FIG. 18 is a cross-sectional view taken along a line XVIII-XVIII of FIG. 17.

FIG. 19 is an enlarged view showing the section XIX in FIG. 15 in a state where a rotary valve of the axial piston device according to the fourth embodiment is positioned at a communication position.

FIG. 20 is a perspective view of the rotary valve of the axial piston device according to the fourth embodiment.

FIG. 21 is a cross-sectional view showing the vicinity of a rotary valve of an axial piston device according to a fifth embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Embodiment 1

Hereinafter, description will be given of an axial piston device according to a preferred embodiment of the present invention with reference to the attached drawings.

An axial piston device according to this embodiment is used as a pump unit, i.e., a hydraulic source with respect to hydraulic equipment such as a hydraulic motor.

FIG. 1 is a longitudinal cross-sectional view showing a pump unit 1 according to this embodiment. Furthermore, FIGS. 2 and 3 are a cross-sectional view taken along a line II-II of FIG. 1 and a cross-sectional view taken along a line III-III of FIG. 1, respectively. Moreover, FIGS. 4 and 5 are views as viewed from an arrow IV of FIG. 2 and an arrow V of FIG. 4, respectively.

As shown in FIGS. 1 to 3, the pump unit 1 according to this embodiment includes a housing 10, a pump shaft 40 to be operatively driven by a drive source (not shown), and a first pump body 50 to be driven by the pump shaft 40.

The housing 10 is configured in such a manner as to accommodate the first pump body 50 therein while rotatably supporting the pump shaft about an axis.

In this embodiment, the housing 10 has a hollow housing body 20 opened at a first end thereof, and a plate 30 disposed at the first end of the housing body 20.

Here, in this embodiment, the housing body 20 is bottomed by closing a second end thereof.

Specifically, the housing body 20 is provided with a side wall 21 having a positioning boss for installing a pump body, and a circumferential wall 22 extending from the peripheral edge portion of the side wall 21 toward a direction of the pump shaft.

The plate 30 is preferably configured in such a manner as to liquid-tightly close an opening 20a at the first end of the housing body 20, and therefore, an inside space 11 of the housing 10 can be used as an oil sump.

The pump shaft 40 is rotatably supported on an axis by the housing body 20 and the plate 30 in a state in which an input end extends outward in such a manner as to be operatively connected to the drive source.

In the pump shaft 40 in this embodiment, a first end 41 located upstream in a transmission direction (i.e., a right end in FIGS. 1 and 2) extends outward of the side wall 21 of the housing body 20, and further, a second end 42 located downstream in the transmission direction (i.e., a left end in FIGS. 1 and 2) also extends outward of the plate 30.

Incidentally, a second pump body 80, described later, is supported at the second end 42 located downstream in the transmission direction of the pump shaft 40.

The first pump body 50 is accommodated inside the housing 10 in such a state as to be freely driven by the pump shaft 40.

The first pump body 50 in this embodiment is configured in a variable displacement type in which a suction/discharge oil rate can be varied according to a slanting position of an output adjusting member 53.

In particular, the first pump body 50 includes a cylinder block 51 supported by the pump shaft 40 in a relatively non-rotatable manner, a piston 52 slidable in the pump shaft direction with respect to the cylinder block 51 while rotating on the pump shaft 40 together with the cylinder block 51, and the output adjusting member 53.

The output adjusting member 53 is provided with a movable swash plate 54 defining a sliding range in the pump shaft direction of the piston 52 according to a position of the piston unit 52 around the pump shaft 40, a connecting arm 55 having a first end connected to the movable swash plate 54, and a control shaft 56 supported by the housing 10 in a rotatable manner on the axis so as to have a first end connected to a second end of the connecting arm 55 and have a second end located outward of the housing 10.

An operating arm 61 is connected to the second end of the control shaft 56, and thus, the control shaft 56 is rotated on the axis by oscillating the operating arm 61 on the axis of the control shaft 56.

As shown in FIGS. 2 to 4, the first pump body 50 in this embodiment includes a neutral position returning mechanism 60 for returning the movable swash plate 54 to a neutral position.

The neutral position returning mechanism 60 is provided with the operating arm 61, a locking pin 62 disposed at a first end 61a of the operating arm 61, a fixed pin 63 fixedly disposed at the housing 10, and a coil spring 64 wound around the outer portion of the control shaft 56.

A second end 61b of the operating arm 61 functions as an operating portion. That is to say, the control shaft 56 is rotated about its axis by oscillating the second end 61b of the operating arm 61 about the control shaft 56, so that the movable swash plate 54 is slanted.

The coil spring 64 includes a central portion 64a wound around the outer portion of the control shaft 56, and a first end 64b and a second end 64c extending from the central portion 64a. The fixed pin 63 and the locking pin 62 are held between the first end 64b and the second end 64c of the coil spring 64.

With this configuration, the fixed pin 63 is adapted to position the movable swash plate 54 at the neutral position in a state in which no operating force is applied to the operating arm 61 from the outside. In other words, the fixed pin 63 functions as a neutral position setting member defining the neutral position of the movable swash plate 54.

Particularly, when the operating arm 61 is oscillated toward one side about the control shaft 56, the movable swash plate 54 is oscillated in a corresponding direction according to the rotation of the control shaft 56 about the axis, and further; the locking pin 62 is also oscillated toward one side about the control shaft.

When the locking pin 62 is oscillated in the above manner, the coil spring 64 is oscillated at only the first end 64b toward one side about the control shaft 56 in a state in which the second end 64c is held by the fixed pin 63, whereby the coil spring 64 retains its resiliency.

Therefore, when the operating force exerted on the operating arm 61 is released, the locking pin 62 and the operating arm 61 are returned to the neutral position by the resiliency retained by the coil spring 64, and accordingly, the movable swash plate 54 is returned to the neutral position.

Preferably, the neutral position returning mechanism 60 may be configured such that the position of the fixed pin 63 can be adjusted relative to the axis position of the control shaft 56.

In particular, the fixed pin 63 can have an eccentric structure. Namely, the fixed pin 63 can be configured to include a first portion 63a, at which the position relative to the axial position of the control shaft 56 is made invariable, and a second portion 63b, which is eccentric from the first portion 63a and is held between the first end 64b and the second end 64c of the coil spring 64.

With this configuration, the position of the second portion 63b relative to the axial position of the control shaft 56 can be readily varied by rotating the first portion 63a about the axis.

Consequently, the position of the second portion 63b relative to the axial position of the control shaft 56 can be easily adjusted to a proper position corresponding to the neutral position of the movable swash plate 54.

Although the first pump body 50 is of a variable displacement type in this embodiment, it may be of a fixed displacement type. If the first pump body 50 is of a fixed displacement type, a fixed swash plate is replaced with the output adjusting member 53.

Next, description will be given of a hydraulic circuit in the pump unit 1 according to this embodiment.

FIG. 6 is a diagram illustrating a hydraulic circuit of the pump unit 1 according to this embodiment.

As illustrated in FIGS. 3 and 6, the plate 30 is provided with a pair of first oil passages 101a, 101b which have first ends forming kidney ports so as to communicate with a discharge port 50a and a suction port 50b of the first pump body 50, respectively, and a drain oil passage 110 for allowing the pair of first oil passages 101a, 101b to communicate with the oil sump.

Each of the pair of first oil passages 101a, 101b has a second end opened to the outer surface of the plate 30. The opening ends constitute pressurized oil supplying/discharging ports 102a, 102b for communicating with a hydraulic device such as a hydraulic motor in cooperation with the pump unit 1.

The first oil passages 101a, 101b are arranged in a substantially linear manner substantially symmetrically with each other in reference to the pump shaft 40 in this embodiment, as shown in FIG. 3.

The drain oil passage 110 has a first end communicating with at least one of the first oil passages 101a, 101b, and a second end communicating with the oil sump.

In this embodiment, the drain oil passage 110 includes a single substantially linear cross oil passage 111 for allowing the pair of first oil passages 101a, 101b to communicate with each other, and a connecting oil passage 112 having a first end communicating with the cross oil passage 111 and a second end opened to the surface of the plate 30, as shown in FIGS. 1 and 3.

As described above, in this embodiment, the inside space 11 of the housing 10 commonly serves as the oil sump. Consequently, the second end of the connecting oil passage 112 is opened to an inner surface facing to the housing inside space 11 of the plate 30.

Here, to the inner surface of the plate 30 is opened also the pair of first oil passages 101a, 101b in addition to the drain oil passage 110.

The pump unit 1 according to this embodiment adopts a configuration below in order to prevent any interference of the pair of first oil passages 101a, 101b and the drain oil passage 110 and to allow these oil passages to communicate with the housing inside space 11.

FIG. 7 is a perspective view showing the plate 30, as viewed from the inner surface.

As shown in FIGS. 1, 2 and 7, the pump unit 1 according to this embodiment includes a valve plate 70 interposed between the plate 30 and the first pump body 50.

The valve plate 70 is configured such that it can rotatably support the cylinder block 51, and further, that it allows the discharge port 50a and the suction port 50b of the first pump body 50 to communicate with the first ends of the first oil passages 101a, 101b, respectively.

At the inner surface of the plate 30, a groove 113 is formed in such a manner as to be opened toward the valve plate 70. The groove 113 extends outward in a radial direction beyond the valve plate 70 in reference to the pump shaft 40.

With this configuration, the second end of the connecting oil passage 112 is opened to the groove 113.

Namely, in this embodiment, the drain oil passage 110 also includes the groove 113 in addition to the cross oil passage 111 and the connecting oil passage 112.

Most part of the groove 113 except for an outer end in a radial direction is designed to be closed by the back surface of the valve body 70 (i.e., a surface in contact with the plate 30) when the valve plate 70 is disposed at the inner surface of the plate 30. As a consequence, a simple structure can allow the drain oil passage 110 to communicate with the oil sump, i.e., the housing inside space 11 without exerting any adverse influence on the oil supplying/discharging function of the cylinder block 51 while preventing the interference with the pair of oil passages 101a, 101b and the drain oil passage 110.

As shown in FIGS. 1 and 3, a disposing hole 120, which has a first end opened to the outer surface of the plate 30 and a second end communicating with the drain oil passage 110, is formed at the plate 30 in addition to the above-described various oil passages.

Furthermore, a rotary valve 130 is inserted into the disposing hole 120 in a rotatable manner about its axis in the state in which the outer end extends outward of the plate 30.

The rotary valve 130 shuts off the drain oil passage 110 when it is located at a predetermined shutoff position about the axis with respect to the disposing hole 120 (see FIG. 3); in contrast, it allows the communication of the drain oil passage 110 when it is located at a communication position at which it is rotated about the axis by a predetermined angle from the shutoff position.

In other words, the rotary valve 130 is switchably operated between the shutoff position and the communication position according to the position about the axis with respect to the disposing hole 120.

Incidentally, in this embodiment, the shutoff position and the communication position can be selectively switched by rotating the rotary valve 130 at 90° about the axis.

Moreover, in this embodiment, the rotary valve 130 includes a detent mechanism 130a which holds the rotary valve 130 at the shutoff position and the communication position.

That is to say, a seal cap 131 coaxial with the disposing hole 120 is screwed at the disposing hole 120 opened to one side end face of the plate 30, and an operating shaft 132 of the rotary valve 130 projects outward of the seal cap 131 and is provided with a handle 133.

Additionally, at the outer edge of the handle 133 are formed two projections 133a, 133b having the same shape as each other at an interval of 90° in a circumferential direction, as shown in FIG. 5.

Furthermore, a positioning plate 134 having a substantial L-shape as viewed in cross section is disposed at the one side end face of the plate 30. The positioning plate 134 includes a lateral plate portion in contact with the one side end face of the plate 30 and a vertical plate portion extending from the lateral plate portion along the axial direction of the rotary valve 130. At the vertical plate portion is formed a recess 134a into which the projection 133a or 133b can be fitted.

The detent mechanism 130a is configured in the above-described manner. Therefore, the projection 133a is fitted into the recess 134a when the rotary valve 130 is located at the shutoff position, so that the handle 133 is held at that position; in contrast, the projection 133b is fitted into the recess 134a when the rotary valve 130 is located at the communication position, so that the handle 133 is held at that position.

In the pump unit 1 having this configuration, the pair of first oil passages 101a, 101b can be remarkably speedily and readily deaerated in comparison with the conventional pump unit.

In the prior art in which the shutoff and communication of the drain oil passage are switched by moving the shutoff valve screwed into the plate in the axial direction, a communication opening width of the drain oil passage cannot be sufficiently secured unless the shutoff valve is rotated about the axis several times.

Furthermore, with this conventional configuration, the valve seat is required to be disposed at a deep portion of the oil passage into which the shutoff valve is screwed.

In contrast, in the pump unit 1 according to this embodiment, the shutoff and communication of the drain oil passage 110 can be switched without rotating the rotary valve 130 once about the axis (only by rotation at 90° in this embodiment), and thus, the pair of first oil passages 101a, 101b can be remarkably speedily deaerated.

Furthermore, in this embodiment, no valve seat is required to be disposed, unlike the prior art, and therefore, the drain oil passage 110 can be readily bored.

Moreover, in the pump unit 1 according to this embodiment, a charge oil passage 140 for supplying charge oil to the pair of first oil passages 101a, 101b is formed at the plate 30, as illustrated in FIGS. 3 and 6.

The charge oil passage 140 includes a first bypass oil passage 141 for allowing the pair of first oil passages 101a, 101b to communicate with each other, and a suction oil passage 142 which has a first end connected to the first bypass oil passage 141 and a second end communicating with the housing inside space 11.

Check valves 150a, 150b for allowing an oil flow from the suction oil passage 142 to the pair of first oil passages 101a, 101b and preventing a reverse oil flow are interposed between a connecting point of the first bypass oil passage 141 to the suction oil passage 142 and the pair of first oil passages 101a, 101b, respectively.

In this embodiment, a throttle 155 is disposed in the check valve 150b interposed between the first oil passage 101b of the first oil passages 101a, 101b and the charge oil passage 140, thereby increasing a neutral width of the first pump body 50.

Additionally, a self-sucking throttle 145 in the case where either one of the first oil passages 101a, 101b becomes low in pressure due to oil leakage is provided on the charge oil passage 140. The inside of each of the first oil passages 101a, 101b can be kept in a state full of oil all the time by providing the throttle 145. As a consequence, in the case where the pump unit 1 according to the present invention is used as, for example, a drive source for a vehicle traveling hydraulic motor, there is no danger that a vehicle cannot be rolled down toward a ravine even if the vehicle is parked on a slope without applying parking brake.

Here, in this embodiment, the second end of the suction oil passage 142 is opened to the groove 113. As described above, most part of the groove 113 except for the outer end in the radial direction is closed by the valve plate 70. As a consequence, the simple structure can allow the suction oil passage 142 to communicate with the housing inside space 11 without exerting any adverse influence on the oil supplying/discharging function of the cylinder block 51 while preventing the interference with the pair of first oil passages 101a, 101b and the drain oil passage 110.

In addition to the above configurations, the pump unit 1 according to this embodiment includes the second pump body 80 to be driven by the pump shaft 40, and a pair of second oil passages 201a, 201b communicating with a discharge port 80a and a suction port 80b of the second pump body 80, respectively.

The second pump body 80 is adapted to supply pressurized oil to the hydraulic device in cooperation with the first pump body 50 or another hydraulic device other than the hydraulic device.

In this embodiment, the second pump body 80 is supported at the second end 42 downstream in the transmission direction of the pump shaft 40 (i.e., the left end in FIGS. 1 and 2).

FIG. 8 is a cross-sectional view taken along a line VIII-VIII of FIG. 1.

As shown in FIGS. 1 to 8, the pair of second oil passages 201a, 201b is bored in a pump case 90 surrounding the second pump body 80.

That is to say, the pump unit 1 according to this embodiment includes the pump case 90 connected to an outer surface on a side opposite to the inner surface of the plate 30 in such a manner as to surround the second pump body 80. The pair of second oil passages 201a, 201b is formed in the pump case 90.

In particular, the second oil passages 201a, 201b have first ends communicated with the discharge port 80a and the suction port 80b of the second pump body 80, respectively, second ends opened to the surface of the pump case 90, thereby forming a discharge port 202a and a suction port 202b, respectively.

As shown in FIGS. 6 and 8, a relief valve 210 for setting an operating oil pressure for the hydraulic device in cooperation with the second pump body 80 is inserted into the positive pressure oil passage 201a communicating with the discharge port 80a of the second pump body 80 out of the pair of second oil passages 201a, 201b.

In this embodiment, a bypass oil passage 220 for allowing the second oil passages 201a, 201b to communicate with each other is formed in the pump case 90, and thus, the relief valve 210 is inserted into the bypass oil passage 220.

In contrast, the negative pressure oil passage 201b communicating with the suction port 80b in the second pump body 80 out of the pair of second oil passages 201a, 201b is connected to the pair of first oil passages 101a, 101b.

Namely, at least a part of the oil, which is supplied from the discharge port 80a of the second pump body 80 to the hydraulic device via one of the second oil passages (i.e., the positive pressure oil passage 201a) and is returned to the suction port 80b of the second pump body 80 via the other one of the second oil passages (i.e., the negative pressure oil passage 201b), is designed to be introduced to the pair of first oil passages 101a, 101b, thereby speedily deaerating the pair of second oil passages 201a, 201b by use of the rotary valve 130.

In this embodiment, the plate 30 includes a first connecting oil passage 231 which has a first end communicating with the charge oil passage 140 and a second end opened to the surface in contact with the pump case 90, as shown in FIG. 1.

Furthermore, the pump case 90 is provided with a second connecting oil passage 232 which has a first end communicating with the negative pressure oil passage 201b and a second end opened to the surface in contact with the plate 30, so as to communicate with the first connecting oil passage 231.

In other words, the negative pressure oil passage 201b is designed to communicate with the pair of first oil passages 101a, 101b via the second connecting oil passage 232, the first connecting oil passage 231 and the charge oil passage 140.

Moreover, a charge relief valve 240 for setting an oil pressure of the pressurized oil flowing to the charge oil passage 140 from the negative pressure oil passage 201b is inserted into the negative pressure oil passage 201b.

Additionally, in the pump case 90 is formed a suction oil passage 250 which has a first end opened to the surface so as to form a suction port 250a and a second end communicating with the negative pressure oil passage 201b.

Incidentally, reference numeral 260 in FIG. 1 designates a drain port for draining the oil reserved inside the housing inside space 11.

In addition, reference numeral 270 in FIG. 6 designates a leak oil passage from the first pump body 50 to the oil sump (i.e., the housing inside space 11 in this embodiment).

Embodiment 2

Hereinafter, description will be given of an axial piston device according to another preferred embodiment of the present invention with reference to the attached drawings.

An axial piston device 1B according to this embodiment is also configured to be used as a pump unit in the same manner as in the first embodiment.

FIG. 9 is a longitudinal cross-sectional view showing the pump unit 1B according to this embodiment. Furthermore, FIGS. 10 and 11 are a cross-sectional view taken along a line X-X of FIG. 9 and a cross-sectional view taken along a line XI-XI of FIG. 9, respectively. Moreover, FIG. 12 is a view as viewed from an arrow XII of FIG. 10.

Here, in FIGS. 9 to 12, the same or corresponding components as or to those in the first embodiment are designated by the same reference numerals; therefore, the detailed description for those components will not be given herein.

The pump unit 1B according to this embodiment is configured in substantially the same manner as that in the first embodiment except that the movable swash plate 54 in the pump unit 1 in the first embodiment is replaced with a trunnion-type movable swash plate 54B and that the seat faces of the check valves 150a, 150b are constituted of components independent of the plate 30.

In particular, the pump unit 1B includes the trunnion-type movable swash plate 54B in place of the movable swash plate 54, as shown in FIGS. 9 and 10.

The above-described movable swash plate 54B of a trunnion type has small sliding resistance, so that the movable swash plate 54B can be speedily returned to a neutral position of the movable swash plate 54B by means of the neutral position returning mechanism 60.

Furthermore, the pump unit 1B includes a pair of seat members 151 to be inserted into the first bypass oil passage 141.

More particularly, the first bypass oil passage 141 includes a small-diameter portion 143 communicating with the suction oil passage 142 and a pair of large-diameter portions 144 whose diameter is enlarged with steps continuous from the small-diameter portion 143 and which communicates with the pair of first oil passages 101a, 101b, respectively, as shown in FIG. 11.

The pair of seat members 151 are disposed inside the large-diameter portions 144, respectively, so that each seat face 155 is oriented toward the corresponding first oil passages 101a, 101b.

Incidentally, the seat member 151 is fixed to the large-diameter portion 144 by, for example, a stopper ring (see FIG. 11) or press-fitting.

In this manner, a repairing work in the case of degradation of the seat face 155 can be readily performed at low cost by forming the seat face 155 of a member independent of the plate 30 (the seat member 151 in this embodiment).

In a situation in which the first pump body 50 is operated for a long period of time in the state of, for example, application of a high load, the check valves 150a, 150b are frequently opened and closed, whereby the seat face 155 is abraded, thereby inducing a possibility of leakage of operating oil from the pair of first oil passages 101a, 101b.

Especially in the case where the plate 30 is made of aluminum, the possibility of leakage is tended to become stronger.

In such a case, the seat face 155 can be repaired by only replacing the seat member 151, if the seat face 155 is formed of a member independent of the plate 30, like in this embodiment.

FIG. 13 is a cross-sectional view showing the plate 30 provided with cartridge-type check valves 152a, 152b.

As described above, the seat member 151 provided with the seat face 155 is used in this embodiment. Alternatively, there may be provided the cartridge-type check valves 152a, 152b each including a valve case having a seat face 155, as shown in FIG. 13.

Embodiment 3

Hereinafter, description will be given of an axial piston device according to still another preferred embodiment of the present invention with reference to the attached drawings.

FIG. 14 is a laterally partial plan view showing an axial piston device 1C according to this embodiment. Furthermore, FIGS. 15 and 16 are a cross-sectional view taken along a line XV-XV of FIG. 14 and a cross-sectional view taken along a line XVI-XVI of FIG. 14, respectively.

The axial piston device 1C according to this embodiment is configured to be used as a motor unit, unlike the first and second embodiments.

In other words, each of the axial piston devices 1, 1B according to the first and second embodiments includes the pump shaft 40 as the rotary shaft and the pump body 50 serving as the rotor rotatable together with the rotary shaft; in contrast, the axial piston device 1C according to this embodiment includes a motor shaft 340 as the rotary shaft and a motor body 350 serving as the rotor.

Specifically, the axial piston device 1C comprises the motor shaft 340, the motor body 350 including a cylinder block 351 fitted around in a non-rotatable manner relative to the motor shaft 340 and a plate 330 which is brought into contact with a discharge port and a suction port in the motor body 350. The motor block 351 is configured in such a manner as to be rotated with the application of an oil pressure from an oil source such as a hydraulic pump unit which is liquid-connected via the plate 330, thereby outputting rotational drive force from the motor shaft 340.

The axial piston device 1C according to this embodiment further comprises a housing 320 surrounding the motor body 350 and the plate 330, wherein its inside space serves as an oil sump.

As shown in FIGS. 14 to 16, an axle case for supporting a pair of drive axle shafts 400 for driving a pair of drive wheels is commonly used as the housing 320 in this embodiment.

That is to say, the axle case 320 includes first and second case bodies 321, 322 which are detachably connected to each other, so that a liquid-tight inside space can be defined by connecting the first and second case bodies 321, 322.

More particularly, the inside space of the axle case 320 is divided into a motor unit accommodating space 320a for accommodating therein the motor body 350 and the plate 330, a deceleration gear train accommodating space 320b for accommodating therein a deceleration gear train 410 operatively connected to the motor shaft 340, a differential gear unit accommodating space 320c for accommodating therein a differential gear unit 420 operatively connected to the deceleration gear train 410, and a drive axle shaft accommodating space 320d for accommodating therein a pair of drive axle shafts 400 operatively connected to the differential gear unit 420.

Incidentally, reference numeral 430 in FIG. 14 designates a brake mechanism capable of applying brake force to the motor shaft 340.

The motor shaft 340 has a base end supported by the plate 330 and a tip end supported on a partition wall of the axle case 320 in such a manner as to be exposed to the deceleration gear train accommodating space 320b.

The motor body 350 includes the cylinder block 351 fitted around in a non-rotatable manner relative to the motor shaft 340, a piston 352 accommodated inside the cylinder block 351 in a freely advancing/retreating manner in an axial direction, and a swash plate 354 defining an advancing/retreating range in the axial direction of the piston 352.

Here, the axial piston device 1C according to this embodiment is of a variable displacement type.

Consequently, the motor body 350 includes a movable swash plate serving as the swash plate 354. Furthermore, the motor body 350 includes a connecting arm 355 having a first end connected to the movable swash plate 354, and a control shaft 356 supported by the housing 320 in a rotatable manner about an axis so as to have a first end connected to a second end of the connecting arm 355 and a second end positioned outward of the housing 320.

As shown in FIG. 15, at the plate 330 are disposed a pair of oil passages 301a, 301b having first ends communicating with a discharge port and a suction port of the motor body 350, respectively, and a drain oil passage 310 for allowing the pair of oil passages 301a, 301b to communicate with the oil sump.

More particularly, as shown in FIG. 14, each first end of the pair of oil passages 301a, 301b is opened to a contact surface 331 in contact with the motor body in outer surface of the plate 330.

Furthermore, each second end of the pair of oil passages 301a, 301b is opened to a back surface 332 on a side opposite to the contact surface 331.

As described above, the plate 330 is also surrounded by the housing 320 in this embodiment.

As a consequence, each second end of the pair of oil passages 301a, 301b is fluid-connected to a hydraulic source such as a hydraulic pump via a conduit member 305 supported by the housing 320 astride inward and outward of the housing 320 (see FIGS. 14 and 16).

The drain oil passage 310 has a first end communicating with at least one of the oil passages 301a, 301b, and a second end communicating with the oil sump (i.e., the inside space of the housing 320 in this embodiment).

According to this embodiment, the drain oil passage 310 includes a single cross oil passage 311 of a substantially linear shape for allowing the pair of oil passages 301a, 301b to communicate with each other, and a connecting oil passage 312 having a first end communicating with the cross oil passage 311 and a second end opened to the back surface 332 of the plate 330, as shown in FIGS. 14 to 16.

Moreover, a disposing hole 120 is bored at the plate 330, like in the first and second embodiments and, further, a rotary valve 130 is inserted into the disposing hole 120 in a rotatable manner about an axis.

Incidentally, according to this embodiment, the outer end of the rotary valve 130 extends outward of the housing 320 (i.e., the axle case) such that the rotary valve 130 can be operated outward of the housing 320.

Additionally, a handle 133 is attached to an outward extending portion 132 at the rotary valve 130, like in the first and second embodiments.

As shown in FIGS. 15 and 16, a projection 133a is formed at the handle 133.

An engaging recess 134a formed is integrally with the housing 320. The projection 133a and the engaging recess 134a constitute a detent mechanism 130a for holding the rotary valve 130 at cutoff/communication positions.

Embodiment 4

Hereinafter, description will be given of an axial piston device according to still another preferred embodiment of the present invention with reference to the attached drawings.

FIG. 17 is a vertical cross-sectional rear view of an axial piston device 1D according to this embodiment. Furthermore, FIG. 18 is a cross-sectional view taken along a line XVIII-XVIII of FIG. 17.

The same or corresponding components as or to those in each of the above embodiments are designated by the same reference numerals; therefore, the detailed description for those components will not be given herein.

The axial piston device 1D according to this embodiment has a drain structure of a configuration different from each of the above embodiments.

An example in which the drain structure is applied to the motor unit is described in this embodiment, but the drain structure may obviously be applied to the pump unit.

In the drain structure according to each of the above embodiments, the rotary valve 130 may be sometimes pushed and moved into a direction of exiting from the disposing hole 120 by the pressure oil flowing from the pair of oil passages 101a, 101b (301a, 301b) to the oil sump when communicating the corresponding pair of oil passages 101a, 101b (301a, 301b) to the oil sump.

The drain structure according to this embodiment effectively prevents such disadvantages.

The drain structure according to each of the above embodiments will first be described.

FIG. 19 is an enlarged view showing the section XIX in FIG. 15 in a state where the rotary valve 130 is positioned at a communication position.

As shown in FIG. 19, the drain oil passage 310 includes an upstream-side drain oil passage 311 fluidly connected to at least one of the pair of oil passages 301a, 301b, a downstream-side drain oil passage 312 fluidly connected to the oil sump (internal space of the housing 320 in the illustrated embodiment), and the disposing hole 120 that crosses both the upstream-side drain oil passage 311 and the downstream-side drain oil passage 312 and that has a base end opened to the outer surface of the plate.

In the illustrated embodiment, the upstream-side drain oil passage 311 is fluidly connected to both of the pair of oil passages 301a, 301b. That is, the upstream-side drain oil passage 311 includes a first upstream-side drain oil passage 311a fluidly connected to one of the pair of oil passages 301a, and a second upstream-side drain passage 311b fluidly connected to the other one of the pair of oil passages 301b.

The rotary valve 130 is inserted into the disposing hole 120, as described above.

Specifically, the rotary valve 130 is inserted into the disposing hole 120 with a gap 121 formed between the distal end face of the rotary valve 130 and the distal end of the disposing hole 120.

The downstream-side drain oil passage 312 has a first end fluidly connected to the oil sump and a second end opened to the gap 121.

The rotary valve 130 has an outer peripheral surface that liquid tightly contacts the inner peripheral surface of the disposing hole 120 at an upstream-side connecting point 311T where the upstream-side drain oil passage 311 and the disposing hole 120 intersect.

Furthermore, the rotary valve 130 is formed with a communication oil passage 135 that causes the drain oil passage 310 to be in the communicating state when the rotary valve 130 is positioned at the communication position and the drain oil passage 310 to be in the shutoff state when the rotary valve 130 is positioned at the shutoff position.

As shown in FIG. 19, the communication oil passage 135 has a first end opened to the outer peripheral surface and a second end opened to the distal end face so as to be fluidly connected to the gap 121.

Specifically, the first end of the communication oil passage 135 is opened to the outer peripheral surface of the rotary valve 130 at a circumferential position so as to be fluidly shutoff with respect to the upstream-side drain oil passage 311 when the rotary valve 130 is positioned at the shutoff position, and fluidly connected to the upstream-side drain oil passage 311 when the rotary valve 130 is positioned at the communication position.

In this embodiment, the upstream-side drain oil passage 311 includes the first and second upstream-side drain oil passages 311a, 311b, as described above.

Therefore, the first end of the communication oil passage 135 is branched into two ends so that both the first and second upstream-side drain oil passages 311a, 311b are fluidly connected to the communication oil passage 135 when the rotary valve 130 is positioned at the communication position.

The rotary valve 130 operates in the following manner.

That is, when positioning the rotary valve 130 at the shutoff position (see FIG. 15), the upstream-side drain oil passage 311 is shutoff with respect to the disposing hole 120 by the outer peripheral surface of the rotary valve 130, and therefore the oil passages 301a, 301b are maintained in a closed circuit.

In contrast, when positioning the rotary valve 130 at the communication position (see FIG. 19), the upstream-side drain oil passage 311 is fluidly connected to the oil sump by way of the communication oil passage 135, the gap 121 and the downstream-side drain oil passage 312. Therefore, the pressure oil in the oil passages 301a, 301b is discharged into the oil sump.

However, in the rotary valve 130, the communication oil passage 135 is fluidly connected to the downstream-side drain oil passage by way of the gap 121, as described above.

In the configuration, the oil pressure is produced in the gap 121 when the rotary valve 130 is positioned at the communication position and the pressure oil in the oil passages 301a, 301b is discharged into the oil sump. The oil pressure pushes the rotary valve 130 into the direction L of exiting from the disposing hole 120.

Therefore, in the rotary valve 130 according to each of the above embodiments, the rotary valve 130 floats from the disposing hole 120 by the oil pressure produced in the gap 121, whereby disadvantages may occur such that the pressure oil is inhibited from flowing from the upstream-side drain oil passage 311 into the communication oil passage 135, and the detent mechanism 130a is more likely to disengage the rotary valve 130.

In view of the above points, the axial piston device 1D according to this embodiment has a drain structure of the following configuration.

That is, the axial piston device 1D according to this embodiment includes a rotary valve 130D in place of the rotary valve 130 in the axial piston device 1C according to embodiment 3, as shown in FIGS. 17 and 18.

Specifically, the axial piston device 1D includes the rotary shaft 340 rotating about its axis; the cylinder block 351 mounted on the rotary shaft 340 in a relatively non-rotatable manner; the plurality of pistons 352 accommodated in the cylinder block 351 in a slidable manner along the axial direction of the rotary shaft 340; the swash plate 354 for directly or indirectly engaging the free end of the plurality of pistons 352 so as to define a sliding range of the piston 352; the plate 330 having a contact surface 331 which is brought into contact with the discharge port and the suction port of the cylinder block 351; and the rotary valve 130D.

Components other than the rotary valve 130D are the same as the components in the above embodiments. Therefore, the detailed explanation thereof is not repeated here.

FIG. 20 is a perspective view of the rotary valve 130D.

As shown in FIGS. 17, 18, and 20, the rotary valve 130D includes a main body 136D having an outer peripheral surface that liquid tightly contacts the inner peripheral surface of the disposing hole 120 at the upstream-side connecting point 311T where the upstream-side drain oil passage 311 and the disposing hole 120 intersect; a small-diameter portion 137D that is contracted with a step 136D′ from the main body 136D and that is extended towards the distal end side of the disposing hole 120 from the main body 136D, the small-diameter portion 137D defining a space S between the inner peripheral surface of the disposing hole 120 and the outer peripheral surface of the small-diameter portion 137D; a flange portion 138D that is enlarged from the small-diameter portion 137D with a step 138D′ and is positioned at the distal end side of the disposing hole 120 from the downstream-side connecting point 312T where the downstream-side drain oil passage 312 and the disposing hole 120 intersect, the flange portion 138D having an outer peripheral surface that liquid tightly contacts the inner peripheral surface of the disposing hole 120; and a communication groove 139D formed on the outer peripheral surface of the main body 136D so as to extend from the position in the axial direction corresponding to the upstream-side connecting point 311T to the space S.

The base end of the main body 136D extends outward as shown in FIG. 17, and forms the operating shaft 132 that is externally operable.

The communication groove 139D is formed at the position in the circumferential direction so as to be fluidly shutoff with respect to the upstream-side drain oil passage 311 when the rotary valve 130D is positioned at the shutoff position, and fluidly connected to the upstream-side drain oil passage 311 when the rotary valve 130D is positioned at the communication position.

In this embodiment, the upstream-side drain oil passage 311 includes the first and second upstream-side drain oil passages 311a, 311b, as shown in FIG. 18.

Therefore, the communication groove 139D includes a first communication groove 139Da and a second communication groove 139Db respectively fluidly connected to the first and second upstream-side drain oil passages 311a, 311b, when the rotary valve 130D is positioned at the communication position.

The rotary valve 130D operates in the following manner.

That is, when positioning the rotary valve 130D at the shutoff position, the upstream-side drain oil passage 311 is shutoff with respect to the disposing hole 120 by the outer peripheral surface of the rotary valve 130D, and therefore the oil passages 301a, 301b are maintained in a closed circuit.

In contrast, when positioning the rotary valve 130D at the communication position, the upstream-side drain oil passage 311 is fluidly connected to the oil sump by way of the communication groove 139D, the space S, and the downstream-side drain oil passage 312, and the pressure oil in the oil passages 301a, 301b is discharged into the oil sump.

When positioning the rotary valve 130D at the communication position, the oil pressure is produced in the space S. While the oil pressure acts on the step 136D′ between the main body 136D and the small-diameter portion 137D to push the rotary valve 130D into a direction of exiting from the disposing hole 120, it acts on the step 138D′ between the small-diameter portion 137D and the flange portion 138D to push the rotary valve 130D towards the distal end side of the disposing hole 120.

That is, in the axial piston device 1D according to this embodiment, even if the oil pressure is increased in the space S when the rotary valve 130D is positioned at the communication position so that the pressure oil in the oil passages 301a, 301b is discharged into the oil sump, the pushing force produced by the oil pressure to push the rotary valve 130D towards the base end side of the disposing hole 120 is canceled out by the pushing force produced by the oil pressure to push the rotary valve 130D towards the distal end side of the disposing hole 120.

Therefore, in this embodiment, the disadvantage of the rotary valve 130D floating from the disposing hole 120 when positioned at the communication position is prevented, and thus the disadvantages such as the detent mechanism 130a being more likely to disengage the rotary valve 130D.

Embodiment 5

Hereinafter, description will be given of an axial piston device according to still another preferred embodiment of the present invention with reference to the attached drawings.

FIG. 21 is a cross-sectional view showing the vicinity of the rotary valve in an axial piston device 1E according to this embodiment.

Similar to the axial piston device 1D according to embodiment 4, the axial piston device 1E according to this embodiment has a drain structure configured so that the rotary valve 130E is effectively prevented from being pushed and moved into the direction of exiting from the disposing hole 120.

An example in which the drain structure is applied to the motor unit is described in this embodiment, but the drain structure may obviously be applied to the pump unit.

The axial piston device 1E according to this embodiment includes a rotary valve 130E in place of the rotary valve 130D in the axial piston device according to embodiment 4, as shown in FIG. 21.

As shown in FIG. 21, the rotary valve 130E includes a main body 136E having an outer peripheral surface that liquid tightly contacts the inner peripheral surface of the disposing hole 120 at the upstream-side connecting point 311T where the upstream-side drain oil passage 311 and the disposing hole 120 intersect and at the downstream-side connecting point 312T where the downstream-side drain oil passage 312 and the disposing hole 120 intersect; and a communication oil passage 135E formed at the main body 136E so as to have a first end and a second end respectively opened to the outer peripheral surface at the positions in the axial direction respectively corresponding to the upstream-side connecting point 311T and the downstream-side connecting point 312T.

Specifically, The first end of the communication oil passage 135E is opened to the outer peripheral surface at the position in the circumferential direction so as to be fluidly shutoff with respect to the upstream-side drain oil passage 311 when the rotary valve 130E is positioned at the shutoff position and fluidly connected to the upstream-side drain oil passage 311 when the rotary valve 130E is positioned at the communication position.

The second end of the communication oil passage 135E is opened to the outer peripheral surface at the position in the circumferential direction so as to be fluidly connected to the downstream-side drain oil passage 312 when the rotary valve 130E is positioned at the communication position.

In the axial piston device 1E having the drain structure of the above configuration, the rotary valve 130E is effectively prevented from being pushed and moved into a direction of exiting from the disposing hole 120 (i.e., rotary valve 130E is prevented from floating from the disposing hole 120) by the pressure oil when the rotary valve 130E is positioned at the communication position so that the pressure oil in the oil passages 301a, 301b is discharged into the oil sump.

Similar to embodiment 4, the upstream-side drain oil passage 311 includes the first and second upstream-side drain oil passages 311a, 311b in this embodiment.

Therefore, the first end of the communication oil passage 135E is branched into two ends so that both the first and second upstream-side drain oil passages 311a, 311b are fluidly connected to the communication oil passage 135E when the rotary valve 130E is positioned at the communication position.

In each of the above embodiments, the pair of oil passages 101a, 101b (301a, 301b) are substantially parallel to each other with the corresponding rotary shaft 40 (340) inbetween and are extended in a direction orthogonal to the axis of the rotary shaft 40 (340).

The disposing hole 120 is formed so as to be substantially parallel to the pair of oil passages 101a, 101b (301a, 301b) between the pair of oil passages 101a, 101b (301a, 301b), whereby both of the pair of oil passages 101a, 101b (301a, 301b) are fluidly connected to the oil sump by way of the rotary valve 130 (130D, 130E) without forming a complicated oil passage structure.

Therefore, deaeration of the oil passage is reliably and rapidly performed, while the oil passage structure for performing deaeration is simplified.

This specification is by no means intended to restrict the present invention to the preferred embodiments set forth therein. Various modifications to the axial piston device may be made by those skilled in the art without departing from the spirit and scope of the present invention as defined in the appended claims.

	Number	Date	Country
Parent	10931095	Sep 2004	US
Child	11498016	Aug 2006	US

Axial piston device

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CPC

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Abstract

Description

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Priority Claims (1)

Continuation in Parts (1)