JP2003074460A - Variable displacement type hydraulic rotating machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability and a service life of a feedback link and heighten reliability by inhibiting the feedback link from vibrating at high frequency. SOLUTION: A casing body 32 is provided with an actuator fitting part 32B in a position axially away from the front bottom 32A, and a tilting actuator 45 or the like is disposed in the actuator fitting part 32B. The feedback link 57 for transmitting the motion of a step piston 47 to a control sleeve 55 is disposed between the step piston 47 of the tilting actuator 45 and the control sleeve 55 of a regulator 53. The feedback link 57 is constituted of a rigid turning lever 58 turned on a pivot pin 59, and a clamping spring 61, one end of which is fixed to the turning lever, and the other end of which is connected to the step piston 47 through a pin 49.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement hydraulic rotating machine suitably used as a hydraulic pump or hydraulic motor mounted on a construction machine such as a hydraulic excavator.

[0002]

2. Description of the Related Art Generally, a construction machine such as a hydraulic excavator is equipped with a variable displacement hydraulic rotating machine such as a hydraulic pump which constitutes a hydraulic source together with a tank, or a hydraulic motor which constitutes a hydraulic actuator for traveling and turning. It is provided.

Then, for example, Japanese Patent Laid-Open No. 11-351134.
In the publication, a variable displacement swash plate type hydraulic pump in which a displacement variable portion is constituted by a swash plate is described as a variable displacement hydraulic rotating machine according to the prior art.

A variable displacement type swash plate type hydraulic pump according to this type of prior art will be described with reference to the displacement controlling hydraulic circuit shown in FIG.

In the drawing, reference numeral 1 is a variable displacement type swash plate type hydraulic pump. The hydraulic pump 1 has a rotating shaft in a casing,
A cylinder block, a plurality of pistons, a plurality of shoes, a valve plate (all not shown), etc. are provided, and a swash plate 2 serving as a capacity varying portion is tiltably provided between the casing and each shoe. ing.

In the hydraulic pump 1, the rotary shaft is rotatably driven by a prime mover (not shown) of a hydraulic excavator or the like, so that the pistons reciprocate in respective cylinders of a cylinder block that rotates integrally with the prime mover. The working oil sucked into each cylinder from the tank 3 according to the reciprocating movement of these pistons is discharged to the discharge pipe 4 side as high pressure oil.

Reference numeral 5 denotes a tilting actuator for tiltingly driving the swash plate 2. The tilting actuator 5 is located outside the cylinder block in the radial direction and serves as a tilting control cylinder formed in the casing. Cylinder holes 6A, 6
B, and a stepped piston 7 as a servo piston slidably fitted in the cylinder holes 6A, 6B.

Further, the stepped piston 7 of the tilt actuator 5 defines a hydraulic chamber 8A in a large diameter cylinder hole 6A and a hydraulic chamber 8B in a small diameter cylinder hole 6B. There is. When the tilt control pressure is supplied to the hydraulic chamber 8B, the tilt actuator 5 causes the stepped piston 7 to slide and move toward the hydraulic chamber 8A side by this pressure, whereby the swash plate 2 is moved. Is driven in the direction of arrow A so that the tilt angle becomes smaller.

On the other hand, when the regulator 11 to be described later is switched from the neutral position (a) to the switching position (b) and the tilt control pressure is supplied into the hydraulic chamber 8A, the tilt actuator 5 is moved.
Causes the stepped piston 7 to slide and displace toward the hydraulic chamber 8B side due to the difference in pressure receiving area between the hydraulic chambers 8A and 8B, which increases the tilt angle of the swash plate 2 in the direction of arrow B. It is driven like this.

Reference numeral 9 denotes a pilot pump in which a low-pressure hydraulic pressure source for generating a tilt control pressure is formed together with the tank 3. The pilot pump 9 sucks hydraulic oil from the inside of the tank 3 and
Pressure oil for tilt control is discharged into the tilt control pressure conduit 10. In this case, the pressure of the pressure oil discharged from the pilot pump 9 is kept sufficiently lower than the discharge pressure of the hydraulic pump 1 by a low pressure leaf valve (not shown) or the like.

Reference numeral 11 denotes a regulator for supplying and discharging the tilt control pressure to and from the tilt actuator 5.
Is a servo valve provided in the casing of the hydraulic pump 1, and constitutes a displacement control valve for the hydraulic pump 1.
The regulator 11 has a valve case (not shown), and a spool 13 is slidably displaced in the valve case via a control sleeve 12.

The regulator 11 has a spool 13
A valve spring 14 is provided at one end of the spool 13 and a hydraulic pilot portion 15 is provided at the other end of the spool 13. Then, in the regulator 11, when the pilot pressure supplied to the hydraulic pilot portion 15 becomes lower than the biasing force of the valve spring 14, the valve spring 14 switches the neutral position (a) shown in FIG. 11 to the switching position (b). .

When the regulator 11 is switched to the switching position (b), the pilot pump 9 is connected to the hydraulic chamber 8A of the tilt actuator 5 via the tilt control pressure lines 10 and 16, and the pilot pump 9 is connected. The tilt control pressure from is supplied into the hydraulic chamber 8A.

When the pilot pressure supplied to the hydraulic pilot portion 15 becomes larger than the biasing force of the valve spring 14, the regulator 11 resists the valve spring 14 and shifts from the neutral position (a) shown in FIG. Switched to (C).
Then, when the regulator 11 is switched to the switching position (C), the tilt control pressure conduit 16 is connected to the tank 3, so that the hydraulic chamber 8A of the tilt actuator 5 is pressurized toward the tank 3 side. Is discharged, and the pressure in the hydraulic chamber 8A drops to a pressure close to the tank pressure.

Reference numeral 17 denotes a feedback link which follows the tilting movement of the swash plate 2 and feedback-controls the control sleeve 12 of the regulator 11.
7 is formed as a link member made of a rigid material, and one end side thereof is rotatably connected to the control sleeve 12 of the regulator 11 using a pin or the like.

The other end of the feedback link 17 is rotatably connected to the stepped piston 7 of the tilt actuator 5 by using a pin or the like.
An intermediate portion in the longitudinal direction of is is rotatably attached to a casing of the hydraulic pump 1 or the like by using a support pin 18.

When the stepped piston 7 of the tilt actuator 5 is displaced in the arrow A direction, the feedback link 17 rotates about the support pin 18 to move the control sleeve 12 in the arrow C direction. Shift to. When the stepped piston 7 is displaced in the direction of arrow B,
The control sleeve 12 is displaced by the feedback link 17 in the arrow D direction.

Reference numeral 19 denotes another tilt control pressure conduit branched from an intermediate portion of the tilt control pressure conduit 10, and the tilt control pressure conduit 19 is provided.
Is for continuously supplying the tilt control pressure from the pilot pump 9 to the hydraulic chamber 8B of the tilt actuator 5.

Reference numeral 20 designates a pilot conduit branched from an intermediate portion of the tilt control pressure conduit 10, and the pilot conduit 20 is
The hydraulic pilot section 15 of the regulator 11 is connected to the pilot pump 9.

Reference numeral 21 is a pressure control valve provided in the middle of the pilot conduit 20. The pressure control valve 21 is an electromagnetic proportional control valve and has an electromagnetic proportional solenoid section 22.
The pressure control valve 21 variably controls the pilot pressure supplied to the hydraulic pilot section 15 of the regulator 11 in accordance with a command signal output to the electromagnetic proportional solenoid section 22 in accordance with, for example, a pressure change in the discharge pipe 4. To do.

The displacement control hydraulic circuit of the swash plate type hydraulic pump 1 according to the prior art has the above-mentioned configuration. Next, the displacement control operation will be described.

First, while the command signal output to the electromagnetic proportional solenoid section 22 of the pressure control valve 21 is kept substantially constant, the spool 13 of the regulator 11 is held at the neutral position (a) as shown in FIG. And tilt actuator 5
As a result, the swash plate 2 of the hydraulic pump 1 is maintained at a substantially constant tilt angle as shown.

When a command signal for reducing the tilt angle of the swash plate 2 is output to the electromagnetic proportional solenoid section 22 in this state, the pilot pressure is raised by the pressure control valve 21, so that the regulator 11 Spool 13 is a valve spring 14
Against this, the neutral position (a) is switched to the switching position (c), and the tilt control pressure conduit 16 is connected to the tank 3.

As a result, in the tilt actuator 5, the pressure oil in the hydraulic chamber 8A is discharged to the tank 3 side, and the tilt control pressure is supplied from the tilt control pressure line 19 into the hydraulic chamber 8B. The stepped piston 7 is slidably displaced in the direction of arrow A by the pressure difference between the hydraulic chambers 8A and 8B, and the swash plate 2 of the hydraulic pump 1 is driven to the small tilt side.

Further, the control sleeve 1 of the regulator 11
2, the feedback link 1 is the movement of the stepped piston 7.
The regulator 11 is feedback-controlled so that it is displaced in the arrow C direction by being transmitted via 7, and the control sleeve 12 is slidably displaced in the same direction as the spool 13.

When the tilt angle of the swash plate 2 reaches an angle corresponding to the small tilt command by the command signal, the displacement of the control sleeve 12 causes the regulator 11 to return to the neutral position (a). Therefore, the discharge amount of the pressure oil by the hydraulic pump 1 becomes a small discharge amount corresponding to the command signal, and the capacity control is performed.

On the other hand, when a command signal for increasing the tilt angle of the swash plate 2 is output to the electromagnetic proportional solenoid section 22, the pilot pressure is reduced by the pressure control valve 21, so that the spool 13 of the regulator 11 is The neutral position (a) is switched to the switching position (b) by the valve spring 14, and the pilot pump 9 is connected to the hydraulic chamber 8A of the tilt actuator 5 via the tilt control pressure lines 10 and 16.

As a result, the tilt actuator 5 is supplied with tilt control pressure from the pilot pump 9 into the hydraulic chambers 8A and 8B, and the stepped piston 7 is indicated by the pressure receiving area difference between the hydraulic chambers 8A and 8B. As a result of sliding displacement in the B direction, the swash plate 2 of the hydraulic pump 1 is driven toward the large tilt side.

Further, the control sleeve 1 of the regulator 11
2, the feedback link 1 is the movement of the stepped piston 7.
The regulator 11 is feedback-controlled so that it is displaced in the direction of the arrow D by being transmitted via 7, and the control sleeve 12 is slidably displaced in the same direction as the spool 13.

When the tilt angle of the swash plate 2 becomes an angle corresponding to the large tilt command by the command signal, the displacement of the control sleeve 12 causes the regulator 11 to return to the neutral position (a). Therefore, the discharge amount of the pressure oil by the hydraulic pump 1 becomes a large discharge amount corresponding to the command signal, and the capacity control is performed.

[0031]

By the way, in the above-mentioned conventional technique, the stepped piston 7 of the tilt actuator 5 and the control sleeve 12 are connected by using the feedback link 17, whereby the tilt actuator 5 is driven. The movement is transmitted to the control sleeve 12 of the regulator 11 to perform feedback control.

However, since the feedback link 17 is made of a rigid material, when the stepped piston 7 of the tilt actuator 5 is exposed to high frequency vibration due to hydraulic pulsation, for example, this is propagated to the feedback link 17. There is a problem that it causes damage and damage.

That is, when pressure pulsation occurs when the discharge pressure of the hydraulic pump 1 is high, the swash plate 2 may repeat high frequency vibration with a high vibration frequency due to the influence of the pulsation. Then, such high frequency vibration is transmitted from the swash plate 2 to the stepped piston 7 and also propagates to the feedback link 17 made of a rigid material as a minute vibration, and the feedback link 17 is damaged due to the influence of the high frequency vibration. Problems such as damage will occur.

When the feedback link 17 is broken or damaged, the feedback control for the control sleeve 12 of the regulator 11 is invalidated.
There is a problem that the capacity control of the hydraulic pump 1 becomes difficult, and the reliability of the variable displacement hydraulic rotary machine deteriorates.

The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to suppress high-frequency vibration of the feedback link, improve the durability and life of the feedback link, and improve reliability. It is an object of the present invention to provide a variable displacement hydraulic rotating machine that can be increased.

[0036]

In order to solve the above-mentioned problems, the invention of claim 1 provides a casing of a hydraulic rotary machine having a variable capacity portion, and a casing provided in the casing for supplying / discharging from the outside. A tilt actuator that tilt-drives the variable capacity unit in accordance with the tilt control pressure, and a spool provided in the casing for variably controlling the tilt control pressure supplied to and discharged from the tilt actuator. The present invention is applied to a variable displacement type hydraulic rotating machine including a regulator including a servo valve having: and a feedback mechanism for performing feedback control of a control sleeve of the regulator by following a tilting operation of the displacement varying unit.

The feedback mechanism is provided between the control sleeve of the regulator and the tilt actuator to transmit the movement of the tilt actuator to the control sleeve. The feedback link is characterized in that at least a part of the feedback link is formed by using a spring material for damping high frequency vibration.

With this configuration, when the variable capacity section repeats high frequency vibration due to the influence of hydraulic pulsation, etc., even if this high frequency vibration is transmitted from the variable capacity section to the tilt actuator, the feedback link The high-frequency vibration can be damped by a part of the spring material, and the damage and damage to the feedback link due to the repeated small vibrations can be suppressed.

The invention according to claim 2 is characterized in that a cylindrical casing, a rotary shaft rotatably provided in the casing, and a rotary shaft provided in the casing so as to rotate together with the rotary shaft. A cylinder block in which a plurality of cylinders that are spaced apart in the circumferential direction and extend in the axial direction are bored, a plurality of pistons that are reciprocally inserted into each cylinder of the cylinder block, and tiltable in the casing. The swash plate provided on the end of each piston has a sliding surface on which the shoe slides, and the swash plate is tilted according to the tilt control pressure provided on the casing from the outside. A tilt actuator that is rotationally driven, and a regulator that includes a servo valve that is provided in the casing and that has a spool in a control sleeve for variably controlling tilt control pressure that is supplied to and discharged from the tilt actuator. Wherein following the tilting operation of the swash plate is applied to a variable displacement type hydraulic rotary machine that includes a feedback mechanism for feedback control of the control sleeve of the regulator.

The feedback mechanism is provided between the control sleeve of the regulator and the tilt actuator to transmit the movement of the tilt actuator to the control sleeve. The feedback link is characterized in that at least a part of the feedback link is formed by using a spring material for damping high frequency vibration.

With this configuration, when the swash plate repeats high frequency vibration due to the influence of hydraulic pulsation, etc.
Even if this high-frequency vibration is transmitted from the swash plate to the tilt actuator, the high-frequency vibration can be damped by the spring material forming a part of the feedback link, and damage and damage to the feedback link due to repeated microvibration can be suppressed.

According to the third aspect of the present invention, the feedback link is rotatably attached to the casing and has a rigid link member made of a rigid material, one end side of which is connected to the control sleeve of the regulator, and one end side of the rigid link member. The elastic link member is fixed to the other end side and the other end side is formed of a spring material connected to the tilt actuator, and configured to be an elastic link member that transmits the movement of the tilt actuator to the rigid link member.

Thus, the elastic link member can attenuate high frequency vibration from the tilt actuator and transmit it to the rigid link member, and can prevent the rigid link member from repeating minute vibrations.

According to the invention of claim 4, the elastic link member is formed by bending an elongated spring material into a substantially U shape, and the bent portion side is wound around the other end side of the rigid link member. It is fixed, and the tip end side extending in a bifurcated shape is connected to the pin provided on the tilt actuator so as to be sandwiched from both sides in the radial direction.

As a result, the elastic link member formed by bending the elongated spring material into a substantially U-shape moves the tilting actuator with the pin of the tilting actuator sandwiching the pin of the tilting actuator from the radial direction. Can be transmitted to the rigid link member and exposure of the rigid link member to high frequency vibration can be suppressed. Further, by using such an elastic link member, the mounting direction of the feedback link with respect to the tilt actuator can be changed in three axial directions, and the degree of freedom in mounting the regulator or the like can be increased.

Further, according to the invention of claim 5, the tilting actuator is provided with a tilting control cylinder provided in a casing, and slidably fitted in the tilting control cylinder to supply the tilting control pressure. And a servo piston that is displaced axially in the tilt control cylinder by being discharged,
Between the casing and the servo piston, a jig for holding the servo piston in a rotation stop state in the tilt control cylinder when the variable capacity part is assembled in the casing is detachably provided.

Thus, for example, during assembly work of the variable displacement hydraulic rotary machine, the servo piston of the tilt actuator can be held in a rotation stop state by using a jig in the tilt control cylinder, and the capacity can be varied in this state. By incorporating the portion (swash plate) in the casing, the variable volume portion can be smoothly connected to the servo piston in a short time.

[0048]

BEST MODE FOR CARRYING OUT THE INVENTION A variable displacement hydraulic rotating machine according to an embodiment of the present invention will be described in detail below with reference to the accompanying drawings, taking as an example a case where the hydraulic pump is applied to a swash plate type hydraulic pump. In addition, in the embodiment, the same components as those of the above-described conventional technique are designated by the same reference numerals, and the description thereof will be omitted.

Here, FIGS. 1 to 8 show a first embodiment of the present invention. In the figure, 31 is a casing of a swash plate type hydraulic pump, and the casing 31 has a stepped cylindrical casing body 32 with one end side being a front bottom portion 32A.
And a rear casing 33 provided on the casing body 32 so as to close the other end side of the casing body 32.

Further, the casing body 3 of the casing 31
2, an actuator mounting portion 32B is provided at a position axially separated from the front bottom portion 32A, as shown in FIG.
2 protrudes outward in the radial direction. Then, as shown in FIG. 3, a tilt actuator 45, which will be described later, and the like are provided in the actuator mounting portion 32B.

Further, the actuator mounting portion 32B of the casing body 32 has a substantially quadrangular opening 32 between it and a regulator 53, which will be described later, as shown in FIGS.
C is formed, and a rotation lever 58 of a feedback link 57, which will be described later, is rotatably mounted in the opening 32C via a pivot pin 59.

On the other hand, the rear casing 3 of the casing 31
3, supply / discharge passages 43, 44 described later are formed, and these supply / discharge passages 43, 44 supply / discharge hydraulic oil (pressure oil) into / from a cylinder 36 via a valve plate 42 described below. It is a thing.

A rotary shaft 34 is rotatably provided in the casing 31. One end (tip) side of the rotary shaft 34 is rotatably mounted in the front bottom portion 32A of the casing body 32 via a bearing or the like. The other end (base end) side is rotatably attached to the rear casing 33 via a bearing or the like.

The prime mover of a hydraulic excavator, for example, is connected to the projecting end of the rotary shaft 34, which projects axially from the front bottom portion 32A of the casing body 32, via a power transmission mechanism (not shown) or the like. The rotating shaft 34 is rotated at a high speed by driving.

Reference numeral 35 denotes a cylinder block located inside the casing 31 and provided on the outer peripheral side of the rotary shaft 34. In the cylinder block 35, a plurality (usually an odd number) extending in the axial direction at intervals in the circumferential direction are provided. Cylinders 36, 36, ... Are drilled. The cylinder block 35 is spline-coupled to the rotary shaft 34 and rotates integrally with the rotary shaft 34.

Numerals 37, 37, ... Are pistons slidably fitted in the respective cylinders 36 of the cylinder block 35,
The pistons 37 reciprocate in the respective cylinders 36 by the rotation of the cylinder block 35, suck the working oil into the respective cylinders 36 from the valve plate 42 side described later, and discharge the working oil as high pressure oil. Is.

In this case, these pistons 37 are
As shown in FIG.
6 is a bottom dead center position that largely protrudes (extends), and a position below the rotary shaft 34 is a top dead center position that is reduced into the cylinder 36. Then, while the cylinder block 35 makes one rotation, each piston 37 slides in the cylinder 36 from the top dead center to the bottom dead center, and the piston 37 slides from the bottom dead center to the top dead center. The displacing discharge process is repeated.

In the intake stroke of the piston 37, which corresponds to a half rotation of the cylinder block 35, the working oil is sucked into the cylinder 36 from the side of the supply / discharge passage 44, which will be described later, and corresponds to the remaining half rotation of the cylinder block 35. Piston 3
In the discharge stroke of No. 7, the piston 37 discharges the oil liquid in each cylinder 36 as high-pressure pressure oil from the supply / discharge passage 43 side described later to, for example, the discharge pipe 4 side shown in FIG. 11.

Reference numerals 38, 38, ... Show shoes swingably provided at the projecting end of each piston 37. Each shoe 38 is pressed by the piston 37 (hydraulic pressure), and a swash plate 40 to be described later is provided. By being pressed by the smooth surface 40A, it slides on the smooth surface 40A so as to draw a ring-shaped locus.

Reference numeral 39 denotes a swash plate support provided on the front bottom portion 32A of the casing main body 32 around the rotary shaft 34. The swash plate support 39 is located on the back side of the swash plate 40, and It is fixed to the front bottom portion 32A of 32. The swash plate support 39 is formed with a pair of tilt sliding surfaces 39A, 39A for tiltably supporting the swash plate 40 as concave curved surfaces, and each tilt sliding surface 39A is shown in FIG. As shown, the rotary shaft 34 is sandwiched between the left and right sides.

Reference numeral 40 denotes a swash plate provided on the front bottom portion 32A side of the casing body 32 with a swash plate support 39 interposed therebetween.
As shown in FIG. 1, the swash plate 40 has a smooth surface 40A as a sliding surface on the front surface side, and an insertion hole 40B through which the rotary shaft 34 is inserted with a gap formed in the center thereof.

The swash plate 40 constitutes a variable capacity portion of the hydraulic pump, and the back side of the swash plate 40 is tiltably abutted on each tilt sliding surface 39A of the swash plate support 39. There is. As a result, the swash plate 40 is moved to the tilt actuator 45 described later.
Thus, the tilting drive is performed in the directions of arrows A and B in FIGS.

Reference numeral 41 denotes a tilt lever integrally formed on the side of the swash plate 40. The tilt lever 41 is provided on the stepped piston 47 described later from the side of the swash plate 40 as shown in FIGS. It has been extended toward. A projecting pin 41A is provided on the tip side of the tilt lever 41, and the projecting pin 41A is connected to a stepped piston 47 via an engaging plate 52 described later.

Reference numeral 42 denotes a valve plate fixedly provided on the rear casing 33. The valve plate 42 constitutes a switching valve plate which is in sliding contact with the end surface of the cylinder block 35. The valve plate 42 has a valve plate as shown in FIG. A pair of supply / discharge ports 42A, 42B are formed around the rotation shaft 34 and extend in an eyebrow shape. Of these supply / discharge ports 42A and 42B, for example, the supply / discharge port 42A is a high-pressure side discharge port, and the supply / discharge port 42B is a low-pressure side suction port.

Reference numerals 43 and 44 denote a pair of supply / discharge passages formed in the rear casing 33. The supply / discharge passage 43 on the high pressure side of the supply / discharge passages 43, 44 is connected to the discharge pipe 4 shown in FIG. 11, for example. The low pressure side supply / discharge passage 44 is connected to the tank 3 side. The high pressure side supply / discharge passage 43 communicates with the supply / discharge port 42A of the valve plate 42, and the low pressure side supply / discharge passage 44 communicates with the supply / discharge port 42B.

When the rotary shaft 34 is rotationally driven in the casing 31, the pistons 37 reciprocate in the respective cylinders 36 as the cylinder block 35 rotates, and these pistons 37 are moved from the supply / discharge passage 44 side to the cylinder 36. The pressure oil is discharged to the supply / discharge passage 43 side while sucking the working oil therein.

Reference numeral 45 is a tilting actuator provided in the actuator mounting portion 32B of the casing body 32.
The tilt actuator 45 has substantially the same structure as the tilt actuator 5 described in the related art, and tilts the swash plate 40 in the directions A and B as shown by a stepped piston 47 described later.

As shown in FIGS. 2 and 3, the tilting actuator 45 is a cylinder hole serving as a tilting control cylinder formed on the actuator mounting portion 32B of the casing body 32 and located outside the cylinder block 35 in the radial direction. 46A and 46B and a stepped piston 47, which will be described later, slidably fitted in the cylinder holes 46A and 46B.

Reference numeral 47 denotes a stepped piston as a servo piston which constitutes a movable part of the tilt actuator 45. The stepped piston 47 is slidably inserted into the cylinder hole 46A on the large diameter side as shown in FIG. The small diameter portion side is slidably inserted into the cylinder hole 46B. Then, the stepped piston 47 has a large diameter hydraulic chamber 4 inside the cylinder hole 46A.
8A is defined and a small diameter hydraulic chamber 4 is provided in the cylinder hole 46B.
8B is defined.

Further, as shown in FIGS. 3 to 5, the stepped piston 47 is provided with recesses 47A and 47B having a U-shaped cross section at positions facing each other in the radial direction (upper and lower), and one recess 47A is formed. An output pin 49 is provided at the center of. When the stepped piston 47 is slidably displaced along the cylinder holes 46A and 46B in the axial direction (directions A and B shown by arrows), the output pin 49 transmits the displacement to a feedback link 57, which will be described later. is there.

On the other hand, an engaging plate 52, which will be described later, is slidably attached to the recess 47B of the stepped piston 47. Further, as shown in FIGS. 7 and 8, a bottomed stop hole 47C is formed to extend in the axial direction on the end surface of the stepped piston 47 on the large diameter side. The stop hole 47C extends from the center of the stepped piston 47. It is arranged at an eccentric position. And the stop hole 4
7C is engaged with a shaft portion 63B of a jig 63, which will be described later, so that the stepped piston 47 moves into the cylinder holes 46A, 46B.
It is held inside in a non-rotatable state.

Numerals 50 and 51 are lid plates forming a part of the tilt actuator 45. As shown in FIG. 3, the lid plates 50 and 51 use bolts or the like on the left and right side surfaces of the actuator mounting portion 32B. And detachably fixed. The left cover plate 50 closes the cylinder hole 46A from the outside, and defines a hydraulic chamber 48A between the left cover plate 50 and the left end surface of the stepped piston 47.

The right lid plate 51 has a cylinder hole 46B.
Is closed from the outside to define a small-diameter hydraulic chamber 48B with the right end surface of the stepped piston 47. The small diameter hydraulic chamber 48B is connected to the tilt control pressure conduit 19 in place of the hydraulic chamber 8B of the tilt actuator 5 according to the prior art illustrated in FIG. 11, and the large diameter hydraulic chamber 48A is tilted. It is connected to the control pressure line 16.

Reference numeral 52 denotes an engaging plate slidably mounted in the recess 47B of the stepped piston 47.
Is formed as a substantially rectangular plate as shown in FIGS. 4 and 5, and the protrusion pin 4 of the tilting lever 41 is provided at the center thereof.
An engagement hole 52A into which 1A is inserted is formed.

Here, the engagement plate 52 is mounted in the recess 47B of the stepped piston 47 with the protruding pin 41A of the tilting lever 41 previously inserted into the engagement hole 52A. Then, in this state, the engagement plate 52 transmits the axial displacement of the stepped piston 47 to the swash plate 40 via the tilt lever 41,
As a result, the swash plate 40 follows the stepped piston 47 and is tilted in the directions of arrows A and B.

Reference numeral 53 is a regulator for supplying and discharging the tilt control pressure to and from the tilt actuator 45.
The valve case 54, the control sleeve 55, and the spool 5 are configured in substantially the same manner as the regulator 11 described in the related art.
It has 6 mag. Then, the valve case 54 includes the actuator mounting portion 32 of the casing body 32 as shown in FIG.
It is removably provided on the side of the actuator mounting portion 32B so as to cover the opening 32C provided in B from the outside.

A sleeve sliding hole (not shown) into which the control sleeve 55 is slidably inserted is formed in the valve case 54, and a spool 56 is provided in the control sleeve 55.
Is slidably inserted. The control sleeve 55 and the spool 56 are operated in substantially the same manner as the control sleeve 12 and the spool 13 of the regulator 11 shown in FIG.

Here, as shown in FIGS. 4 to 6, the control sleeve 55 has a notch portion 55A which is located on one side in the axial direction and which extends in an arc shape in the circumferential direction and engages with an engagement pin 60 described later.
And a plurality of oil holes 55B, 5 which are separated from the cutout portion 55A to the other side in the axial direction and penetrate in the radial direction of the control sleeve 55.
5C, 55D, etc. are provided, and these oil holes 55B, 5
5C and 55D communicate with and are blocked from the tank 3, the tilt control pressure lines 10 and 16 and the like illustrated in FIG.

Reference numeral 57 is a feedback link as a feedback mechanism for feedback-controlling the regulator 53 by following the tilting movement of the swash plate 2. The feedback link 57 is constructed in substantially the same manner as the feedback link 17 described in the prior art. However, they are different in that they have a pinching spring 61 described later.

As shown in FIGS. 2 to 7, the feedback link 57 is composed of a turning lever 58 described later, a pivot pin 59 as a support pin, an engaging pin 60 and a holding spring 61. Further, the rotating lever 58, the clamping spring 61, and the like are arranged so as to extend between the actuator mounting portion 32B and the valve case 54 of the regulator 53 substantially in parallel with the tilt lever 41 as shown in FIG. It is rotated around the pin 59.

Reference numeral 58 is a rotary lever as a rigid link member which constitutes a part of the feedback link 57, and the rotary lever 58 is formed of a rigid material such as steel as a rod-shaped body as shown in FIGS. , A pin hole 5 to which an engaging pin 60 described later is fixed by using a means such as press fitting.
8A is drilled.

Further, on the other end side of the rotating lever 58, a columnar head portion 58B to which a bent portion 61A of a holding spring 61, which will be described later, is fixed in a wound state is provided so as to project downward. Further, another pin hole 58C is formed in the middle portion of the rotation lever 58 in the longitudinal direction so that the pivot pin 59 penetrates up and down. As shown in FIG.
Reference numeral 8 is rotatably attached to the opening 32C of the actuator attachment portion 32B via a pivot pin 59.

Reference numeral 60 denotes an engagement pin fixed to the pin hole 58A of the rotation lever 58, and the engagement pin 60 is the rotation lever 5
It projects downward from one end side of 8 and is engaged with the notch 55A of the control sleeve 55. Then, when the turning lever 58 is turned (swing) about the pivot pin 59, the engagement pin 60 transmits the movement of the turning lever 58 to the control sleeve 55, whereby the control sleeve 55 is regulated. It is for sliding displacement in the axial direction within the valve case 54 of 53.

Reference numeral 61 denotes a sandwiching spring as an elastic link member which constitutes the feedback link 57 together with the rotating lever 58. The sandwiching spring 61 is an elongated metal spring plate having a spring property and has a length as shown in FIGS. 4 to 6. U in the middle of the direction
By bending it into a letter shape, it is formed as a pincer-shaped holding body (clip body), for example. Then, the holding spring 61 has a pair of holding portions 61B, 6 having a substantially U-shaped bent portion 61A at one end side and a bifurcated shape at the other end side.
It is 1B.

Further, as shown in FIG. 6, the bent portion 61A of the holding spring 61 is provided with a pair of pin mounting holes 61C and 61C at positions opposed to each other in the radial direction. The bent portion 61A of the holding spring 61 is fitted around the head portion 58B of the rotary lever 58 so as to be wound around the head portion 58B, and the stopper pin 62 is inserted into each pin mounting hole 61C and the head portion 58B. It is fixed to the portion 58B in a retaining state.

On the other hand, each holding portion 61B of the holding spring 61 is
The stepped piston 47 is inserted in a direction crossing the recess 47A, and is connected to the output pin 49 so as to sandwich the output pin 49 from both sides in the radial direction. The displacement of the stepped piston 47 is transmitted from the output pin 49 to the clamping spring 61, and the rotary lever 58 integrated with the clamping spring 61 causes the stepped piston 4 to move.
It follows the displacement of 7 and is rotated around the pivot pin 59.

Reference numeral 63 is a jig for holding the stepped piston 47 of the tilt actuator 45 in a rotation-stopped state. The jig 63 includes a lid portion 63A and a lid portion 63A as shown in FIG.
, And a shaft portion 63B that is inserted into the stop hole 47C of the stepped piston 47 and is fitted in the lid portion 63A. Plural bolt insertion holes 63C, 63C, ... Are bored in the lid portion 63A.

Here, the lid portion 63A of the jig 63 is replaced with the lid plate 50 shown in FIG. 3 to close the cylinder hole 46A from the outside when the hydraulic pump is assembled, for example.
As shown in FIG. 5, the actuator attachment portion 32B is detachably attached to the side surface of the actuator attachment portion 32B with a bolt or the like.

The shaft 63B of the jig 63 is fitted into the stop hole 47C of the stepped piston 47 as shown in FIG.
In this state, set the stepped piston 47 into the cylinder holes 46A, 46
It keeps the rotation stop in B. After the swash plate 40, the tilt lever 41, etc. are assembled in the casing 31 as described later, the jig 63 is moved to the actuator mounting portion 32.
Removed from the side of B, and in this state, cylinder hole 46A
Is to be closed from the outside by using a cover plate 50 as shown in FIG.

The variable displacement type swash plate type hydraulic pump according to the present embodiment has the above-mentioned structure, and its basic operation is not significantly different from that of the prior art.

However, according to the present embodiment, the feedback link 57 for transmitting the movement of the tilt actuator 45 to the control sleeve 55 of the regulator 53 and performing feedback control of the control sleeve 55 is provided with the rotation lever 58 made of a rigid material. And the holding spring 61 made of a spring material, the following operational effects can be obtained.

That is, when pressure pulsation occurs in the state where the discharge pressure of the hydraulic pump is high, the influence of the pressure pulsation is oblique through the cylinders 36 of the cylinder block 35, the pistons 37, etc. The swash plate 4 is transmitted to the plate 40.
0 may repeat high frequency vibration with a high vibration frequency due to the influence of pulsation.

Then, such high frequency vibration is generated by the swash plate 4.
Since it is transmitted from 0 to the stepped piston 47 of the tilt actuator 45 through the tilt lever 41, the engaging plate 52, etc.,
When the stepped piston 47 is exposed to high-frequency vibration, it also propagates to the feedback link 57 as a minute vibration, which may damage or damage the feedback link 57 under the influence of the high-frequency vibration.

However, in the present embodiment, the feedback link 57 is composed of the rotating lever 58 having rigidity and the sandwiching spring 61 having spring property, so that the sandwiching spring 61 damps high frequency vibration. It is possible to prevent this vibration from being directly transmitted to the rotating lever 58 made of a rigid material.

The holding spring 61 is formed, for example, as a tweezer-like holding body (clip body) by bending an elongated metal spring plate into a substantially U-shape at the middle portion in the longitudinal direction, and one end side thereof is formed. With a substantially U-shaped bent portion 61A,
The other end side is a pair of holding portions 61B, 61B extending in a bifurcated shape.

The bent portion 61A of the holding spring 61
Is attached to the head portion 58B of the rotating lever 58 so as to be wound around the head portion 58B by using a stop pin 62 or the like.
It is fixed to B in a retaining state, and each holding portion 61B of the holding spring 61 is connected to the output pin 49 so as to hold the output pin 49 from both sides in the radial direction within the recess 47A of the stepped piston 47. There is.

Therefore, when the tilt actuator 45 is operated, the axial displacement of the stepped piston 47 is converted into the output pin 49.
To the holding spring 61, the turning lever 58 can be moved integrally with the holding spring 61, the turning lever 58 can be turned about the pivot pin 59, and the control sleeve 55 of the regulator 53 is stepped. Feedback control can be performed following the displacement of the piston 47.

Therefore, according to the present embodiment, by constructing the feedback link 57 with the rotating lever 58 and the sandwiching spring 61, it is possible to properly suppress the high frequency vibration of the rotating lever 58, and to provide the feedback. Link 5
7. The durability and life of the whole 7 can be improved.

By using the feedback link 57, the control sleeve 55 of the regulator 53 can be stably feedback-controlled, and the capacity control of the swash plate type hydraulic pump can be stabilized for a long period of time to improve the reliability. it can.

Further, the holding spring 61 has a bent portion 61A on one end side fixed to the head portion 58B of the rotary lever 58 by a fixing pin 62 or the like so as to be wound, and each holding portion 61B on the other end side.
Are configured to be connected to the output pin 49 of the stepped piston 47 so as to be sandwiched from both sides in the radial direction. Therefore, by using such a sandwiching spring 61, the mounting direction of the feedback link 57 to the tilt actuator 45 can be easily performed. It is possible to increase the degree of freedom in mounting the regulator 53 and the like.

On the other hand, in the present embodiment, a jig 63 for holding the stepped piston 47 of the tilt actuator 45 in a rotation-stopped state is detachably provided on the actuator mounting portion 32B of the casing body 32. Since it has the configuration, the assembling work of the hydraulic pump can be efficiently performed.

That is, in the assembly process of the hydraulic pump,
After the tilting actuator 45, the regulator 53, the feedback link 57 and the like are attached to the actuator mounting portion 32B of the casing body 32, the rotary shaft 34, the swash plate support 39 and the like are incorporated into the casing body 32, and then the casing The swash plate 40, the cylinder block 35, and the like are sequentially installed on the inner side of the main body 32, and then the other end of the casing main body 32 is closed by the rear casing 33.

However, in the assembling process of the swash plate 40, as shown in FIG.
As illustrated in FIG. 5, the protruding pin 41A of the tilting lever 41 is removably inserted together with the engaging plate 52 into the concave portion 47B of the stepped piston 47 previously mounted in the cylinder holes 46A and 46B of the actuator mounting portion 32B. It is necessary to set the stepped piston 47 to the cylinder holes 46A and 46B at this time.
If it rotates inside, it becomes difficult to assemble them.

Therefore, in the present embodiment, as shown in FIG. 8, the lid 63A of the jig 63 is attached to the actuator mounting portion 32B.
Is detachably attached to the side surface of the cylinder using a bolt or the like so that the cylinder hole 46A is closed from the outside. At this time, the shaft portion 63B of the jig 63 is fitted into the stop hole 47C of the stepped piston 47, Step piston 47 into cylinder hole 4
6A and 46B are held in a rotation-stopped state.

As a result, the swash plate 40, the tilt lever 41, etc. are indicated by the arrow E in FIG.
When the stepped piston 47 is inserted into the inner side of the casing body 32 (front bottom portion 32A shown in FIG. 2).
Can be restricted from rotating in the cylinder holes 46A and 46B, and the protruding pin 41A of the tilt lever 41 can be easily engaged with the engaging plate 52 in the recess 47B of the stepped piston 47.

Therefore, at the time of assembling the hydraulic pump,
The stepped piston 47 of the tilt actuator 45 can be held in the cylinder holes 46A and 46B in a rotation-stopped state by using the jig 63, and in this state, the swash plate 40 is assembled into the casing body 32 together with the tilt lever 41 and the like. Thereby, the tilt lever 41 of the swash plate 40 can be efficiently connected to the stepped piston 47 in a short time.

After the swash plate 40, the tilt lever 41, etc. are assembled in the casing 31, the jig 63 is removed from the side surface (cylinder hole 46A side) of the actuator mounting portion 32B, and in this state, the cylinder hole 46A. Can be closed from the outside by using a cover plate 50 as shown in FIG. 3, and a hydraulic chamber 48A can be defined between the stepped piston 47 and the cover plate 50.

Next, FIG. 9 shows a second embodiment of the present invention, and the feature of this embodiment is that the mounting position of the regulator with respect to the casing of the hydraulic pump is changed. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the figure, reference numeral 71 denotes a casing of the hydraulic pump, and although the casing 71 has substantially the same structure as the casing 31 described in the first embodiment, the casing 71 is of the casing main body 72. The configuration is different from that of the first embodiment. That is, the casing body 72
Is the front bottom portion 72A, the actuator mounting portion 72B
And an opening 72C and the like.

However, the opening 72 of the casing body 72
C is to the left of the opening 32C described in the first embodiment,
It is formed at a position on the opposite side in the right direction (for example, the axial direction of the rotating shaft 34). As a result, the mounting position of the regulator 73 described later is also on the opposite side to the regulator 53 described in the first embodiment.

Reference numeral 73 is a regulator adopted in this embodiment. The regulator 73 has the same structure as the regulator 53 described in the first embodiment, and the valve case 74,
It has a control sleeve 75, a spool 76 and the like.

However, the valve case 74 of the regulator 73
Is the opening 7 provided on the left side face of the actuator mounting portion 72B of the casing main body 72 as shown in FIG.
Actuator mounting portion 72B so as to cover 2C from the outside
It is detachably attached to the left side of the. As a result, the feedback link 57 has a mounting direction opposite to that of the first embodiment.

Thus, the present embodiment having such a configuration can also obtain substantially the same operational effects as those of the first embodiment, but particularly in the present embodiment,
The regulator 73 is located at a position opposite to the actuator mounting portion 72B of the casing body 72 in the left and right directions (for example, the axial direction of the rotary shaft 34) from the first embodiment.
Can be provided.

That is, in the present embodiment, by using the holding spring 61 of the feedback link 57,
The attachment direction of the feedback link 57 with respect to the tilt actuator 45 can be reversed in the left and right directions, and the degree of freedom in attaching the regulator 73 and the like can be increased.

Also in this case, by using the feedback link 57 composed of the rotating lever 58 and the sandwiching spring 61, it is possible to favorably suppress the high frequency vibration of the rotating lever 58 and the feedback link 57.
The overall durability and life can be improved, and the control sleeve 75 of the regulator 73 can be stably feedback-controlled to improve reliability.

Next, FIG. 10 shows a third embodiment of the present invention, which is characterized in that the mounting position of the regulator on the casing of the hydraulic pump is changed in the direction away from the rotary shaft. Especially. In this embodiment, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the figure, reference numeral 81 indicates a casing of the hydraulic pump, and although the casing 81 is constructed in substantially the same manner as the casing 31 described in the first embodiment, the casing 81 is of the casing main body 82. The configuration is different from that of the first embodiment. That is, the casing body 82
Is the front bottom portion 82A and the actuator mounting portion 82B.
And an opening 82C and the like.

However, the opening 82 of the casing body 82
Unlike the opening 32C described in the first embodiment, C is formed, for example, at a position spaced radially outward of the rotary shaft 34. Thereby, the regulator 8 described later
5 is also arranged at a position further outside in the radial direction than the regulator 53 described in the first embodiment.

Reference numeral 83 denotes a tilting actuator provided on the actuator mounting portion 82B of the casing main body 82, and the tilting actuator 83 has substantially the same structure as the tilting actuator 45 described in the first embodiment. However, in the tilt actuator 83, the stepped piston 84 has a different shape.

An output pin 49 for the feedback link 57 is attached to the stepped piston 84 in a direction substantially parallel to the rotary shaft 34. Further, the pivot pin 59 of the feedback link 57 has the casing body 8
It is attached to the second opening 82C and extends in a direction substantially parallel to the rotating shaft 34. The turning lever 58 and the holding spring 61 of the feedback link 57 are oriented so as to extend in the radial direction of the rotating shaft 34.

Reference numeral 85 is a regulator adopted in the present embodiment. The regulator 85 has the same structure as the regulator 53 described in the first embodiment, and the valve case 86,
It has a control sleeve 87, a spool 88 and the like.

However, the valve case 86 of the regulator 85
As shown in FIG. 10, the actuator attachment portion 82B of the casing main body 82 is detachably attached to the actuator attachment portion 82B so as to cover the opening portion 82C provided on the radially outer surface from the outside, for example. As a result, the feedback link 57 is arranged in a mounting direction different from that of the first embodiment by about 90 degrees.

Thus, the present embodiment having such a configuration can obtain substantially the same operational effect as that of the first embodiment, but particularly in the present embodiment,
The regulator 85 can be arranged at a position on the outside of the actuator mounting portion 82B of the casing body 82 in the radial direction different from that of the first embodiment.

That is, in the present embodiment, by using the holding spring 61 of the feedback link 57,
It is possible to change the mounting direction of the feedback link 57 with respect to the tilt actuator 83 by about 90 degrees, and it is possible to increase the degree of freedom in mounting the regulator 85 and the like.

Also in this case, by using the feedback link 57 composed of the rotating lever 58 and the holding spring 61, it is possible to well suppress the high frequency vibration of the rotating lever 58, and the durability and life of the entire feedback link 57. In addition, the control sleeve 87 of the regulator 85 can be stably feedback-controlled, and the reliability can be improved.

In each of the above-mentioned embodiments, the case where the swash plate type hydraulic pump is used as the variable displacement hydraulic rotating machine has been described as an example, but the present invention is not limited to this.
For example, it may be applied to a variable displacement swash plate hydraulic motor, or may be applied to a swash shaft hydraulic pump, a hydraulic motor, or the like.

[0127]

As described in detail above, according to the first aspect of the invention, in order to transmit the movement of the tilt actuator to the control sleeve of the regulator, it is provided between the control sleeve of the regulator and the tilt actuator. Since the feedback link is formed by using a spring material that attenuates high frequency vibration, when the variable capacity section repeats high frequency vibration due to hydraulic pulsation, etc., this high frequency vibration is tilted from the variable capacity section. Even if it is transmitted to the actuator, the high frequency vibration can be damped by the spring material forming a part of the feedback link, and the damage and damage of the feedback link due to the repetition of minute vibration can be suppressed. Therefore, the durability and life of the entire feedback link can be improved, the control sleeve of the regulator can be stably feedback-controlled, and the capacity control of the hydraulic rotary machine can be stabilized for a long period of time to improve reliability. be able to.

Further, according to the invention described in claim 2, when the swash plate repeats high frequency vibration due to the influence of hydraulic pulsation or the like,
Even if this high-frequency vibration is transmitted from the swash plate to the tilt actuator, the high-frequency vibration can be damped by the spring material forming a part of the feedback link, and damage and damage to the feedback link due to repeated microvibration can be suppressed. Therefore, the durability and life of the entire feedback link can be improved, stable feedback control of the control sleeve of the regulator can be performed, and the capacity control of the swash plate hydraulic rotary machine can be stabilized for a long period of time to improve reliability. it can.

According to the third aspect of the present invention, the feedback link is composed of the rigid link member and the elastic link member made of a spring material. Therefore, the elastic link member elastically applies high frequency vibration from the tilt actuator. It can be attenuated by the link member and transmitted to the rigid link member, and the rigid link member can be prevented from repeating microvibration, and the durability and life of the rigid link member can be improved.

According to the invention described in claim 4,
Since the elastic link member is formed by bending an elongated spring material into a substantially U-shape, the bent portion side can be fixed by winding it around the other end side of the rigid link member. The movement of the tilt actuator can be transmitted to the rigid link member by sandwiching the pin of the tilt actuator from the radial direction, and thus the rigid link member can be prevented from being exposed to high frequency vibration. Further, by using such an elastic link member, the mounting direction of the feedback link with respect to the tilt actuator can be changed in three axial directions, and the degree of freedom in mounting the regulator or the like can be increased.

Further, according to the invention of claim 5,
The tilt actuator comprises a tilt control cylinder and a servo piston, and a jig for holding the servo piston in the rotation control cylinder in the tilt control cylinder can be attached and detached between the casing and the servo piston. Therefore, for example, at the time of assembling work of the variable displacement hydraulic rotary machine, the servo piston of the tilt actuator can be held in a rotation stop state by using a jig in the tilt control cylinder,
By incorporating the variable volume portion (swash plate) in the casing in this state, the variable volume portion can be efficiently connected to the servo piston in a short time, and workability during assembly can be reliably improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a variable displacement swash plate hydraulic pump according to a first embodiment of the present invention.

FIG. 2 is an arrow II in FIG. 1 showing a tilt actuator, a regulator, a feedback link, etc. of the hydraulic pump.
It is the sectional view seen from the -II direction.

FIG. 3 is a sectional view showing a cylinder block, a tilt actuator, a feedback link, etc. of the hydraulic pump in an enlarged manner as seen from the direction of arrows III-III in FIG.

4 is an enlarged perspective view showing a swash plate, a tilt lever, a stepped piston, a feedback link, a control sleeve and the like in FIG.

5 is an exploded perspective view showing enlargedly a tilt lever, a stepped piston, a feedback link, a control sleeve and the like in FIG.

FIG. 6 is an exploded perspective view of the stepped piston, the feedback link, the control sleeve, and the like in FIG. 5 viewed from different directions.

7 is an exploded perspective view showing a swash plate, a tilt lever, a stepped piston, a feedback link and the like in FIG. 2 together with a jig.

FIG. 8 is an enlarged cross-sectional view showing a state in which a jig is attached to the actuator attachment portion of the hydraulic pump, as seen from the direction of arrows VIII-VIII in FIG. 2.

9 is a vertical cross-sectional view showing a variable displacement swash plate hydraulic pump according to a second embodiment from the same position as in FIG.

FIG. 10 is a vertical sectional view showing a variable displacement swash plate hydraulic pump according to a third embodiment from the same position as in FIG.

FIG. 11 is a hydraulic circuit diagram for capacity control of a swash plate hydraulic pump according to a conventional technique.

[Explanation of symbols]

31,71,81 Casing 32, 72, 82 casing body 32B, 72B, 82B actuator mounting part 32C, 72C, 82C opening 33 Rear casing 34 rotation axis 35 cylinder block 36 cylinders 37 pistons 38 shoe 39 Swash plate support 40 Swash plate (variable volume part) 40A Smooth surface (sliding surface) 41 Tilt lever 42 valve plate 43,44 supply and discharge passage 45,83 Tilt actuator 46A, 46B Cylinder hole (tilt control cylinder) 47,84 Stepped piston (servo piston) 47A, 47B recess 47C stop hole 48A, 48B hydraulic chamber 49 output pins 52 engagement plate 53, 73, 85 regulator 54,74,86 valve case 55,75,87 Control sleeve 56,76,88 spools 57 Feedback link (feedback mechanism) 58 Rotating lever (rigid link member) 59 Axis pin (support pin) 60 engagement pin 61 Clamping spring (elastic link member) 63 jig

Continued front page    F term (reference) 3H070 AA01 BB06 BB25 CC07 DD31                 3H071 AA03 BB01 CC26 DD89 EE15                 3H084 AA08 AA16 BB09 CC32 CC35

Claims (5)

[Claims] 1. A casing of a hydraulic rotary machine having a variable capacity section, and a tilting drive for tilting the variable capacity section according to a tilting control pressure provided in the casing and supplied and discharged from the outside. An actuator, a regulator composed of a servo valve provided in the casing for variably controlling the tilt control pressure supplied to and discharged from the tilt actuator and having a spool in a control sleeve, and a tilt operation of the capacity varying unit are followed. And a feedback mechanism for feedback controlling the control sleeve of the regulator, wherein the feedback mechanism is provided between the control sleeve of the regulator and the tilt actuator. A feedback link for transmitting the movement of the actuator to the control sleeve, the feedback link comprising: Without even variable displacement type liquid-pressure rotating, characterized in that formed using a spring member for damping high-frequency vibrations of the part. 2. A cylindrical casing, a rotary shaft rotatably provided in the casing, and a shaft provided in the casing so as to rotate together with the rotary shaft and spaced apart in a circumferential direction of the rotary shaft. Cylinder block having a plurality of cylinders extending in the same direction, a plurality of pistons reciprocatingly fitted into the cylinders of the cylinder block, and an end of each piston tiltably provided in the casing. A swash plate having a sliding surface on which a shoe mounted on the portion slides; and a tilt actuator that tilts and drives the swash plate according to tilt control pressure that is provided in the casing and is externally supplied and discharged. A regulator including a servo valve provided in the casing and having a spool in a control sleeve for variably controlling a tilt control pressure supplied to and discharged from the tilt actuator; and a tilt operation of the swash plate. Accordingly, in a variable displacement hydraulic rotary machine including a feedback mechanism for performing feedback control of the control sleeve of the regulator, the feedback mechanism is provided between the control sleeve of the regulator and the tilt actuator. A variable displacement hydraulic rotating machine comprising a feedback link for transmitting the motion of a rotary actuator to a control sleeve, and at least a part of the feedback link is formed by using a spring material for damping high frequency vibration. 3. The feedback link includes a rigid link member rotatably attached to the casing, one end side of which is made of a rigid material connected to a control sleeve of the regulator, and one end side of which is connected to the other end side of the rigid link member. 3. The variable capacitance type according to claim 1, wherein the variable capacity type is formed of a spring material that is fixed and the other end side is connected to the tilt actuator, and is configured by an elastic link member that transmits the movement of the tilt actuator to the rigid link member. Hydraulic rotary machine. 4. The elastic link member is formed by bending an elongated spring member into a substantially U shape, and the bent portion side is wound around and fixed to the other end side of the rigid link member to form a bifurcated shape. 4. The variable displacement hydraulic rotating machine according to claim 3, wherein the tip side extending to the tilt actuator is connected so as to be sandwiched from both sides in the radial direction with respect to the pin provided on the tilt actuator. 5. The tilt actuator comprises: a tilt control cylinder provided in the casing; and a tilt control pressure supplied to and discharged from the tilt control cylinder so as to be slidably fitted in the tilt control cylinder. The tilt control cylinder includes a servo piston that is displaced in the axial direction in the tilt control cylinder, and the servo piston is provided between the casing and the servo piston when the capacity varying unit is incorporated in the casing. The variable displacement hydraulic rotating machine according to claim 1, 2, 3, or 4, wherein a jig for holding the rotation-stopped state inside is detachably provided.