WO2017169550A1

WO2017169550A1 - Tilt control device and hydraulic rotation device including same

Info

Publication number: WO2017169550A1
Application number: PCT/JP2017/008895
Authority: WO
Inventors: 啓森田; 直紀菅野; 智史前川
Original assignee: 株式会社神戸製鋼所
Priority date: 2016-03-28
Filing date: 2017-03-07
Publication date: 2017-10-05
Also published as: JP2017180125A

Abstract

Provided are a tilt control device that precisely transmits the movement of a spool of a control valve to a driving cylinder and achieves highly precise tilt control and a hydraulic rotation device including same. A tilt control device 1B controls the tilt of a variable displacement type rotation machine. The tilt control device 1B is provided with a housing 1H, a movable member 20, a spool 222, and a first position adjusting mechanism 2. The movable member 20 is connected to the eccentric ring of the rotation machine and allowed to move in the axial direction. The movable member 20 is provided with a connection part 21 and a tubular sleeve part 22. The spool 222 moves in the tubular inside of the sleeve part 22 in the axial direction. The first position adjusting mechanism 2 moves the spool 222 in the axial direction. The movable member 20 and the housing 1H form a driving cylinder that moves the eccentric ring, and the movable member 20 and the spool 222 form a control valve.

Description

Tilt control device and hydraulic rotation device provided with the same

The present invention relates to a tilt control device and a hydraulic rotation device including the tilt control device.

Conventionally, variable displacement hydraulic rotating machines that can be used as hydraulic pumps or hydraulic motors are known. Such a hydraulic rotating machine includes a housing, a rotating shaft, a cylinder block, and a plurality of pistons. The rotating shaft is rotatably supported by the housing. The cylinder block includes a plurality of cylinders formed along the circumferential direction of the rotation shaft, and rotates together with the rotation shaft. The pistons are respectively accommodated in a plurality of cylinders of the cylinder block and reciprocate as the cylinder block rotates.

When the hydraulic rotating machine is used as a hydraulic pump, the rotating shaft is rotated by the output of a predetermined driving unit, so that the cylinder block rotates together with the rotating shaft, and each piston reciprocates. At this time, the hydraulic oil flows into the cylinder of the cylinder block from the predetermined low pressure port, is pressurized by the piston, and is discharged from the predetermined high pressure port.

On the other hand, when the hydraulic rotating machine is used as a hydraulic motor, the high-pressure hydraulic oil flows into the cylinder of the cylinder block from the high-pressure port, so that the hydraulic fluid that has flowed in acts on the piston. After the reciprocating motion of the piston rotates the rotating shaft together with the cylinder block, the hydraulic oil is discharged from the low pressure port.

Patent Documents 1, 2, and 3 disclose techniques in which the extrusion capacity of a hydraulic pump is changed according to the axial movement of a servo cylinder. In Patent Document 1, when the servo valve spool is stroked according to the secondary pressure of the proportional valve, the servo cylinder connected to the sleeve of the servo valve via the spring moves in the axial direction. Moreover, in patent document 2, with respect to the eccentric ring that functions as a cylinder block, a servo cylinder and a servo valve and a regulator that regulates the position of the eccentric ring are arranged at different positions. Further, in Patent Document 3, when the spool of the servo valve is stroked by the secondary pressure of the proportional valve, the servo piston connected to the servo valve sleeve moves in the axial direction. The movement of the servo piston swings the swash plate of the hydraulic pump via the link mechanism.

JP-A-8-49264 Japanese Patent Laid-Open No. 2004-68796 Japanese Patent No. 4033849

In the hydraulic pumps described in Patent Documents 1 and 2, a spring is disposed between the servo valve and the servo cylinder. For this reason, the amount of movement of the servo cylinder is determined by the balance between the servo valve stroke and the urging force of the spring. As a result, there is a problem that the accuracy of the stroke control of the servo piston is lowered. In the hydraulic pump described in Patent Document 3, a link mechanism is disposed between the servo valve and the servo piston. For this reason, the structure of the hydraulic pump is complicated by the link mechanism, and the stroke control of the servo piston is difficult to stabilize.

An object of the present invention is to provide a tilt control device capable of accurately transmitting the movement of the spool of the control valve to the drive cylinder and realizing highly accurate tilt control, and a hydraulic rotation device including the tilt control device. There is to do.

A tilt control device according to one aspect of the present invention is a tilt control device that controls the tilt of a variable displacement hydraulic rotating machine including a tilt adjusting unit, and one end side in the axial direction is open to the outside. A housing provided with the cylinder portion, a connecting portion connected to the tilt adjusting portion of the hydraulic rotating machine, a cylindrical sleeve portion continuously provided to the connecting portion, and an inner peripheral surface of the cylinder portion And a first outer peripheral portion forming a hydraulic chamber into which hydraulic oil flows, and the cylinder is movable along the axial direction according to the hydraulic pressure of the hydraulic oil flowing into the hydraulic chamber And a movable member that constitutes a drive cylinder that moves the tilt adjusting portion together with the housing, and is accommodated inside the sleeve portion so as to be movable along the axial direction. A spool and the spool along the axial direction. And the movable member and the spool control the inflow of the hydraulic oil into the hydraulic chamber by the movement of the spool in the axial direction. An oil passage for guiding the hydraulic oil is formed so as to constitute a control valve.

A hydraulic rotation device according to another aspect of the present invention includes the above-described tilt control device, a rotating body including a plurality of cylinders, and a plurality of cylinders, which are respectively housed and reciprocated, The hydraulic rotating machine includes a plurality of pistons that perform suction and discharge, and the tilt adjustment unit that adjusts the reciprocation of the plurality of pistons.

It is sectional drawing of the hydraulic-pressure rotating apparatus which concerns on one Embodiment of this invention. It is sectional drawing of the tilt control apparatus of the hydraulic rotation apparatus which concerns on one Embodiment of this invention. It is a hydraulic circuit diagram in case the hydraulic rotation apparatus which concerns on one Embodiment of this invention is used as a hydraulic pump. It is sectional drawing which shows a mode that a movable member is moved in the tilt control apparatus of the hydraulic-pressure rotating apparatus which concerns on one Embodiment of this invention. It is sectional drawing which shows a mode that a movable member is moved in the tilt control apparatus of the hydraulic-pressure rotating apparatus which concerns on one Embodiment of this invention. It is sectional drawing which shows a mode that a movable member is moved in the tilt control apparatus of the hydraulic-pressure rotating apparatus which concerns on one Embodiment of this invention. It is sectional drawing which shows a mode that a movable member is moved in the tilt control apparatus of the hydraulic-pressure rotating apparatus which concerns on one Embodiment of this invention. FIG. 5 is a hydraulic circuit diagram of a hydraulic rotation device according to a modified embodiment of the present invention. It is sectional drawing of the tilt control apparatus of the hydraulic-pressure rotating apparatus which concerns on the deformation | transformation embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a hydraulic rotating device 1 according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the tilt adjustment mechanism 1B of the hydraulic rotating device 1 according to the embodiment of the present invention. FIG. 3 is a hydraulic circuit diagram when the hydraulic rotating device 1 according to one embodiment of the present invention is used as a hydraulic pump. In the following, in each figure, directions of “up”, “down”, “front” and “rear” are shown, and these directions indicate the tilt control device and the hydraulic rotation according to the present embodiment. It is shown for convenience in order to describe the structure of the apparatus, and does not limit the usage mode of the tilt control apparatus and the hydraulic rotation apparatus according to the present invention.

The hydraulic rotation device 1 according to the present embodiment functions as a hydraulic pump that discharges hydraulic oil by being connected to a drive source 100 (FIG. 3) such as an engine. The hydraulic rotating device 1 includes a rotating machine 1A (hydraulic rotating machine) and a tilt control device 1B.

Rotating machine 1A functions as a variable displacement radial piston type hydraulic rotating machine. The rotating machine 1A includes a casing 10, a rotating shaft 11, a cylinder block 12 (rotating body), a plurality of pistons 13, a retainer ring 14, an eccentric ring 15 (tilt adjusting unit), and a plurality of shoes 16. A pair of guide rails 17 and a timing plate 18 are provided.

The casing 10 functions as a housing that supports each member of the rotating machine 1A. The casing 10 has a cylindrical shape extending in the front-rear direction (direction orthogonal to the paper surface of FIG. 1), and has an internal space in which the rotating shaft 11, the cylinder block 12, the eccentric ring 15, and the like are accommodated. A shaft hole (not shown) that supports the rotating shaft 11 is provided at both ends of the casing 10 in the front-rear direction.

The rotating shaft 11 is disposed at a substantially central portion of the casing 10 and extends long in a direction (front-rear direction) orthogonal to the paper surface of FIG. The rotary shaft 11 is rotationally driven by a drive source 100 (FIG. 3).

The cylinder block 12 is a ring-shaped unit arranged around the rotating shaft 11. The cylinder block 12 is coupled to the rotating shaft 11 by a spline (not shown). For this reason, the cylinder block 12 rotates integrally with the rotating shaft 11. Inside the cylinder block 12, there are provided a plurality of cylindrical cylinders arranged radially around the rotation shaft 11.

The plurality of pistons 13 are accommodated in the plurality of cylinders of the cylinder block 12, respectively. The piston 13 reciprocates in the cylinder as the cylinder block 12 rotates, thereby sucking and discharging hydraulic oil. A spherical body (not shown) is provided at the tip of the piston 13. The plurality of shoes 16 are fitted to the spherical body portion of the piston 13 to form a spherical bearing portion. The plurality of shoes 16 are supported by a ring-shaped retainer ring 14. In FIG. 1, a reference numeral is assigned to each of the plurality of pistons 13 and the plurality of shoes 16.

The eccentric ring 15 is a ring member disposed around the retainer ring 14 and formed concentrically with the rotary shaft 11. The inner surface of the eccentric ring 15 is a smooth curved surface on which the shoe 6 slides. The eccentric ring 15 is slidable left and right along a pair of guide rails 17 provided at the upper and lower ends of the casing 10. As a result, the eccentric ring 15 can be arranged eccentrically with respect to the rotating shaft 11. The sliding movement of the eccentric ring 15 is controlled by the tilt control device 1B. Note that the radially outer sliding surface of the shoe 16 has the same curvature shape as the inner surface of the eccentric ring 7. Further, a movable member engaging portion 15S to which the movable member 20 of the tilt control device 1B is connected is formed at the right end portion of the eccentric ring 15. In the present invention, the eccentric ring 15 functions as a tilt adjustment unit that adjusts the amount of reciprocation of the plurality of pistons 13.

The timing plate 18 is disposed between the rotary shaft 11 and the cylinder block 12. The timing plate 18 has a ring shape, and has a hydraulic oil discharge path and a suction path formed therein. A hole is formed in the timing plate 18 so that the suction and discharge of the hydraulic oil can be switched with the cylinder block 12, and the hydraulic oil is sucked and discharged as the cylinder block 12 rotates. .

Further, a narrow oil passage is provided inside the shoe 6 and communicates with an oil passage that penetrates the inside of the piston 13. As a result, a part of the hydraulic oil in the cylinder of the cylinder block 12 is supplied to the spherical joint portion between the piston 1 and the shoe 16 and the sliding surface between the shoe 16 and the eccentric ring 15 to lubricate each sliding portion. To do.

When the rotating shaft 11 is rotated by the drive source 100, the cylinder block 12, the piston 13, the retainer ring 14, and the shoe 16 rotate integrally with the rotating shaft 11. At this time, the rotational force around the central axis of the rotary shaft 11 transmitted from the cylinder block 12 to the piston 13 is transmitted to the shoe 16. As the shoe 16 slides and rotates along the inner surface of the eccentric ring 15, the piston 13 reciprocates (extends and contracts) within the cylinder. Then, when the piston 13 is displaced along the radial direction, oil is sucked and discharged through the timing plate 10 at a predetermined timing, and the rotational energy of the rotating machine 1A is converted into hydraulic energy. Note that a first oil tank 101 (FIG. 3) is connected to the rotating machine 1A in order to suck and discharge the hydraulic oil.

The tilt control device 1B (FIGS. 1 and 2) has a function of controlling the tilt of the variable capacity rotating machine 1A. The tilt control device 1 B is mechanically directly connected to the eccentric ring 15 via the movable member 20. Then, the tilt control device 1B causes the eccentric ring 15 to be eccentric with respect to the rotating shaft 11 as the movable member 20 expands and contracts (moves in the axial direction) (left-right direction in FIG. 1). As a result, the eccentric ring 15 changes the stroke amount of the piston 13, whereby the pump discharge amount of the rotating machine 1A is controlled. Note that the rotating machine 1A of FIG. 1 is in a zero tilt state (neutral position).

2, the tilt control device 1B includes a housing 1H, a movable member 20, a spool 222, and a first position adjustment mechanism 2 (movement mechanism). The housing 1H functions as a housing that supports each member of the tilt control device 1B. A cylinder portion 1HS is formed in the housing 1H. The cylinder portion 1HS is a cylindrical space portion whose left end side (one end side in the axial direction) is open to the outside. The movable member 20 is accommodated in the cylinder part 1HS.

The movable member 20 has a servo mechanism that follows the stroke of the spool 222 described later. The movable member 20 includes a connection portion 21 and a sleeve portion 22. In this embodiment, the connection part 21 and the sleeve part 22 are comprised integrally (FIG. 2). The connection part 21 is connected to the eccentric ring 15 (FIG. 1) of the rotating machine 1A. The sleeve portion 22 is a cylindrical member that is connected to the connection portion 21. The sleeve portion 22 includes a first piston portion 22P and outer peripheral portions 20P and 20Q (both are first outer peripheral portions). The first piston portion 22P is a part of the outer peripheral portion of the sleeve portion 22, and has a shape protruding outward in the radial direction from the outer peripheral portion 20P and the outer peripheral portion 20Q. The first piston portion 22P is disposed on the sleeve portion 22 so as to be adjacent to the outer peripheral portion 20P and the outer peripheral portion 20Q between the outer peripheral portion 20P and the outer peripheral portion 20Q in the left-right direction (axial direction). It slides along the left and right direction on the peripheral surface. The outer peripheral portions 20P and 20Q are a part of the outer peripheral portion of the first piston portion 22P, and the first hydraulic chamber 211 and the second hydraulic chamber 212 into which hydraulic oil flows between the inner peripheral surface of the cylinder portion 1HS. Forming. The cross-sectional shapes of the first piston part 22P, the outer peripheral part 20P, and the outer peripheral part 20Q are all circular, and the outer diameter of the first piston part 22P is larger than the outer diameters of the outer peripheral part 20P and the outer peripheral part 20Q.

The movable member 20 communicates a later-described supply oil passage 33 with the right oil passage 31 or the left oil passage 32 in accordance with the relative position with respect to the spool 222, and pressurizes the first hydraulic chamber 211 or the second hydraulic chamber 212. It has a function to supply and discharge oil. In other words, the movable member 20 is accommodated in the cylinder portion 1HS so as to be movable along the left-right direction (axial direction) according to the hydraulic pressure of the hydraulic oil flowing into the first hydraulic chamber 211 and the second hydraulic chamber 212. Thus, the drive cylinder 1G for moving the eccentric ring 15 (FIG. 1) is configured together with the housing 1H.

The spool 222 is a shaft-like member that is accommodated in the cylindrical interior 221 of the sleeve portion 22 so as to be movable along the left-right direction. Note that an oil passage extending in the axial direction is formed inside the spool 222 (see the broken line arrow in FIG. 4). The spool 222 includes a second piston portion 222A, an outer peripheral portion 222B, and an outer peripheral portion 222C (both are second outer peripheral portions). The second piston portion 222A is a part of the outer peripheral portion of the spool 222, and has a shape protruding outward in the radial direction from the outer peripheral portion 222B and the outer peripheral portion 222C. The second piston portion 222A is slidable along the left-right direction on the inner peripheral surface of the sleeve portion 22 of the movable member 20, and has a function of sealing a central oil passage 20R described later at a predetermined position in the left-right direction. ing. The outer peripheral portion 222B and the outer peripheral portion 222C are part of the outer peripheral portion of the spool 222, and are disposed adjacent to the second piston portion 222A so as to sandwich the second piston portion 222A in the left-right direction. The outer peripheral portion 222B and the outer peripheral portion 222C are located between the central oil passage 20R and the right side between the inner peripheral surface of the sleeve portion 22 when the second piston portion 222A moves in the left-right direction from the position where the central oil passage 20R is sealed. A communication path that communicates with the oil path 31 or the left oil path 32 is formed. The cross-sectional shapes of the second piston part 222A, the outer peripheral part 222B, and the outer peripheral part 222C are all circular, and the outer diameter of the second piston part 222A is larger than the outer diameters of the outer peripheral part 222B and the outer peripheral part 222C.

Further, a third hydraulic chamber 213 (FIG. 2) is formed between the tip end portion of the spool 222 and the left end portion inside the cylinder of the sleeve portion 22. Further, the spool 222 is a three-position spool valve that can switch the connection destination of the first hydraulic source 102 and the second oil tank 28 described later between the right oil passage 31 and the left oil passage 32.

The housing 1H and the movable member 20 are provided with a control valve for controlling the inflow of hydraulic oil into the first hydraulic chamber 211 or the second hydraulic chamber 212 by the movement of the spool 222 in the left-right direction. As configured, oil passages (20R, 31, 32, 33) for guiding hydraulic oil are formed.

The movable member 20 includes a central oil passage 20R (first oil passage), a right oil passage 31 (second oil passage), and a left oil passage 32 (second oil passage). Further, as described above, there are two hydraulic chambers (first hydraulic chamber 211 and second hydraulic chamber 212) formed of a ring-shaped space between the outer peripheral portion of the sleeve portion 22 and the inner peripheral portion of the cylinder portion 1HS. Is formed. The central oil passage 20R is formed in the first piston portion 22P of the sleeve portion 22 along the radial direction. The central oil passage 20R allows the supply oil passage 33 and the cylindrical interior of the sleeve portion 22 to communicate with each other when the movable member 20 is disposed at a predetermined position in the left-right direction in the cylinder portion 1HS.

The right oil passage 31 is inclined from the outer peripheral portion 20Q toward the inside of the sleeve portion 22, and communicates the second hydraulic chamber 212 with the cylindrical inside of the sleeve portion 22. Similarly, the left oil passage 32 is provided to be inclined from the outer peripheral portion 20 P toward the inside of the sleeve portion 22, and communicates the first hydraulic chamber 211 and the cylindrical inside of the sleeve portion 22. The right oil passage 31 and the left oil passage 32 are inclined so as to approach the central oil passage 20 R as they proceed toward the radially inner side of the sleeve portion 22. For this reason, the communication path formed by the outer peripheral portions 222B and 222C of the spool 222 is set to be short, and the stroke amount of the lateral movement of the spool 222 can be reduced.

The housing 1 H includes a supply oil passage 33 and a discharge oil passage 34. The supply oil passage 33 is provided so as to communicate with the cylinder portion 1HS, and supplies hydraulic oil to the cylinder portion 1HS. The upstream side of the supply oil passage 33 is connected to the first hydraulic source 102 (FIG. 3). The discharge oil passage 34 has a function of discharging hydraulic oil flowing out from the inside of the sleeve portion 22 and the spool 222 to the second oil tank 28 (FIG. 3).

The first position adjustment mechanism 2 is connected to the spool 222 and moves the spool 222 along the left-right direction. Specifically, the first position adjusting mechanism 2 moves the sleeve portion 22 in a state where the second piston portion 222A seals the central oil passage 20R along the left and right directions, thereby supplying the central oil passage from the supply oil passage 33. The hydraulic oil that has flowed into 20R is caused to flow into the second hydraulic chamber 212 or the first hydraulic chamber 211 from the right oil passage 31 or the left oil passage 32 through the communication passage. As a result, the first position adjusting mechanism 2 moves the movable member 20 connected to the eccentric ring 15 (FIG. 1) along the left-right direction.

The first position adjustment mechanism 2 includes both rod cylinders 23 (rod cylinders), a spring 24, a zero point adjustment unit 25 (position adjustment unit), and a hydraulic unit 1S (sub-movement mechanism).

Both rod cylinders 23 are arranged so as to extend along the axial direction inside the housing 1H. In the present embodiment, as shown in FIG. 2, both rod cylinders 23 are arranged on the same axis as the spool 222. The left end portion (one end portion in the axial direction) of both rod cylinders 23 is connected to the spool 222. Both rod cylinders 23 include a third piston portion 23A and outer

peripheral portions

23P and 23Q (both are third outer peripheral portions). Between the housing 1H and the outer peripheral portion 23P and the outer peripheral portion 23Q of both rod cylinders 23, there are a fourth hydraulic chamber 231 (sub hydraulic chamber) and a fifth hydraulic chamber 232 (sub hydraulic chamber) formed of ring-shaped spaces. Is formed. The fourth hydraulic chamber 231 and the fifth hydraulic chamber 232 are partitioned on the left and right by a third piston portion 23 A projecting radially from both rod cylinders 23. The third piston portion 23A slides along the left-right direction with respect to the inner wall portion of the housing 1H so that the volumes of the fourth hydraulic chamber 231 and the fifth hydraulic chamber 232 change.

Both rod cylinders 23 move to the left and right by the supply and discharge of pressure oil from the sub supply oil passage 35 (FIG. 2) or the sub supply oil passage 36 (FIG. 2) of the hydraulic unit 1S. As a result, both rod cylinders 23 cause the spool 222 to stroke left and right.

The spring 24 urges the rod cylinders 23 toward the left (movable member 20 side) with a spring seat 24H provided in the housing 1H as a fulcrum. When no pressure oil is supplied from the auxiliary supply oil passage 35 or the auxiliary supply oil passage 36 to the rod cylinders 23, the urging force of the spring 24 causes the rod cylinders 23 to be in the neutral position (zero tilt position). Retained. In other words, when both rod cylinders 23 are arranged at the neutral position, the biasing force (elastic force) of the spring 24 is set to be zero.

Further, the zero point adjusting portion 25 is disposed so as to be interposed between the right end portion (the other end portion opposite to the one end portion) of both the rod cylinders 23 and the housing 1H. The zero point adjustment unit 25 has a function of adjusting the reference position in the axial direction of both rod cylinders 23 by adjusting the position of the spring seat 24H. In particular, in the tilt control device 1B according to this embodiment capable of adjusting both tilts of the rotating machine 1A, the zero point adjusting unit 25 rotates when the eccentric ring 15 (FIG. 1) is arranged at the neutral position. A zero point adjustment function for adjusting the reference position of both rod cylinders 23 to the zero point position is provided so that the discharge capacity of the machine 1A becomes zero.

The hydraulic unit 1S moves both rod cylinders 23 and the spool 222 integrally in the left-right direction by flowing hydraulic oil into the fourth hydraulic chamber 231 or the fifth hydraulic chamber 232. The hydraulic unit 1S includes a first hydraulic source 102, a first proportional valve 26, a second proportional valve 27, and a third oil tank 29 (FIG. 3). Further, in the housing 1H and the hydraulic unit 1S, there are a sub supply oil passage 35 (FIGS. 2 and 3), a sub supply oil passage 36 (FIGS. 2 and 3), a first unit oil passage 37, and a second unit oil passage 37. A unit oil passage 38 (see FIG. 3 for both) is formed.

The first hydraulic source 102 supplies hydraulic oil to the first hydraulic chamber 211, the second hydraulic chamber 212, and the fourth hydraulic chamber 231 and the fifth hydraulic chamber 232 formed by the rod cylinders 23 formed in the cylinder portion 1HS. To do. The first proportional valve 26 and the second proportional valve 27 switch the supply path and supply amount of the hydraulic oil supplied from the first hydraulic pressure source 102. The first proportional valve 26 and the second proportional valve 27 are electromagnetic valves that can be converted into a secondary pressure by an electrical signal transmitted from a control unit (not shown). The third oil tank 29 collects the hydraulic oil discharged from the fourth hydraulic chamber 231 or the fifth hydraulic chamber 232.

In the present embodiment, the tilt control device 1B functions as a displacement control mechanism (so-called regulator) of the rotating machine 1A (variable displacement radial piston pump). That is, when the tilt control device 1B controls the stroke of the spool 222, the eccentric amount of the eccentric ring 15 connected to the movable member 20 is controlled. As a result, the pump tilt (discharge amount) in the rotating machine 1A can be controlled. Next, the tilt adjustment function of the rotating machine 1A by the tilt control device 1B will be described in detail. 4 and 5 are cross-sectional views showing a state in which the movable member 20 is moved to the left side in the tilt control device 1B of the hydraulic rotating device 1 according to the present embodiment.

In FIG. 2, the movable member 20 and the spool 222 are disposed at the zero tilt position (neutral position). When the movable member 20 is caused to stroke leftward from the state of FIG. 2, a control unit (not shown) switches the first proportional valve 26 so that the supply oil passage 33, the first unit oil passage 37, and the sub supply oil passage. 36 is communicated, and pressure oil is supplied to the fifth hydraulic chamber 232 side of both rod cylinders 23 (see solid arrows in FIG. 4). On the other hand, the second proportional valve 27 connects the auxiliary supply oil passage 35 and the second unit oil passage 38 to discharge the pressure oil on the fourth hydraulic chamber 231 side of both rod cylinders 23 to the third oil tank 29 ( (See dashed arrow in FIG. 4). As a result, both rod cylinders 23 stroke in the left direction. At this time, the amount of pressure oil supplied to the fifth hydraulic chamber 232 by the first proportional valve 26 is adjusted, whereby the stroke amount of both rod cylinders 23 is controlled.

In the initial state of FIG. 2, the relative position between the sleeve portion 22 of the movable member 20 and the spool 222 corresponds to the neutral position, and the port position of the servo valve is the B position in FIG. Accordingly, the pressure oil is not supplied to or discharged from the movable member 20, and the tilt (zero tilt) in the state of FIG. 2 is maintained.

When the rod cylinders 23 stroke in the left direction as described above from the initial state, the spool 222 mechanically coupled directly to the rod cylinders 23 also moves in the left direction. When the spool 222 moves in the left direction, the relative positional relationship between the spool 222 and the sleeve portion 22 changes from the B position to the C position (see FIG. 3). As a result, the supply oil passage 33 and the right oil passage 31 communicate with each other, and the discharge oil passage 34 and the left oil passage 32 communicate with each other. By this switching, the pressure oil supplied from the first hydraulic source 102 is supplied to the second hydraulic chamber 212, and the first hydraulic chamber 211 communicates with the second oil tank 28, and the pressure oil is supplied from the first hydraulic chamber 211. Is discharged (see arrow in FIG. 4). As a result, the movable member 20 strokes leftward together with the eccentric ring 15 (FIG. 2) (arrow D51 in FIG. 5), and changes the tilt of the rotating machine 1A in a larger direction.

In this embodiment, by setting the cross-sectional area of the fifth hydraulic chamber 232 to be larger than the cross-sectional area of the second hydraulic chamber 212, a larger thrust can be obtained with respect to the movable member 20. For this reason, it becomes possible to change the extrusion capacity of the rotating machine 1A with a smaller driving force by adjusting the cross-sectional area ratio.

When the movable member 20 strokes to the left and eventually the sleeve portion 22 moves until the relative positional relationship between the spool 222 and the sleeve portion 22 becomes the same as the initial state described above (position B in FIG. 2), Since the supply and discharge of the pressure oil to the first hydraulic chamber 211 and the second hydraulic chamber 212 are interrupted, the stroke of the movable member 20 stops. As a result, the extrusion capacity (tilt) of the rotating machine 1A is fixed.

Thus, in this embodiment, the stroke amount of both rod cylinders 23 can be controlled so that the movable member 20 is disposed at an arbitrary position. The stroke amount of the movable member 20 can be controlled via the first proportional valve 26 and the second proportional valve 27 connected to the rod cylinders 23, and the pushing capacity of the rotating machine 1A as a hydraulic pump can be controlled. It is possible to control.

On the other hand, FIGS. 6 and 7 are cross-sectional views showing how the movable member 20 is moved to the right side in the tilt control device 1B of the hydraulic rotating device 1 according to the present embodiment. When the movable member 20 is moved in the right direction, an operation opposite to the procedure in the left direction is performed. First, when the first proportional valve 26 is controlled by a control unit (not shown) and the auxiliary supply oil passage 36 (FIG. 3) and the second unit oil passage 38 (FIG. 3) communicate with each other, the fifth hydraulic chamber 232 is provided. Is discharged to the third oil tank 29. Further, the second proportional valve 27 is controlled, and the auxiliary supply oil passage 35 and the supply oil passage 33 are communicated (FIGS. 2 and 3). As a result, pressure oil is supplied from the first hydraulic source 102 to the fourth hydraulic chamber 231. As a result, both rod cylinders 23 stroke in the right direction, and the spool 222 also moves in the right direction by the same stroke amount. The relative positional relationship between the sleeve portion 22 and the spool 222 is the A position in FIG. 3, the supply oil passage 33 and the left oil passage 32 communicate with each other, and the discharge oil passage 34 and the right oil passage 31 are connected. Communicate. Then, the pressure oil is supplied to the first hydraulic chamber 211, and the pressure oil in the second hydraulic chamber 212 is discharged to the second oil tank 28 through the discharge oil passage 34 (see the arrow in FIG. 6). The member 20 strokes in the right direction (arrow D71 in FIG. 7). As a result, the eccentric ring 15 of the rotating machine 1A is moved rightward along the guide rail 17, and the tilt of the pump of the rotating machine 1A is set small. Further, when the moving amount of the eccentric ring 15 is greatly changed in the right direction, the tilt of the rotating machine 1A is changed to the reverse tilt side. As a result, the rotating machine 1A can function as a piston motor. Thus, in this embodiment, both tilt control of the rotating machine 1A becomes possible by the tilt control device 1B. Therefore, the tilt control device 1B can function not only as a tilt control of the hydraulic pump or hydraulic motor but also as a tilt control device of the hydraulic pump motor.

As described above, in the present embodiment, the housing 1H and the movable member 20 constitute a drive cylinder that moves the eccentric ring 15 of the rotating machine 1A. Further, the movable member 20 and the spool 222 constitute a control valve (servo valve) that moves the movable member 20. For this reason, it is possible to transmit the movement of the spool 222 to the eccentric ring 15 with higher accuracy than in the case where the member having the piston function of the drive cylinder and the member having the sleeve function of the control valve are configured as separate members. It becomes. As a result, highly accurate tilt control can be realized, and the pump tilt characteristics of the rotating machine 1A can be stably obtained. Further, since the sleeve portion 22 of the movable member 20 has both the piston function of the drive cylinder and the sleeve function of the control valve, the radial size of the tilt control device 1B can be reduced and tilt control can be performed. The number of parts of the device 1B can be reduced. Further, as shown in FIG. 2, an oil passage connecting the radially outer side and the inner side of the sleeve portion 22 is formed, so that the first hydraulic chamber 211 and the second hydraulic chamber 212 are moved according to the movement of the spool 222. It becomes possible to let hydraulic oil flow in.

In this embodiment, since the connecting portion 21 and the sleeve portion 22 of the movable member 20 are integrally formed, the movement of the spool 222 can be transmitted to the eccentric ring 15 with higher accuracy.

Furthermore, in this embodiment, even when the bi-tilt control is performed in the rotating machine 1A of the hydraulic rotating device 1, the movable member 20 can smoothly follow the left and right movement of the spool 222. At this time, in the first position adjusting mechanism 2 (FIG. 2) of the tilt control device 1B, the eccentric ring 15 of the rotating machine 1A is at a predetermined neutral position and on the left side (one axial end side) of the neutral position. Between the first position where the rotating machine 1A functions as a hydraulic pump and the second position which is on the right side (the other end side in the axial direction) from the neutral position and which functions the rotating machine 1A as a hydraulic motor. The movable member 20 is moved leftward (first direction) and rightward (second direction opposite to the first direction) along the left-right direction (axial direction) so that the position can be changed. For this reason, both tilt control and zero tilt control of the rotating machine 1A can be realized with high accuracy. In particular, compared to a known control mechanism in which pressure oil flows into both end ports of the servo valve and zero tilt control is performed according to the pressure balance, highly accurate zero tilt control can be realized.

Further, in the present embodiment, the tilt control device 1B includes the zero point adjustment unit 25 (position adjustment unit). Therefore, even if there is a deviation in the position control of the movable member 20 due to a manufacturing shape error or the like, the position of the movable member 20 can be adjusted by the zero point adjustment unit 25. For this reason, it can suppress that a shift | offset | difference arises in the target inclination of 1 A of rotary machines with the component tolerance of each member of the inclination control apparatus 1B. In other words, when a manufacturing error has occurred in each member of the tilt control device 1B, or when an error has occurred in the spring performance of the spring 24 (FIG. 2), both rod cylinders 23, A positional shift may occur in the first proportional valve 26, the second proportional valve 27, and the movable member 20. In the present embodiment, the zero point position that is the reference point of the movable member 20 can be finely adjusted by using the zero point adjustment unit 25 so that it becomes a preset target position. For this reason, the zero point position of the tilt adjustment unit can be adjusted stably. As a result, it is possible to reduce positional deviation due to individual differences between the rotating machine 1A and the tilt control device 1B, and to perform tilt control with high accuracy.

Furthermore, in the present embodiment, the first proportional valve 26 and the second proportional valve 27 switch the supply path and supply amount of hydraulic oil supplied from the first hydraulic source 102. In particular, the second proportional valve 27 and the first proportional valve 26 are independently connected to the fourth hydraulic chamber 231 and the fifth hydraulic chamber 232 of both rod cylinders 23, respectively. For this reason, the left and right movements of both rod cylinders 23 are possible. As a result, the rotating machine 1A can be used for both tilting of the hydraulic pump or the hydraulic motor.

Further, in the present embodiment, the hydraulic unit 1S can move the movable member 20 connected to the eccentric ring 15 by moving the spool 222 and the rod cylinders 23 integrally. As a result, the tilt of the rotating machine 1A can be accurately controlled by the axial movement of the shaft-like members arranged on the same axis.

Further, in the present embodiment, the relationship between the cross-sectional area of the fifth hydraulic chamber 232> the cross-sectional area of the second hydraulic chamber 212 and the cross-sectional area of the fourth hydraulic chamber 231> the cross-sectional area of the first hydraulic chamber 211 is satisfied in advance. It is desirable that the shape of each member is set. In this case, it becomes possible to reduce the driving force for driving the movable member 20, and it is also possible to use a low pressure source. FIG. 8 is a hydraulic circuit diagram of a hydraulic rotation device according to a modified embodiment of the present invention, and the tilt control of the rotating machine 1A is performed by the tilt control device 1C instead of the tilt control device 1B of the above embodiment. Is done. In the tilt control device 1C, a second hydraulic pressure source 103 is arranged separately from the first hydraulic pressure source 102 that supplies pressure oil to the cylinder portion 1HS (FIG. 2). The second hydraulic source 103 is a lower pressure hydraulic source than the first hydraulic source 102. In the tilt control device 1 C, the second hydraulic source 103 supplies pressure oil to the fourth hydraulic chamber 231 or the fifth hydraulic chamber 232 of both rod cylinders 23 via the first proportional valve 26 or the second proportional valve 27. Supply. As a result, compared to the tilt control device 1B, low-pressure specification equipment can be used, and the tilt control device 1C can be reduced in size and cost.

The

tilt control devices

1B and 1C and the hydraulic rotating device 1 including the

tilt control devices

1B and 1C according to the embodiments of the present invention have been described above. According to the hydraulic rotating device 1 described above, it is possible to accurately transmit the movement of the spool 222 of the

tilt control devices

1B and 1C to the movable member 20 and to realize highly accurate tilt control of the rotating machine 1A. Become. The present invention is not limited to these forms. As the tilt control device and the hydraulic rotation device according to the present invention, the following modified embodiments are further possible.

(1) In the above embodiment, the

tilt control devices

1B and 1C have been described as having the first position adjustment mechanism 2 as the movement mechanism of the present invention, but the present invention is not limited to this. . FIG. 9 is a cross-sectional view of a tilt control device 1D (tilt control device) of a hydraulic rotating device according to a modified embodiment of the present invention. In the present modified embodiment, instead of the first position adjustment mechanism 2 of the tilt control device 1B according to the previous embodiment, the tilt control device 1D includes a second position adjustment mechanism 6 (movement mechanism). The second position adjusting mechanism 6 is connected to the spool 222 and causes the hydraulic oil to flow into the first hydraulic chamber 211 or the second hydraulic chamber 212 by moving the spool 222 along the left-right direction (axial direction). As a result, the second position adjusting mechanism 6 moves the movable member 20 connected to the eccentric ring 15 along the axial direction.

The second position adjusting mechanism 6 includes an electric motor 60 and a ball screw 61. The ball screw 61 is disposed so as to extend in the left-right direction, and the left end portion thereof is connected to the spool 222. The ball screw 61 includes a screw shaft that is rotated around an axis extending in the left-right direction. Further, the electric motor 60 rotates the screw shaft of the ball screw 61 around the axis, thereby moving the screw shaft and the spool 222 integrally along the left-right direction. That is, in this modified embodiment, by using the electric motor 60 and the ball screw 61, the rotational force of the electric motor 60 is converted into a propulsive force through the ball screw 61, and the spool 222 mechanically directly connected to the ball screw 61 is provided. It can be moved in the left-right direction. By moving the spool 222, the movable member 20 moves following the spool 222, and the tilt of the rotating machine 1A (FIG. 1) can be controlled. According to such a configuration, the tilt of the rotating machine 1A can be controlled with high accuracy by the axial movement of the shaft-like members arranged on the same axis. In the present modified embodiment, the second position adjustment mechanism 6 does not include a proportional valve as compared to the previous embodiment. For this reason, it becomes possible to reduce the influence on the pump tilt characteristic due to the operation variation of the proportional valve. Further, in this modified embodiment, the stroke control of the movable member 20 is all controlled by the position control of the electric motor. For this reason, it becomes possible to perform the stroke control of the movable member 20 and the tilt control of the rotating machine 1A with high accuracy without providing the zero adjustment function.

(2) In the above embodiment, the rotating machine 1A of the hydraulic rotating device 1 has been described as being a radial piston type hydraulic rotating machine, but the present invention is not limited to this. The tilt switching device according to the present invention can be applied not only to a radial type pump but also to a radial type motor. Further, by using the stroke of the movable member 20, a known axial type pump and motor tilt switching can be used. It can also be applied to control.

(3) Moreover, in said embodiment, although the connection part 21 demonstrated in the aspect which consists of a cylindrical part with which the front-end | tip part of the sleeve part 22 was equipped, this invention is not limited to this. The connection portion 21 may be formed of another shape that can move the eccentric ring 15 (tilt adjustment portion) of the rotating machine 1A.

Claims

A tilt control device for controlling the tilt of a variable capacity hydraulic rotating machine including a tilt adjusting unit,
A housing including a cylinder portion having one end side in the axial direction opened to the outside;
The hydraulic oil flows between a connecting portion connected to the tilt adjusting portion of the hydraulic rotating machine, a cylindrical sleeve portion connected to the connecting portion, and an inner peripheral surface of the cylinder portion. A first outer peripheral portion forming a hydraulic chamber, and being housed in the cylinder portion so as to be movable along the axial direction according to the hydraulic pressure of the hydraulic oil flowing into the hydraulic chamber, A movable member that, together with the housing, constitutes a drive cylinder that moves the tilt adjustment portion;
A spool accommodated inside the sleeve portion so as to be movable along the axial direction;
A moving mechanism for moving the spool along the axial direction;
Have
In the housing and the movable member, the hydraulic oil is configured such that the movable member and the spool constitute a control valve that controls the inflow of the hydraulic oil into the hydraulic chamber by the movement of the spool in the axial direction. The tilt control device is formed with an oil passage that guides.
The housing includes a supply oil passage that is provided to communicate with the cylinder portion and supplies the hydraulic oil to the cylinder portion;
The movable member is
A first piston portion disposed in the sleeve portion so as to be adjacent to the first outer peripheral portion in the axial direction, and sliding along the axial direction on an inner peripheral surface of the cylinder portion;
A first oil that is formed in the first piston portion and communicates between the supply oil passage and the cylindrical interior of the sleeve portion when the movable member is disposed at a predetermined position in the axial direction in the cylinder portion. Road,
A second oil passage that is provided from the first outer peripheral portion toward the inside of the sleeve portion and communicates the hydraulic chamber and the cylindrical inside of the sleeve portion;
With
The spool is
A second piston portion that is slidable along the axial direction on the inner peripheral surface of the sleeve portion of the movable member, and seals the first oil passage at a predetermined position in the axial direction;
An inner circumferential surface of the sleeve portion when the second piston portion is disposed adjacent to the second piston portion in the axial direction and moved in the axial direction from a position where the second piston portion seals the first oil passage; A second outer peripheral portion that forms a communication passage that communicates the first oil passage and the second oil passage between,
With
The moving mechanism flows into the first oil passage from the supply oil passage by moving the spool in a state where the second piston portion seals the first oil passage along the axial direction. 2. The tilt according to claim 1, wherein hydraulic oil is allowed to flow into the hydraulic chamber from the communication path and the second oil passage, and the movable member connected to the tilt adjustment unit is moved along the axial direction. Control device.
The tilt control device according to claim 1 or 2, wherein the connecting portion and the sleeve portion of the movable member are integrally configured.
The moving mechanism is
A third outer peripheral portion that is disposed so as to extend along the axial direction on the same axis as the spool, has one end in the axial direction connected to the spool, and further forms a sub hydraulic chamber with the housing A rod cylinder with
A sub-movement mechanism that moves the rod cylinder and the spool integrally along the axial direction by flowing hydraulic oil into the sub-hydraulic chamber;
The tilt control device according to claim 2, comprising:
The position adjustment part which is arrange | positioned between the other end part on the opposite side to the said one end part of the said rod cylinder, and the said housing, and adjusts the reference | standard position in the said axial direction of the said rod cylinder is further provided. Tilt control device.
The moving mechanism is
A ball screw including a screw shaft that is disposed so as to extend along the axial direction on the same axis as the spool, and that is connected to the spool at one end in the axial direction and rotated about an axis extending in the axial direction; ,
An electric motor that integrally moves the screw shaft and the spool along the axial direction by rotating the screw shaft around the axis;
The tilt control device according to claim 2, comprising:
In the moving mechanism, the tilt adjusting unit of the hydraulic rotating machine has a predetermined neutral position and one end side in the axial direction from the neutral position, and causes the hydraulic rotating machine to function as a hydraulic pump. The movable member is movable so that the position of the movable member can be changed between the position of 1 and the second position on the other end side in the axial direction from the neutral position and causing the hydraulic rotating machine to function as a hydraulic motor. 2. The tilt control device according to claim 1, wherein the tilt control device is moved in a first direction and a second direction opposite to the first direction along the axial direction.
In the moving mechanism, the tilt adjusting unit of the hydraulic rotating machine has a predetermined neutral position and one end side in the axial direction from the neutral position, and causes the hydraulic rotating machine to function as a hydraulic pump. The movable member is movable so that the position of the movable member can be changed between the position of 1 and the second position on the other end side in the axial direction from the neutral position and causing the hydraulic rotating machine to function as a hydraulic motor. Moving along the axial direction in a first direction and a second direction opposite to the first direction;
The position adjustment unit has a zero point adjustment function for adjusting the reference position of the rod cylinder so that the discharge capacity of the hydraulic rotating machine becomes zero when the tilt adjustment unit is disposed at the neutral position. The tilt control device according to claim 5.
A tilt control device according to claim 1;
A rotating body having a plurality of cylinders, a plurality of pistons that are respectively housed in the plurality of cylinders and reciprocated to suck and discharge hydraulic oil, and the tilt that adjusts a reciprocating amount of the plurality of pistons An adjustment unit, and the hydraulic rotating machine comprising:
A hydraulic rotating device.