WO2001066942A1

WO2001066942A1 - Swash plate type axial piston hydraulic unit

Info

Publication number: WO2001066942A1
Application number: PCT/JP2001/001887
Authority: WO
Inventors: Kunihiko Sakamoto; Takeaki Nozaki; Kouji Sakata; Masaki Nankou
Original assignee: Yanmar Diesel Engine Co., Ltd.
Priority date: 2000-03-10
Filing date: 2001-03-09
Publication date: 2001-09-13

Abstract

A swash plate type axial piston hydraulic unit formed as a hydraulic pump or a hydraulic motor by installing plungers (3) in a plunger block (2) along the rotating axis of the plunger block (2) rotated while sliding on a valve plate (18) and arresting, on the swash plate (5) through retainers (6), shoes (4) installed, integrally with each other, on the head parts of the plungers projected from the plunger block, wherein a platy retainer function part (6d) forming guide holes (6a) for guiding and arresting the shoes and a fitting part for directly fitting the plungers into the curved rotating axis tip part (2b) of the plunger block are formed on the retainer, a center hole (6c) allowing the rotating axis tip part of the plunger block to be inserted is formed in the retainer at the center part of the retainer function part, a pressing part (6b) having a spring elasticity and pressing the rotating axis tip part is disposed facing the center hole, and the center hole and pressing part form a fitting part fitted to the rotating axis tip part of the plunger block.

Description

Description Swash plate type axial biston hydraulic unit Technical field

The present invention relates to a structure of a retainer for holding a connection between a swash plate and a piston (plunger) of a swash plate type axial piston hydraulic unit applied to a hydraulic pump and a hydraulic motor of a hydraulic stepless transmission. . Background art

The structure of a conventional general swash plate type axial piston type hydraulic unit applied to a hydraulic pump ゃ a hydraulic motor of a hydraulic type continuously variable transmission will be described with reference to FIG. A valve plate 113 is rotatably slidably abutted on one side of the plunger block 102. Along with the axis of the plunger block 102 and the valve plate 113, a rotary shaft provided as a pump shaft or a motor shaft 101 force is not allowed to rotate relative to the plunger block 102. The rotating shaft 101 passes through the swash plate 105 (fixed or movable) disposed on the opposite side of the plunger block 102 from the valve plate 113. I have.

A plurality of plungers 103 parallel to the rotation axis 101 are arranged radially around the rotation axis 101 in the plunger mouthpiece 102, and are slidably fitted. . The tip of the plunger 103 protrudes from the plunger block 102, and the tip 104, which is mounted via a ball * socket type joint 104a at the tip, comes into contact with the swash plate 105. I have. The shower 104 is pressed against the swash plate 105 by a retainer 106 described later.

The periphery of the rotation axis 101 of the bunjab mouthpiece 102 protrudes toward the swash plate 105, and the protruding end thereof is slidable relative to the rotation axis 101. An outer peripheral surface provided so as not to rotate is fitted into a hemispherical retainer guide 112.

At the center of the plunger block 102, a panel chamber 107 is formed at a fixed length along the rotation axis 101 from the surface facing the valve plate 113. Spring chamber 1 0 7 In the vicinity of the valve plate 113, a stop ring 110 for inserting the rotary shaft 101 is fixedly provided at a position near the valve plate 113, and opposed thereto, the rotary shaft 101 is inserted while the rotary shaft 101 is inserted. A movable ring 109 movable along is provided. Movable ring 109 and Stono ,. A compression panel 111 is interposed between the ring 110 and the rotation axis 101, and the compression panel 111 directs the movable ring 109 to the swash plate 105. It is energizing.

In the vicinity of the rotating shaft 101, a push pin 1 08 parallel to the rotating shaft 101 is freely moved to the plunger block 102, and one end of each push pin 108 is connected to the plunger block 102. The other end is in contact with the movable ring 109, and the other end is in contact with the retainer guide 112. The force of the compression spring 111 is transmitted to the retainer guide 112 via the movable ring 109 and the push pin 108 to urge the retainer guide 111 toward the swash plate 105. are doing. The force of the compression spring 111 also acts as a pressing force of the plunger block 102 against the valve plate 113.

The retainer 106 has a ring plate shape as a whole, and the inner peripheral surface of the central hole 106 a is curved to have the curvature of the outer peripheral spherical surface of the retainer Naga 12. The retainer is slidably fitted into 06 a with strong force. Further, a plurality of guide holes 106 b are formed radially around the center hole 106 a, and each of the plurality of guide holes 106 b is provided with a respective plunger 103 and a shroud 110. A ball-and-socket type hand 104 is provided between the terminal 104 and the terminal 104. The force by which the retainer guide 1 1 2 presses the inner peripheral surface of the retainer 106 a to the swash plate 105 with the force of the compression panel 111 It extends radially to the outer periphery of 06, and as a result, the retainer 106 is pressed against the swash plate 105 by the retainer 106. In this way, the retainer 106 presses the swash plate 104 against the swash plate 105 while the plunger mouthpiece 102 rotates integrally with the rotating shaft 101, and the swash plate 10 5 and the connection of all the plungers 103, so that the plunger 103 normally reciprocates while revolving around the rotating shaft 101. In particular, the plunger 103 entering the P stroke enters the plunger block 102 exactly against the pipe resistance, and a specified amount of oil is supplied to the plunger 103 via the valve plate 113. Inhalation. The conventional axial piston type hydraulic pump or hydraulic motor shown in FIG. In order to prevent the shell 104 from disengaging from the swash plate 105 and to press the plunger block 102 against the valve plate 113, the retainer 106 and the A large number of members are required, such as a guide 1 112, a push pin 108, a movable ring 109, a compression spring 111, and a stopper ring 110. This was a factor in increasing the size and cost of the equipment.

Further, in this structure, the compression spring 111 is arranged in the axial direction of the plunger block 102, and although the pressing force against the valve plate: I13 of the plunger block 102 is secured, This became too large and the overall efficiency of the hydraulic unit (hydraulic pump or hydraulic motor) was low. In order to improve the overall efficiency, the pressing force on this valve plate; 113 should be reduced, but the action of the plunger block 102 trying to separate from the valve plate 113 during rotation should be Effective deterrence is needed. Disclosure of the invention

An object of the present invention is to dispose a plunger inside a plunger block along a rotation axis of a plunger block that is rotated as a hydraulic pump or a hydraulic motor, and to project the plunger from the plunger opening with a retainer. This is an axial piston type hydraulic unit that restrains the shower integrally provided on the plunger head against the slant, and reliably secures the plunger head without requiring many parts as in the past. And a retainer that prevents the plunger block from coming off the valve plate, thereby improving assembly efficiency, making the equipment compact, and reducing costs. And to improve the overall efficiency of the hydraulic unit.

In order to achieve this object, the retainer has a plate-shaped retainer function portion forming a guide hole for guiding and restraining the shoe, and a panel elasticity for directly fitting the plunger block. And a fitting portion having the same. As described above, since the retainer itself is provided with the fitting portion directly to the plunger mouth, a retainer different from the above-described retainer is fitted to the plunger mouth. This eliminates the need for many components to achieve the above-described effects. Then, friction is generated between the fitting portion having spring elasticity and the plunger hook to cause hysteresis in the fitting portion, thereby causing the unbalance acting during rotation of the plunger block. Moment (force for detaching from the valve plate) can be effectively suppressed. Therefore, the pressing force on the valve plate can be small, and the overall efficiency of the hydraulic unit can be increased accordingly.

In the retainer, a central hole is formed at a central portion of the plate-shaped retainer function portion so as to fit a tip end of a rotation axis of the plunger hook, and opposed to the central hole, A pressing portion which has a panel elasticity and presses against the tip of the rotary shaft is disposed, and the center hole and the pressing portion are fitted to the tip of the rotary shaft of the plunger hook. Department. That is, the fitting to the plunger block can be obtained by a simple structure in which the tip of the rotation axis is fitted into the center hole of the retainer, and the pressing contact portion having panel elasticity is pressed. Yes, the urging force from the plunger block to the swash plate is applied to the retainer via the pressing portion, and the plunger block swings due to the spring elastic force during the rotation of the hydraulic unit. This ensures that the shoe is bound to the swashplate.

Then, at the pressing portion pressed against the tip of the rotating shaft core of the plunger block, the above-mentioned hysteresis occurs, and the unbalance moment acting on the rotating plunger block is effectively suppressed, and the pressure from the valve plate is reduced. Withdrawal can be prevented. A part of the retainer function part between the adjacent guide holes in the retainer is formed with a constricted portion that extends a part of the guide hole, thereby dispersing stress that tends to concentrate on the part. The durability of the retainer can be increased.

Further, when the portion between the adjacent guide holes in the retainer itself is an arm-shaped portion having a pressing contact portion as described later, the spring constant of the arm-shaped member is reduced. This increases the panel elasticity and prevents the plunger block from coming off the swash plate. Effective hysteresis can be generated.

Further, when the pressing force of the retainer unit against the shoe becomes weaker as the elasticity is imparted, the retainer function part forms a protrusion in contact with the shoe near the guide hole. As a result, a concentrated pressing force is applied to the projection, and the restraining force on the shoe can be secured. It is also conceivable to secure the rigidity of the retainer by forming the retainer function portion of the retainer into a disk shape and bending the outer peripheral edge thereof over the entire periphery to form a flange portion.

By making a notch that connects at least one of the guide holes and the center hole in the retainer, the entire press-contact portion has the flexibility to absorb the run-out of the plunger lock, thereby generating effective hysteresis. As a result, unbalanced moments that occur during rotation of the plunger block and attempt to separate the plunger block from the valve plate can be reliably suppressed. In addition, the spring constant of each pressing portion formed between the cuts is reduced, so that the hysteresis for preventing the plunger block from being detached from the valve plate can be increased.

If the guide holes are formed at regular intervals in at least three directions around the center hole, it is conceivable to divide the pressing portion of the peripheral edge of the center hole into three by the cut. That is, a uniform pressing contact portion is arranged in three directions from the axis of the plunger block, and a uniform biasing force is applied to the swash plate in almost all directions from the plunger block via the retainer, and In the pressing portion, substantially omnidirectional hysteresis occurs, so that the behavior of the plunger block can be effectively suppressed.

Further, by forming a notch communicating the guide hole of the retainer and the outside of the outer peripheral edge of the retainer, an effect of reducing the panel constant of the retainer itself can be obtained. A more desirable effect can be expected by providing a notch that connects the hole and the guide hole.

The above-mentioned cuts can be easily obtained by a press or the like during the processing of the retainer, that is, the effect of reducing the panel constant of the retainer can be obtained without requiring other parts. .

First, it is conceivable that the pressing portion of the retainer is formed by bending the entire inner peripheral edge forming the center hole of the retainer function portion into a spring shape. A push-contact portion is provided around the entire periphery of the tip of the rotating shaft core of the plunger jaw to ensure the fitting, and the inner periphery of the retainer can be easily folded over the entire periphery with a press or the like. Can be obtained.

And secondly, a center hole is formed at the inner peripheral edge of the retainer function part, May be formed in a portion different from the inner peripheral edge of the retainer function portion. In this case, the retainer function section can be processed in a simple disk shape, and only a part of the retainer can be processed in another process to obtain the pressing portion.

The number of the pressing portions configured in this way is determined by the number necessary for holding the target plunger block, and an appropriate number of pressing portions may be formed. Here, at least three are required to generate omnidirectional hysteresis in the retainer, and if the number of guide holes is larger than the number of plungers, rigidity will be lacking. The range should be at least three and no more than the number of plungers. The following structure is possible by forming the pressing portion at a portion different from the inner peripheral edge of the retainer function portion forming the center hole in the retainer as described above. That is, when fitting the tip of the rotating shaft core of the blanc lock to the fitting portion of the retainer, when the fitting depth of the rotating shaft core tip is shallow, it is in contact with only the pressing portion, By fitting it deeper, it also comes into contact with the inner peripheral edge of the retainer function part. Therefore, when the behavior of the plunger hook is large during the operation of the hydraulic unit, the inner peripheral edge of the retainer function portion comes into contact with the tip of the rotation shaft core of the plunger lock, thereby acting as a stopper. By preventing the retainer from being pushed into the valve 扳 side of the plunger block, damage can be prevented.

In the above-described second structure, a part of the retainer function part may be a part extending toward the center part, and the pressing part having panel elasticity may be formed by bending the part. Conceivable. That is, in this way, by simply utilizing a part of the retainer function part and extending it centripetally, the part necessary for the pressing part can be obtained by the retainer.

As one of the structures for forming such a pressing portion, it is considered that a part of the inner peripheral edge of the retainer function portion is bent and extended so as to have panel elasticity, thereby forming the pressing portion. Can be That is, a part of the inner peripheral edge of the retainer function part may be extended as the pressing part. In this structure, while the rigidity of the inner peripheral edge of the retainer function portion is ensured to be high, a pressing portion having panel elasticity can be formed.

The other is to form an arm-shaped portion toward the center from at least a position on the outer peripheral side of the inner peripheral edge of the retainer function portion, and bend it appropriately to have spring elasticity. W

It is conceivable to form a pressing portion that performs the pressing. Since the arm-shaped portion can be long, the panel constant can be reduced, high spring resilience can be obtained in the pressing portion, and the shape can be devised in various ways to optimize the stress distribution, etc. The degree of freedom increases. If the arm-shaped portion extends from the outer peripheral edge of the retainer function portion to the center hole, the longest dimension of the arm-shaped portion can be secured, and the above-mentioned effect can be reliably obtained. As a bending mode of the arm portion for obtaining the panel elasticity, it is conceivable that the arm portion is bent in a substantially S-shape or a substantially arc shape to form a pressing portion at the tip end thereof. Alternatively, it is also conceivable to extend the arm-like portion substantially linearly and to bend only the tip portion thereof to form a pressing portion. In this case, the pressing portion can be obtained by easy bending.

First, it is conceivable that a contact surface of the pressing portion of the retainer with respect to the tip of the rotating shaft center of the curved plunger hook may be substantially planar. In this case, the process of forming the contact portion is simple.

Alternatively, the contact surface of the pressing portion is formed as a substantially concave curved surface, and its curvature is made substantially coincident with the curvature of the curved surface of the tip end of the rotary shaft of the plunger hook to increase the contact area. Thus, the Hertzian surface pressure applied to both can be reduced, the fitting to the plunger block can be reliably obtained, and the durability of the retainer and the plunger block can be improved. The curvature of the contact surface of such a pressing portion should be substantially the same as the curvature of the curved surface of the tip of the rotation axis of the plunger lock when viewed in a cross section along the axis of the tip of the rotation axis of the plunger lock. By doing so, the effect of absorbing the axial run-out of the plunger mouth can be greatly obtained.

On the other hand, the curvature of the contact surface of such a pressing portion is such that when viewed in a cross section orthogonal to the axis of the tip of the rotation axis of the plunger block, the curved surface of the tip of the rotation axis of the plunger mouthpiece. If the curvature substantially matches the curvature of the plunger block, the effect of absorbing the touch around the axis of the plunger block can be greatly obtained. In addition, since the drawing process does not have to be performed when the pressing portion is processed, the processing can be simplified and the cost can be reduced.

According to another aspect, the curvature of the contact surface of the pressing portion may be larger than the curvature of the curved surface of the tip of the rotation axis of the plunger block. Even in this case, a large contact area can be ensured to some extent, and it can be expected that the effect of reducing the Hertzian surface pressure applied to both of them can be obtained. The effect of reducing the Hertzian surface pressure and the effect of suppressing the behavior of the plunger jaw by panel elasticity W

While observing, etc., the curvature of the contact surface of the pressing portion is increased in this way, or the curvature of the curved surface of the tip end of the rotating shaft of the plunger block is made approximately the same as described above, so that the optimum What is necessary is just to set the curvature of the contact surface.

Also in this case, the curvature is measured when viewed in a cross section along the axis of the tip of the rotation axis of the plunger block, or when viewed in a cross section orthogonal to the axis of the tip of the rotation axis of the plunger block. The above effects can be enhanced in the direction of the axis of the plunger block and in the direction around the axis, respectively, by making the curvature of the curved surface at the tip of the rotation axis of the plunger mouth larger. be able to.

Conversely, it is also conceivable that the contact surface of the pressing portion of the retainer is a substantially convex curved surface. In this case, intensive surface pressure is applied in a small area to the tip of the rotating shaft core of the plunger lock, and the pressing portion and the plunger hook are securely pressed against each other.

It is also conceivable that the pressing portion of the retainer is bent in a substantially V-shape to abut on the tip of the rotating shaft of the plunger block at two points to ensure the pressing. In the case of this substantially V-shaped bent structure, if the pressing portion bends in a substantially V-shape when viewed in a cross section along the axis at the tip of the rotation axis of the plunger block, the shaft of the plunger jaw In addition to obtaining the above-mentioned effect in the center direction, the rotation axis of the push-contact portion and the plunge-mouth opening can be selected according to the fitting depth of the tip of the rotation axis of the plunger mouth into the press-contact portion. The number of contact points with the part is changed. That is, one point can be set if the fitting is shallow, and two points can be set if the fitting is deep. In this case, for example, if the pressing portion is formed by the arm-like portion, the mounting state (position) of the retainer to the plunger block, that is, the one-point contact state and the two-point contact state The length dimension from the base end of the arm-shaped part of the retainer to the pressing part changes depending on the contact state. In other words, the arm-shaped part has the optimum spring constant in each mounting state.

Alternatively, it is conceivable that the pressing portion is bent substantially in a V-shape when viewed from a cross section orthogonal to the axis of the tip of the rotation axis of the plunger block. In this case, the above-described effect can be greatly obtained in the direction around the axis of the plunger block. The pressing portion may be made of a member different from the member forming the retainer function portion of the retainer. In this case, as a structure for connecting the pressing portion to the retainer, the pressing portion is formed integrally with one end of the arm-shaped member, and the other end of the arm-shaped member is connected to the retainer. -It is conceivable to fit into a notch or hole formed in the hole.

In this case, the thickness of the retainer itself as the retainer function part can be made different from the thickness of the pressing part and the arm-shaped member forming the same. That is, it is conceivable that the retainer itself is made thicker to secure rigidity, and the arm-shaped member is made thinner to lower the panel constant.

Also, if properly removed, the retainer and the arm-like members themselves have simple and compact configurations, respectively, and can be easily configured.

In the retainer, a notch or a hole for connecting the arm-shaped member is formed at a position closer to the outer peripheral edge than the guide hole of the retainer. A large length of the member can be secured, and the panel constant can be set low.

By forming the contact surface of the pressing portion to the plunger block in a curved shape, the plunger block is securely supported.

Other and further objects, features, and advantages of the present invention will become apparent in the following description with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a side sectional view of a conventional axial piston type hydraulic unit. FIG. 2 is a side sectional view of an axial piston type hydraulic unit having a retainer according to the first embodiment of the present invention.

FIG. 3 is a front view of the retainer 6 used in the embodiment of FIG.

FIG. 4 is a side sectional view of the retainer 6 shown in FIG. 3 in a state where the retainer 6 is mounted at a predetermined position.

FIG. 5 is a front view of the retainer 6 according to the second embodiment in which the outer peripheral edge of the retainer 6 shown in FIG. 3 is cut off.

FIG. 6 is a front view of a retainer .6 according to a third embodiment having a structure in which several guide holes 6a are connected to each other and divided into three guide hole groups.

FIG. 7 is a front view of the retainer 6 according to the fourth embodiment in which a constriction 6 g is formed in a part of the guide hole 6a. FIG. 8 is a perspective view of the retainer 6 according to the fifth embodiment in which the inner peripheral edge of the retainer function portion 6d is further bent to form the pressing portion 6b.

FIG. 9 is a side sectional view of the fifth embodiment.

FIG. 10 is a front view of a sixth embodiment of the retainer 6 having a shape obtained by cutting the outer peripheral portion of the retainer 6 of FIG.

FIG. 11 is a perspective view of a structure in which a retainer 16 and a panel member 17 are combined.

FIG. 12 is a side sectional view showing a state where the retainer 16 and the panel member 17 shown in FIG. 11 are mounted.

FIG. 13 is a side sectional view of an embodiment in which a contact portion of the spring member 17 with the spherical portion 2b is curved.

Fig. 14 shows a retainer 6 having a structure in which the guide hole 6a and the center hole 6c communicate with each other at the cut 6f, and the seventh embodiment in which three cuts 6f are formed at equal intervals. FIG.

FIG. 15 is a perspective view of an eighth embodiment of the present invention having a structure in which a notch 6ί is formed for each of the entire guide holes 6a.

FIG. 16 shows a retainer according to a ninth embodiment in which the pressing portion 6b is provided by three tongue pieces 11 formed by partially extending the inner peripheral edge of the retainer function portion 6d. FIG.

FIG. 17 shows that six tongue pieces 11 formed by partially extending the inner peripheral edge of the retainer function part 6 d are divided into three places, and these are used to press the contact parts 6 b. FIG. 28 is a perspective view of a retainer 6 according to a tenth embodiment that provides the following.

FIG. 18 shows that the tongue pieces 11 as many as the number of the guide holes 6 a partially extending on the inner peripheral edge of the retainer function part 6 d are arranged at equal intervals, and these tongue pieces are FIG. 9 is a perspective view of a retainer 6 according to a first “1” embodiment, in which a pressing portion 6 b is formed.

FIG. 19 shows a twelfth embodiment in which an S-shaped bent spring arm 12 is extended from the outer peripheral edge of the retainer function part 6 d to the center to form a pressing contact part 6 b. FIG. 4 is a perspective view of such a retainer 6.

FIG. 20 shows a portion between adjacent guide holes 6a in the retainer function portion 6d. Is a perspective view of a retainer 6 according to a thirteenth embodiment in which the spring arm 12 is used as it is.

FIG. 21 shows a second embodiment in which a portion between the adjacent guide holes 6 a in the retainer function portion 6 d is used as it is as a spring arm 12, and a neck 6 g is formed at the base end of the arm-shaped portion 12. FIG. 21 is a perspective view of a retainer 6 according to a fourteenth embodiment.

FIG. 22 is a perspective view of a retainer 6 according to the fifteenth embodiment in which a projection 6i is formed around a guide hole 6a.

FIG. 23 is a view taken along the line X X H—XX X in FIG.

FIG. 24D is a perspective view of a retainer 6 according to a sixteenth embodiment in which a flange 6.j is formed on the outer peripheral edge.

FIG. 25 is a perspective view of the retainer 6 according to the seventeenth embodiment, which has a cut 6 f ′ communicating the guide hole 6 a with the outside of the outer peripheral edge of the retainer function part 6 d. It is. FIG. 26 is a side sectional view of the retainer 6 fitted to the plunger block 2, which is common to the thirteenth to seventeenth embodiments.

FIG. 27 is a first embodiment of a mode of forming the pressing portion 6b formed on the spring arm 12 in which the pressing portion is formed by bending the spring arm 12 into an S-shape. It is shown in a schematic side view of the object.

FIG. 28 is a schematic side view of a second embodiment of the same embodiment, in which a spring arm 12 is curved in an arc shape to form a pressing portion.

FIG. 29 is a perspective view of a third embodiment of the same embodiment, in which the pressing portion 6b has a curl shape projecting toward the spherical surface 2b.

FIG. 30 is a schematic side view of a fourth embodiment of the same embodiment, in which the panel arm 12 is extended linearly and only the tip is bent to form a pressing portion. FIG. 31 is a perspective view of a fifth embodiment of the same embodiment, in which the contact surface of the pressing portion 6b with the spherical surface 2b is substantially flat.

FIG. 32 is a perspective view of a sixth embodiment of the same embodiment, in which the corresponding contact surface is a concave curved surface.

FIG. 33 is a perspective view of a pressing portion 6b according to the sixth embodiment shown in FIG. 32,

(a) is a similar curved surface for both the contact surface and the back surface with the same thickness for the entire contact portion 6b. (B) is a diagram in which a spherical press concave surface 6j along the spherical surface of the spherical portion 2b is formed only on the contact surface with the spherical portion 2b.

FIG. 34 is a perspective view of a modification of the sixth embodiment, in which the pressing portion 6b is formed in an annular shape.

FIG. 35 shows a seventh embodiment of the same forming mode, in which the corresponding contact surface is a concave curved surface along the latitude line of the spherical portion 2 and is viewed from a cross section orthogonal to the axis of the plunger block 2. FIG. 9 is a perspective view of a case where the curvature is made substantially equal to the curvature of the spherical portion 2b. FIG. 36 is a cross-sectional view taken along a cross section orthogonal to the axis of the plunger block 2 in FIG.

FIG. 37 shows an eighth embodiment of the same form of formation, in which the corresponding contact surface is a concave curved surface along the meridian of the spherical portion 2 b and is viewed in a cross section along the axis of the plunger block 2. FIG. 7 is a perspective view of a lens whose curvature is made substantially equal to the curvature of the spherical portion 2b. Fig. 38 is also a side view.

FIG. 39 is a perspective view of a ninth embodiment of the same embodiment, in which the corresponding contact surface is a concave curved surface and the curvature is larger than the curvature of the spherical portion 2b.

FIG. 40 is also a side view.

FIG. 41 is a perspective view of a tenth embodiment of the same embodiment, in which the pressing portion 6b is bent in a V shape along the diameter of the spherical surface 2b.

FIG. 42 is a sectional view of a section orthogonal to the axis of the plunger block 2.

FIG. 43 shows an eleventh embodiment of the same forming mode, in which the pressing portion 6b is bent in a V-shape along the latitude line of the spherical surface 2b, but one point is formed on the spherical surface 2b. It is a side view of the state which contact | abutted at.

FIG. 44 is a side view of the eleventh embodiment in a state where the spherical surface 2b is in contact with the spherical surface 2b at two points. BEST MODE FOR CARRYING OUT THE INVENTION

The entire swash plate type axial piston unit (as a hydraulic pump or hydraulic motor) shown in Fig. 2 (hereinafter referred to as “axial piston unit”) The configuration will be described. One end surface of the plunger block 12 abuts on the valve plate 18 so that it can slide and rotate freely. The rotating shaft 1 is rotatably supported by bearings 9 and the like. The force penetrates through the core shaft hole 2 a of the plunger block 2 and the center hole of the valve plate 18. The rotary shaft 1 and the plunger block 2 are spline-fitted in the core shaft hole 2a. On the other hand, the rotation shaft Γ is rotatable relative to the valve plate 18. Therefore, when the rotating shaft 1 rotates, the plunger block 2 slides and rotates with respect to the valve plate 18 integrally with the rotating shaft 1 while the valve plate 18 remains fixed.

A plurality of plungers 3 parallel to the rotating shaft 1 are slidably fitted in the plunger block 2 radially about the rotating shaft 1 in a cross-sectional view. A shoe 4 is attached via a ball-and-socket type joint 4 a, and each shoe 4 is pressed against a swash plate 5.

In the radial direction of the rotating shaft 1, a portion of the plunger block 2 closer to the shaft hole 2a than the plunger 3 protrudes toward the swash plate 5, and the protruding portion has a spherical tip end of the rotating shaft core (hereinafter referred to as a "spherical shape"). Part)) forming 2b. The retainer 6 is a generally ring-shaped member having a center hole 6c at the center as shown in FIG. 3, and an inner peripheral edge surrounding the center hole 6c is formed of the spherical portion 2b. It is processed into a curved surface in accordance with the outer surface to form an elastic contact portion 6b. As shown in FIG. 2, the spherical portion 2b is fitted into the central hole 6c of the retainer 6, and the pressing portion 6b of the retainer 6 slides on the outer surface of the spherical portion 2b. It comes into contact freely.

As shown in FIGS. 2 and 3, in the retainer 6, the same number of guide holes 6a as the plungers 3 are formed radially around the center hole 6c (the pressing portion 6b) of the retainer 6. The ball-socket joint 4a between each plunger 3 and each shroud 4 is arranged in each guide hole 6a. The outer diameter of each shoe 4 is larger than the diameter of each guide hole 6a, and the periphery of each guide hole 6a of the retainer 6, which is properly supported on the spherical portion 2b as described above. However, each bush 4 is pressed against the swash plate 5.

Here, it is assumed that the axial piston unit A is used, for example, as a hydraulic motor, and two oil passages for suction and discharge are interposed between the valve plate 18 and a hydraulic pump (not shown). Due to the action of the hydraulic pump, the oil pressure in the suction oil passage becomes high, Low pressure. When high-pressure oil enters the plunger mouth 2 from the hydraulic pump through the suction oil passage and the valve plate 18, the pressure of the high-pressure oil acts on the end face of the base end of the plunger 3, causing the plunger 3 to move. Slide to the slant 5 and press the shoe 4 to the slant 5.

The pressing of the shower 4 against the swash plate 5 generates a component force in a direction orthogonal to the sliding direction of the plunger 3, and this component force turns the plunger block 2 as a rotational force. The rotation of the plunger block 2 causes the rotating shaft 1 to rotate as a motor shaft. Further, with the rotation of the plunger block 2, the high-pressure plunger 3 moves from the top dead center to the bottom dead center, and discharges oil through the valve plate 18 to the low-pressure discharge oil passage. However, the plunger 3 that has been under the low pressure moves from the bottom dead center to the top dead center, and the high pressure oil is sucked from the suction oil passage.

Conversely, when the axial piston unit A is used as a hydraulic pump and, for example, a hydraulic motor (not shown) is provided with a discharge oil passage and a suction oil passage The jaw mouthpiece 2 rotates, and the rotation of the plunger mouthpiece 2 causes each plunger 3 to reciprocate in the direction of the rotation axis 1, and the suction stroke by moving from the bottom dead center to the top dead center, and the top dead center And the discharge stroke by moving to the bottom dead center is repeated, and this is sequentially executed in the plurality of plungers 3. In this way, high-pressure oil generated by the discharge stroke of each plunger 3 is discharged into the discharge oil passage via the valve plate 18, and the high-pressure oil which has become low in the suction stroke is introduced into the cylinder in which the plunger 3 is inserted. Low-pressure oil is sucked from the oil passage.

The plunger 3 during the discharge stroke when the axial piston unit A is used as a hydraulic motor, or the plunger 3 during the suction stroke when the axial piston unit A is used as a hydraulic pump, has a low-pressure side oil passage (the former). In this case, it is a discharge oil passage, and in the latter case, it is a suction oil passage.) The low oil pressure in the inside causes the bow I drawing force to act on the valve plate 18 side. When the plunger 3 moves away from the swash plate 5, the stroke of the plunger 3 becomes unstable, and the suction and discharge of the unit A pressure oil is not performed at the original effective capacity. The pump 4 is hit against the swash plate 5 during the suction stroke when the pump is used as a hydraulic motor, and the discharge stroke when the pump is used as a hydraulic pump. W

Board 5 will be damaged. The retainer 6 presses and holds the shoe 4 against the swash plate 5 so that the shoe 4 does not separate from the slope 5 in this manner. Conventionally, a separate guide member (retainer guide 112 in FIG. 1) is interposed between the plunger block and the retainer, and the plunger block 2 is further moved to the swash plate 5 side and the valve plate 18 side. Various components (panel 11 and other components in Fig. 1) must be prepared to urge the plunger, and the plunger block must be subjected to various processes for its arrangement. Was.

The retainer 6 of the present invention is directly fitted to the tip (spherical portion 2 b) of the rotating shaft of the plunger block 2 formed in a spherical shape, and is squeezed by the urging force generated by the panel elasticity. The hysteresis generated by the force of the panel holding the press-contact of the swash plate 5 and suppressing the unbalanced momentum on the rotating plunger hook 2 prevents the valve plate 1 It is to prevent departure from 8. That is, a plate-shaped retainer function portion 6 d having a guide hole 6 a for guiding and locking each shoe 4, and a center hole 6. The plunger block also has a fitting part for directly fitting to the front end of the rotating shaft core part of the plunger block 2 having a pressing part 6 b on the inner peripheral edge surrounding the plunger block. Since the number of parts and the cost required for pressing the plate and the processing cost of the plunger block can be reduced, assembly becomes easy, and the axial piston unit A can be made compact. is there.

On the other hand, during rotation, an unbalanced moment acts on the plunger block 2 so as to separate from the valve plate 18. Pressing the plunger block 2 against the valve plate 18 in the axial direction as in the prior art compression panel 1 1 1 (Fig. 1) can prevent this detachment. The overall efficiency of the unit (hydraulic pump or hydraulic motor) will be reduced. According to the present invention, by providing the retainer 6 with a fitting portion to the plunger block 2 having the spring resilience, hysteresis is generated by the spring property of the spring 6 due to the reduction of the pressing force on the valve plate 18. Therefore, since the unbalance moment is suppressed to prevent the valve plate 18 from coming off, the axial piston unit A with high overall efficiency can be provided.

Next, various examples of the retainer 6 will be described. The basic structure shown in Figs. 3 and 4 W 01

The retainer 6 is a retainer 6 applied to the axial piston unit A shown in FIG. 2, and is formed by processing a thin plate with a press or the like.

Guide holes 6a are arranged radially around the center of the plunger 3 as many as the number of the plungers 3, and the inner periphery defining the center hole 6c matches the curvature of the surface of the spherical portion 2b of the plunger block 2. It is bent to form the pressing portion 6b. The pressing portion 6b formed of a thin plate has elasticity. The pressing portion 6b is fitted on the spherical portion 2b, and the retainer

When 6 is pushed into the valve plate 18 side, the press-contact portion 6 b is spread out, and the degree of bending increases to generate a restoring force due to elasticity. Energize to.

In this manner, the retainer 6 urges the plunger block 2 toward the swash plate 5, so that each shroud 4 attached to the tip of each plunger 3 inserted into the plunger block 2 also moves to the swash plate 5. Even if the plunger 3 receives the pulling force to the valve plate 18 due to the low pressure action on the plunger 3, the biasing force of the retainer 8 exceeds the pulling force, and the shroud 4 remains pressed against the slant 5 And the plunger 3 stroke is maintained normally.

Further, due to the bending of the pressing portion 6b, the pressing portion 6b functions as a panel, and hysteresis occurs due to friction with the spherical portion 2b, so that the unbalance motor of the plunger block 2 during the rotation described above. Can be suppressed.

The retainer 6 shown in FIG. 5 has a structure in which the outer edge is cut to enhance panel elasticity.

That is, the portion of each guide hole 6a near the press contact portion 6b is extended along the outer edge shape of the press contact portion 6b, and thereby, between the press contact portion 6b and the entire guide hole 6 Thus, a circumferential region having a small constant width d1 as a whole is formed. Further, the outer peripheral end of the retainer 6 is formed in a small circular arc shape with a constant width d2 along the edge shape of the guide hole 6a near the outer peripheral portion. As described above, the retainer 6 shown in FIG. 5 has a reduced rigidity by reducing the area of the plate-shaped portion, and accordingly, the panel constant is reduced (panel elasticity is increased), and a large hysteresis is generated. can do.

The retainer 6 shown in FIG. 6 is formed by cutting out some of the connecting portions 6 e connecting the outer peripheral end of the retainer 6 formed between the adjacent guide holes 6 a and the pressing portion 6 b, That is, W

Several continuous guide holes 6a are connected, and the connecting portion 6e is formed to be smaller than the number of the guide holes 6a to enhance the elasticity. In FIG. 6, the connecting portion 6e is formed in a number that is one third of the number of the guide holes 6a. In the case of this structure, the panel constant can be set variously depending on how many guide holes 6a are open, that is, how many connection portions 6e are formed.

The retainer 6 shown in FIG. 6 forms a constricted portion 6 g at the outer peripheral end of the connecting portion 6 e in FIG. 6 to reduce the rigidity of the outer peripheral end of the connecting portion 6 e, The panel constant is to be reduced. In addition, since the outer peripheral end of the connecting portion 6e is a place where stress tends to concentrate, the constriction also has the effect of dispersing the stress and improving the durability.

The retainer 6 shown in FIGS. 8 and 9 is configured such that each connecting part 6e is bent from the middle part to the pressing part 6b, and is bent to the opposite side of the bending side of the pressing part 6b (the pressing part). If it is assumed that the portion 6b is bent upward, bend it downward), and bend the portion from the outer peripheral end of the retainer 6 through the connecting portions 6e to the tip of the pressing portion 6b. Are doubled to enhance the panel elasticity.

Further, as shown in FIG. 10, even when the connecting portion 6e is bent as shown in FIGS. 8 and 9, similarly to the case of the retainer 6 in FIG. Due to the effective force between 6 a and the center hole 6 c, the entire circumference has the same small width d 1, and the effective width between each guide hole 6 a and the outer peripheral end of the retainer 6 is the same small width The rigidity may be reduced by forming an arc shape of d2, and the panel constant may be further reduced. Figures 11 to 13 show the ball of plunger block 2 separately from the retainer! A configuration is shown in which a fitting member for the dog portion 2b is provided, and the fitting member has a function of urging the retainer toward the swash plate 5.

The retainer configuration shown in FIGS. 11 and 12 will be described. The ring-shaped retainer 16 has the same number of guide holes 6a as the number of the plungers 3 and radially around the center hole 16b for the passage of the spherical portion 2b. The force with 16a is arranged. The inner peripheral edge is not bent and is entirely flat.

On the other hand, the spring member 1 と to be fitted to the plunger block 2 has an annular fitting ring 1 Ί a fitted to the spherical portion 2 b of the plunger block 2 (retainers 1 and 6). The inner diameter defining the central hole 16b is larger than the outer diameter of the fitting ring 17a. When the fitting ring 17a is arranged in a circular shape in a plan view, as shown in FIG. 11, the fitting ring 17a is centered on the fitting ring 17a as shown in FIG. It comprises a plurality of arms 17b which extend outward substantially in a radial manner, and each arm 17b is elastically curved in an arcuate shape as shown in FIG. .

In the vicinity of the outer peripheral edge of the retainer 16, notches 16 c and / or 揷 insertion holes 16 d are formed in the same number as the arms 17 b of the spring member 17 in total. 16c and / or 揷 Insert the tip of each arm 17b into each of the insertion holes 16d, and fit the fitting ring 17a of the spring member 17 to the center of the retainer 16. Concentrically arranged in hole 16b. Each arm 17 b only has a protrusion 17 c for retaining, and if it is inserted into each notch 16 c or insertion hole 16 d, it is naturally resilient by the protrusion 17 c due to its elasticity. It is in a state of being hooked to the tener 16. That is, there is no need to use a special member for connecting the retainer 16 to the spring member 17, and assembly is easy.

In addition, each of the arms 17 b incorporated into the retainer 16 in this manner is connected to the fitting ring 1 Ί a disposed further inside than the inner peripheral edge of the retainer 16 from the retainer 16. It extends up to the notch 16c or the opening 16h near the outer peripheral end, and has a length sufficient to obtain sufficient elasticity.

With the ball-and-socket joints 4a arranged in the guide holes 16a of the retainer 16 and the fitting ring 17a of the spring member 17 incorporated in the retainer 16 as described above, When the inner peripheral portion is pressed against the outer surface of the spherical portion 2b of the plunger block 2, the retainer 16 is urged to the swash plate 5 by the elastic force of the arm 17b, and the retainer 16 is pressed. The entire shoe 4 is pressed and held on the swash plate 5.

The inner peripheral surface of the fitting ring 17a that contacts the outer surface of the spherical portion 2b of the plunger block 2 may be linear in cross section as shown in FIG. As shown in the figure, the spherical portion 2b may be formed into a spherical shape having an arcuate cross section in accordance with the spherical shape. The fitting ring 17a in Fig. 13 increases the contact area with the spherical portion 2b, reduces the Hertzian surface pressure, and increases the durability of the fitting ring 17a and the spherical portion 2b. It will be.

Each of the above-described retainers 6 shown in FIGS. 2 to 10 has a constant plate thickness throughout. That is, the peripheral portion of each guide hole 6a that presses the shoe 4 against the swash plate also has the same thickness as the pressing portion 6b. On the other hand, in FIGS. 11 and 12, retainers 16 and spring members 17 having different thicknesses from each other can be used. For example, by forming the retainer 16 from a slightly thicker plate-like member, its rigidity is ensured and the shoe 4 is securely restrained, while the spring member 17 is formed from a thin plate, It is possible to apply to the arm 17 the spring elasticity necessary to generate the urging force for surely pressing the swash plate 5 and the hysteresis for preventing the plunger block 2 from separating from the valve plate 18. .

As described above, the retainer is fitted to the spherical portion 2b of the plunger block 2 so as to contact the spherical portion 2b of the plunger block 2 over the entire circumference (that is, the pressing portion 6b of the retainer 6; FIG. 11). In these examples, the fitting ring 1a) of the spring member 17 is formed. Next, from the viewpoint of increasing the elasticity of the panel portion as the fitting portion abutting on the spherical portion 2b and stabilizing the support of the fitting portion on the spherical portion 2b, the fitting portion is divided. O Various embodiments of the retainer 6 adopting the configuration of

FIGS. 14 and 15 show some additional guides for the retainer 6 of FIGS. 8 and 9 (which can also be used for the retainer 6 shown in FIG. 10). A notch 6ί communicating between the hole 6a and the center hole 6c is formed to divide the pressing portion 6b to increase its elasticity, that is, to reduce the panel constant. In addition, the structure in which the cut 6 mm is formed may be adopted for the retainer 6 (that is, the connecting portion 6 e which is not bent in the middle) in each of the modes shown in FIGS. 3 to 7. In each of the retainers 6 shown in FIGS. 6 and 7, one notch 6f is formed from a plurality of connected guide holes 6a to the center hole 6c.

In the retainer 6 shown in FIG. 14, a notch 6 f is formed from each of three equally spaced guide holes 6 a to a central hole 6 c to divide the pressing portion 6 b into three equal parts. By contacting the pressing portion 6b in this state with the spherical portion 2b, the retainer 6 is supported at a point on the spherical portion 2b, and the support of the retainer 6 also increases stability. . In order to make the hysteresis generated by the spring elasticity of the pressing portion 6b function in all directions, it is effective to form the pressing portion 6b separated at least in three directions as described above. The retainer 6 shown in FIG. 15 has a cut 6 mm between each guide hole 6a and the center hole 6c, and equally divides the press contact portion 6b into the same number as the guide holes 6a. ing. As described above, by appropriately setting the number of cuts 6 mm, the spring constant (elasticity) of the pressing portion 6b can be appropriately adjusted.

From the standpoint of simply reducing the spring constant of the retainer 6, a cut may be made from the outer end of the appropriate guide hole 6a to the outer peripheral end of the retainer 6 (see FIG. See f '.)

The retainer 6 shown in FIGS. 16 to 18 does not bend the inner peripheral edge defining the center hole 6c around the entire periphery to form the pressing portion 6b, but tongue at several places. The piece 11 extends toward the center of the retainer 6 and is bent to provide panel elasticity, thereby forming the pressing portion 6b. Therefore, the pressing portion 6b of each tongue piece 11 comes into contact with the spherical portion 2b, and the retainer 6 is supported at a plurality of positions with respect to the spherical portion 2b and is stabilized. In addition, as will be described later, a retainer function unit is provided in comparison with a retainer 6 which provides a pressing portion 6 b by forming a vane 12 extending from the outer periphery to the center of the retainer 6. 6 d can be held in a circular shape, and rigidity can be secured.

The retainer 6 shown in FIG. 16 has three tongue pieces 11 having the pressing portions 6b at equal intervals on the inner peripheral edge of the retainer 6. In FIG. 17, a pair of adjacent retainers 6 are formed at three locations at equal intervals, for a total of six tongues 11. In FIG. 18, the same number of tongue pieces 11 as the guide holes 6 a are formed at regular intervals. FIGS. 16 to 18 show that the retainer 6 shown in FIGS. 14 and 15 has the spring constant of the pressing portion 6b and the bearing stability set appropriately for the number of cuts 6f. The retainer 6 also appropriately sets the spring constant and the bearing stability by the number of the tongue pieces 11 formed.

FIGS. 19 to 26 show a panel arm 12 having a pressing portion 6 b at its tip for pressing against the spherical portion 2 b by its panel elastic force. Various modes of a retainer 6 configured to extend centripetally from a position (outer peripheral edge in this embodiment) closer to the outer peripheral edge than the inner peripheral edge of d are shown. In these, sufficient spring elasticity is secured by the length of the spring arm 12 from the outer peripheral end of the retainer 6 to the spherical portion 2b. The retainer 6 shown in FIG. 19 is formed by folding back a flat plate of the retainer 6 so as to extend from an appropriate position on the outer peripheral end toward the center of the retainer 6, and integrally form a spring arm. 12 are formed, and the front end thereof is positioned closer to the center than the inner peripheral edge of the retainer 6 to form a pressing contact portion 6b.

In the retainer 6 shown in FIG. 20, the guide hole 6a and the center hole 6c are communicated with each other through the cut 6f in order to increase the spring elasticity of the retainer 6 itself. The guide holes 6a communicating with the center c through the cuts 6f may be selected instead of all. A connecting portion 6 e that separates adjacent guide holes 6 a (in this case, the connecting portion 6 e simply extends centrifugally from the outer peripheral edge of the retainer 6 and has an inner peripheral edge of the retainer 6 at its tip. Some of are curved in the shape of an arch to form a spring arm 12, the tip of which extends closer to the center than the other uncurved connecting portion 6 e. The pressing portion 6b is used.

In FIG. 20, three panel arms 12 are formed at equal intervals. In this case, too, by appropriately setting the number of spring arms 12 and the locations where the spring arms 12 are formed, the swash plate 5 is formed. The biasing force and bearing stability can be adjusted.

FIGS. 21 to 25 show a retainer 6 in which, as shown in FIG. 20, three of the connecting portions 6 e that are equally spaced are applied as spring arms 12. However, in these cases, the number of panel arms 12 and the locations where the panel arms 12 are formed may be appropriately set.

The retainer 6 shown in FIG. 21 has two guide holes for sandwiching the spring arm 12 at the base end (base portion) of each spring arm 12 of the retainer 6 shown in FIG. A part of each of them is expanded to form a constricted part 6 g, and the retainer 6 in FIG. 22 is provided along the outer edges of the two guide holes 6 a sandwiching the spring arm 12. A constriction 6 h near the base end of the spring arm 12 is provided on the outer peripheral edge of the corner 6. These constrictions 6 g and 6 h have the effect of avoiding concentration of stress at the base end of the spring arm 12 and enhancing the elasticity of the spring arm 12 (reducing the panel constant).

It should be noted that as the spring elasticity of the spring arms 12 is increased, the rigidity of the retainer 6 decreases, and the restraining force of the shoe 4 may be reduced. In the retainer 6 shown in FIG. 22, as shown in FIGS. 22 and 23, the surface facing the shroud 4 in the periphery of the guide hole 6 a not adjacent to the spring arm 12. In the case of An appropriate number of projections 6 i for projecting are provided. The projection 6 i abuts on the surface of the shoe 4 when the retainer 6 is normally disposed, and the point-like intensive pressing force applied to the shoe 6 reliably and stably holds the shoe 4. to bound. '

As another example of a structure for increasing the rigidity of the retainer 6 to secure the binding force of the shroud 4 while increasing the spring elasticity of the panel arm 1 (while reducing the panel constant), FIG. As shown in FIG. 1, a flange 6 j is formed by bending the entire outer peripheral edge of the retainer 6 having a constriction 6 h at the base end of each panel arm 12 to one side.

In FIG. 25, in order to improve the spring elasticity of the retainer 6 itself, a notch 6 f communicating with the guide hole 6 a and the center hole 6 c is provided in FIG. A notch 6 ′ ′ is formed from the guide hole 6 a not adjacent to the hole 12 to the outer peripheral edge of the retainer 6.

In the retainer 6 shown in FIGS. 8, 14 and 15, the inner peripheral edge surrounding the central hole 6c of the retainer function part 6d itself is the pressing contact part 6b. On the other hand, the pressing portion 6b at the tip of the spring arm 12 of the retainer 6 in FIG. 20 to FIG. 25 is different from the inner peripheral edge of the retainer function portion 6d, As shown in FIG. 26, the retainer function part 6 d is located slightly closer to the center of the retainer 6 than the inner peripheral edge of the retainer function part 6 d. Originally, only these contact portions 6 b are pressed against the outer surface of the spherical portion 2 a, but the axial piston unit

If the fluctuation of the behavior of the plunger block 2 is large during the operation of A, the retainer 6 may be shifted toward the valve 18 against the urging force of the spring arm 12. However, in this case, as shown by the virtual fountain, the inner peripheral edge spherical portion 2a of the retainer 6 has a larger diameter at a position closer to the valve plate 18 than the portion where the spherical portion 2a is pressed to the original pressed portion 6b. It does not come into contact with the outer surface of the part and does not move the retainer 6 force closer to the valve plate 18. That is, the inner peripheral edge of the retainer 6 functions as a stop of the retainer 6 on the spherical portion 2a, and the retainer 6 and the plunger block which are extremely displaced toward the retainer 6 force valve plate 18 are provided. 2. Damage to the plunger 3, ball / socket joint 4a, and shoe 4, etc. can be prevented.

As described above, in addition to increasing the elasticity of the spring arm 12 by performing processing such as cutting and constriction on the retainer 6, it is also possible to extend the groove from the base end to the pressing contact portion 6 b at a predetermined position. The length of the spring arm 12 obtained by bending etc. should be adjusted so that it fits the bending to obtain an appropriate spring force when pressed properly against the pressing part 6 b and the force spherical part 2 b. It can be adjusted.

Next, the manner of bending the panel arm 12 and the manner of forming the pressing portion 6b at the tip thereof will be described with reference to FIGS. 27 to 44. FIG. These embodiments described below may be applied to any of the panel arms 12 of the retainer 6 in various embodiments shown in FIGS. 19 to 26. Further, these aspects of the spring arm 12 may be applied to a tongue piece 11 formed on the inner peripheral edge of the retainer 6 as shown in FIGS. 16 to 18.

The spring arm 12 shown in FIG. 27 has an S-shape, that is, it is bent to one side and then to the other before reaching the pressing portion 6 b at the tip, and the elasticity of the spring arm 12 itself is increased. Is increasing. Spring arm in Fig. 28; Reference numeral 2 is curved to one side only in the portion where the pressing portion 6b at the tip is formed. At the extreme, as shown in FIG. 29, the spring arm 12 may be curved in a force shape to form the pressing portion 6b. The pressing portions 6b of any of the spring arms 12 shown in FIGS. 27 to 29 are also convex with respect to the outer curved surface of the spherical portion 2b, that is, warped to the opposite side, and are extremely small. The contact is made at the contact point, and the urging force due to the panel elasticity is effectively applied to the spherical portion 2b.

The spring arm 12 shown in FIGS. 30 and 31 forms a flat pressing portion 6b by a simple bending process. When the pressing portion 6b is pressed against the spherical portion 2b, the pressing portion 6b is pushed up with the bent portion of the spring arm 12 as a fulcrum, and the panel arm 12 is bent by this, and this bending is performed via the pressing portion 6b. The urging force and hysteresis generated by the above are applied to the spherical portion 2b.

In particular, the panel arm 12 shown in FIG. 30 extends linearly until it reaches the pressing portion 6b, and only the pressing portion 6b at the tip is formed by bending, and has a simple structure. The number of points such as bending work is small.

The pressing portion 6b shown in FIG. 32 is curved, and the contact surface with the spherical portion 2b is a concave curved surface. FIG. 33 shows an example of such a form of the pressing portion 6b.

As shown in (a), the contact portion 6b may have a uniform thickness, and the contact surface and the back surface may be curved with the same curvature, or as shown in FIG. 33 (b). In particular, the concave surface 6 j along the spherical surface is applied only to the abutting surface of the spherical portion 2 b, particularly only at the abutting portion on the spherical surface.

Z 3 It may be formed with a tress or the like.

Further, as shown in FIG. 34, the pressing portion 6b may be formed in an annular shape so that the panel constant is further reduced so that effective hysteresis can be imparted to the plunger hook 2.

In a sectional view of the spherical portion 2b when divided by a plane along the axis of the plunger block 2 (the extending direction of the rotating shaft 1), FIGS. The arcuate line of the outer circumference of the spherical portion 2b when divided on a plane perpendicular to the axis (hereinafter, this line is a sphere)! ), The contact portion 6b of FIGS. 37 and 38 has an arcuate line around the spherical portion 2b (hereinafter, this line is referred to as a spherical shape). It is concavely curved at approximately the same curvature along the "meridian" of part 2. These concave curved surfaces can be formed by press working or the like.

As described above, the contact area 6b of FIGS. 35 to 38 has a large contact area with the spherical part 2b, and the Hertzian surface pressure applied between them is reduced. This improves the durability of the retainer 6 and the plunger jaw 2.

FIGS. 37 and 38 show a panel arm 1 having a pressing contact portion 6b concavely curved along the meridian of the spherical portion 2b at substantially the same curvature as the spherical portion 2b, as shown in FIG. 2, showing that the panel arm 1 2 is also curved up to the bent portion to form the pressing portion 6b.

The pressing portion 6b in FIGS. 39 and 40 is also concavely curved along the meridian of the spherical portion 2b, as in FIGS. 37 and 38. Is larger than the curvature of the meridian and the contact area is smaller than that in FIG. Adjust the contact area appropriately while observing the effect of reducing the Hertzian surface pressure and the effect of generating hysteresis.

As shown best in FIG. 42, the pressing portion 6b shown in FIGS. 41 and 42 has a spherical portion 2a when divided by a plane perpendicular to the axis of the plunger lock 2. In the cross-sectional view of FIG. 2, the portion is bent into a V-shape, and two partial force contacts are made to the latitude line of the spherical portion 2a symmetrically with respect to the bent portion of the V-shape. As described above, the contact surface with the spherical portion 2b is provided in two in the latitude direction of the spherical portion 2b by one pressing portion 6b, The retainer 6 can be stably supported on the spherical portion 2b without increasing the number of the spring arms 12.

Similarly, the pressing portion 6b in FIGS. 43 and 44 is bent in a V shape, but in this case, the bending direction is the same as that in the case of FIGS. 41 and 42. Of the two parts which are orthogonal to each other and are symmetrical with respect to the meridian of the spherical part 2a with respect to the V-shaped bent part of the pressing part 6b, at the beginning of fitting to the spherical part 2a, As shown in FIG. 43, only one of the contact portions comes into contact with the spherical portion 2a, and the retainer 6 is still pushed into the valve 扳 18 side, and finally, as shown in FIG. The two symmetrical portions contact the meridian of the spherical portion 2b across the V-shaped bent portion of 6b, and stably support the retainer 6 on the spherical portion 2a. Industrial applicability

The present invention provides a highly efficient HST (hydraulic type) with a low cost and simple structure that restrains the plunger swash plate and prevents the plunger block from detaching from the valve plate. Hydraulic pump with a continuously variable transmission mechanism. It has the potential to be used as a swash plate type axial piston hydraulic unit used as a hydraulic motor.

Claims

The scope of the claims

1. A plunger (3) is mounted inside the plunger block along the axis of rotation of the plunger block (2) which is rotated as a hydraulic pump or a hydraulic motor.

In (6), a swash plate type axial piston type hydraulic system in which a shroud (4) integrally provided on the plunger head projecting from the plunger block is restrained against the swash plate (5) The retainer has a plate-like retainer function part (6d) forming a guide hole (6a) for guiding and restraining the shoe, and a retainer for the plunger block. A swash plate type axial piston type hydraulic unit, wherein a swash plate type axial piston type hydraulic unit is provided with a fitting portion having panel elasticity for direct fitting.

2. In the retainer (6), a central hole into which the tip (2b) of the rotation axis of the plunger block (2) is inserted into the center of the plate-shaped retainer function portion (6d).

(6c) is formed, and a pressing portion (6b) having panel elasticity and pressing against the tip end of the rotary shaft core is disposed to face the center hole. 2. The swash plate type axial piston type hydraulic unit according to claim 1, wherein said press contact portion is a fitting portion to be fitted to said plunger port.

3. A part of the retainer function part (6d) between the adjacent guide holes (6a) in the retainer (6), and a part of the guide hole (6a) is expanded. (6 g). The swash plate type axial piston hydraulic unit according to claim 1, wherein

4. In the retainer function part (6d) of the retainer (6), a projection (6i) is formed in the vicinity of the guide hole (6a) to be in contact with the shoe (4). The oblique axial biston-type hydraulic unit according to claim 1, characterized in that:

5. A retainer function part (6d) of the retainer (6) is formed in a disk shape, and its outer peripheral edge is bent over the entire circumference to form a flange part (6j). The swash plate type axial piston hydraulic unit according to claim 1.

6. The retainer (6) is provided with a notch (6f) connecting at least one of the guide holes (6a) and the center hole (6c). 3. The swash plate type axial piston hydraulic unit according to claim 2.

7. The guide holes (6a) are formed at equal intervals on at least three sides around the center hole (6c), and the pressing portions (6) on the periphery of the center hole are formed at the cuts (6f). 7. The swash plate type axial piston type hydraulic unit according to claim 6, wherein b) is divided into three parts.

8. In the retainer (6), a notch (6Γ) is formed to communicate the guide hole (6a) with the outside of the outer peripheral edge of the retainer. 3. The swash plate type axial piston hydraulic unit according to item 2.

9. In the retainer (6), the pressing portion (6b) bends an inner peripheral edge forming a center hole (6c) of the retainer function portion (6d) into a panel shape. 3. The swash plate type axial piston type hydraulic unit according to claim 2, wherein the hydraulic unit is formed of:

10. In the retainer (6), the center hole (6c) is formed at an inner peripheral edge of the retainer function part (6d), and the pressing part (6b) is 3. The swash plate type axial piston hydraulic unit according to claim 2, wherein the retainer function portion is formed in a portion (11-12) different from an inner peripheral edge.

11. The oblique connection according to claim 10, wherein the number of the pressing portions (11) in the retainer (6) is not less than three and not more than the number of plungers (3). Type axial piston type hydraulic unit.

1 2. Connect the tip (2b) of the rotation axis of the plunger block to the retainer (6). When the fitting depth of the tip of the rotating shaft core is shallow when fitting into the fitting portion of

The swash plate type according to claim 10, wherein the swash plate is in contact with only the inner peripheral edge of the retainer function portion (6d) by being fitted more deeply. Axial piston type hydraulic unit.

13. In the retainer (6), a part of the retainer function part (6d) is formed as a part (11, 12) extending toward the center, and this part is bent to form the pusher having panel elasticity. 11. The swash plate type axial piston type hydraulic unit according to claim 10, wherein the contact portion (6b) is formed.

14. A part (11) of the inner peripheral edge of the retainer function part (6d) is bent and extended so as to have panel elasticity, thereby forming a pressing contact part (6b). 14. The oblique axial piston type hydraulic unit according to claim 13, wherein:

15. In the retainer function part (6d), an arm-shaped part (12) is formed from at least a position on the outer peripheral side of the inner peripheral edge toward the center part, and this is bent appropriately to have a spring elasticity. 14. The oblique axial piston type hydraulic unit according to claim 13, wherein the pressing portion (6b) is formed.

16. The arm according to claim 15, wherein the arm-shaped portion (12) extends from the outer peripheral edge of the retainer function portion (6d) to the center hole (6c). The described swash plate type axial piston hydraulic unit.

17. The swash plate according to claim 15, wherein the arm-shaped portion (12) is bent in a substantially S-shape to form the pressing portion (6b) at a tip end thereof. Type axial piston type hydraulic unit.

18. The swash plate according to claim 15, wherein said arm-shaped portion (12) is bent in a substantially arc shape to form said pressing contact portion (6b) at a tip end thereof. Type Aki Charactor-type hydraulic unit.

1 9. The arm-shaped portion (12) comprises a portion between the adjacent guide holes (6a) in the retainer (6). Oblique axial piston type hydraulic unit.

20. A constriction (6 g) formed by expanding a part of the guide hole (6a) at a base end of the arm-shaped portion (12). The oblique axial piston type hydraulic unit described in the item.

2 1. The arm-shaped portion (11) extends substantially linearly, and only the tip portion is bent to form the pressing portion (6b). The swash plate type axial piston hydraulic unit according to item 15.

22. The contact surface of the pressing portion (6b) of the retainer (6) is substantially flat with respect to the curved rotating shaft core tip portion (2b) of the plunger block (2). The swash plate type axial piston type hydraulic unit according to claim 2, characterized in that:

23. The contact surface of the press contact portion (6b) of the retainer (6) has a substantially concave curved surface with respect to the curved rotary shaft center end portion (2b) of the plunger block (2). 3. The swash plate type axial piston type hydraulic unit according to claim 2, wherein the curvature is substantially matched with the curvature of a curved surface of a tip portion of a rotation axis of the plunger hook. .

2 4. The curvature of the contact surface of the pressing portion (6b) is determined by the rotation axis of the plunger block when viewed in a cross section along the axis of the rotation axis of the plunger block (2b). 4. The oblique axial piston type hydraulic unit according to claim 3, wherein a curvature of the curved surface of the distal end portion substantially coincides with a curvature of the curved surface.

25. The curvature of the contact surface of the pressing portion (6b) is such that when viewed in a cross section orthogonal to the axis of the rotating shaft tip (2b) of the plunger block, the rotating shaft tip of the plunger block. 24. The swash plate type axial biston hydraulic unit according to claim 23, wherein a curvature of the swash plate type axial unit substantially coincides with a curvature of the curved surface.

26. The abutment surface of the pressing portion (6b) of the retainer (6) is a concave curved surface with respect to the curved rotating shaft core tip (2b) of the plunger block (2). 3. The swash plate type axial piston type hydraulic unit according to claim 2, wherein the curvature is larger than the curvature of a curved surface of a tip portion of a rotation axis of the plunger block.

27. The curvature of the contact surface of the pressing portion (6b) is determined by the cross-section along the axis of the rotating shaft tip (2b) of the plunger block. 27. The swash plate type axial piston type hydraulic unit according to claim 26, wherein the curvature is larger than the curvature of the curved surface.

28. The curvature of the contact surface of the pressing portion (6b) is such that when viewed in a cross section orthogonal to the axis of the rotating shaft tip (2b) of the plunger block, the rotating shaft tip of the plunger block. Claim 2 wherein the curvature of the curved surface is larger than the curvature of the curved surface.

The swash plate type axial biston hydraulic unit according to item 6.

29. The contact surface of the pressing portion (6b) of the retainer (6) is a substantially convex curved surface with respect to the curved rotary shaft core tip (2b) of the plunger block (2). 3. The swash plate type axial biston hydraulic unit according to claim 2, wherein:

30. The push-contact portion (6b) of the retainer (6) is bent substantially in a V-shape with respect to the curved tip end (2b) of the rotating shaft of the plunger block (2) at two points. At 3. The oblique axial piston type hydraulic unit according to claim 2, wherein the hydraulic unit is in contact with the hydraulic unit. ·

3 1. The pressing portion (6b) is bent substantially in a V-shape when viewed in a cross-section along the axis of the tip (2b) of the axis of rotation of the plunger block. 31. A swash plate type axial piston type hydraulic unit according to item 30.

32. Depending on the fitting depth of the tip (2b) of the rotating shaft core of the plunger block into the pushing portion (6b), the contact between the pushing portion and the rotating shaft center selecting portion of the plunger block is made. 32. The oblique axial piston hydraulic unit according to claim 31, wherein the number of contacts is changed.

33. The press contact portion (6b) is bent substantially in a V-shape when viewed in a cross section orthogonal to the axis of the tip end portion (2b) of the rotation axis of the plunger block. 31. The oblique axial piston hydraulic unit according to item 30.

34. The retainer (16), wherein a pressing portion (17a) made of a member different from a member forming a retainer function portion of the retainer (16) is connected to the retainer. 3. The swash plate type axial piston type hydraulic unit according to claim 2.

3 5. The pressing portion (17a) is formed integrally with one end of the arm member (17), and the other end of the arm member is connected to the retainer (16). 35. The swash plate type axial piston hydraulic unit according to claim 34, wherein the swash plate type axial piston type hydraulic unit is fitted in the notch (16c) or the hole (16d) formed in the swash plate.

36. In the retainer (16), the notch (16c) or the hole (16d) is formed at a position closer to the outer peripheral edge than the guide hole (16a) of the retainer (16). 36. The swash plate type axial piston type hydraulic unit according to claim 35, wherein the hydraulic unit is formed by:

37. The pressing surface of the pressing portion (17a) with respect to the plunger block is formed in a curved shape in accordance with the curved surface of the tip end portion (2b) of the rotating shaft of the plunger block (2). The swash plate type according to claim 34, wherein:

Ton type hydraulic unit.