JP2002031209A - Hydraulic device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic device capable of easily assembling a second thrust/radial bearing and a first thrust/radial bearing by pressing the second thrust/radial bearing against the first thrust/radial bearing side. SOLUTION: When a holder 14 is fastened to a cover part 13 through a bolt B, the stepped bottom part of a bearing housing hole 20 presses the input side surface of a cylinder block 25 through an outer ring 16b, an inner ring 16a and a sleeve 21, and the output side surface of the cylinder block 25 presses a locking flange 15a. The stepped part 15b presses the stepped bottom surface of a diameter enlarged part 38b through an inner ring 41a and an outer ring 41b. The side surface of a stepped part 38d is allowed to abut on and locked on the input side surface of a diameter contracted part 12b through an inner ring 45a, an outer ring 45b, a sleeve 44, and an outer ring 17b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a hydraulic device which can be widely used in various industrial fields such as industrial machines and vehicles.

[0002]

2. Description of the Related Art Conventionally, as a hydraulic device, there is a hydraulic device having a case for covering parts such as a cylinder block, such as a swash plate type hydraulic pump or a swash plate type hydraulic motor. The case of such a hydraulic device includes a case body having a bottom and having one end opened, and a lid member closing the opening. A shaft is inserted through the lid member and the bottom of the case body, and both ends of the coaxial shaft are supported by the lid member and the case body bottom via bearings. In the case,
Parts such as a cylinder block are attached to the shaft.

[0003]

SUMMARY OF THE INVENTION The present invention relates to a hydraulic device for supporting a shaft as described above with a bearing, and more particularly, to a hydraulic device for a first thrust / radial dual purpose and a second thrust / radial dual purpose bearing. In the hydraulic device supporting the shaft, by pressing the second thrust / radial dual-purpose bearing toward the first thrust / radial dual-purpose bearing,
The second thrust / radial combined use bearing and the first thrust
It is an object of the present invention to provide a hydraulic device capable of easily assembling a radial dual-purpose bearing.

[0004]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention is directed to a hydraulic apparatus having a cylinder block which accommodates a plunger disposed parallel to an axis and is rotatably supported. A cylinder block engaging portion is provided on one side of the shaft, and a portion which comes into contact with the first thrust / radial dual-purpose bearing provided on the cylinder block engaging portion side is provided coaxially, and the coaxial receiver is provided on the anti-contact portion side. The cylinder block is pressed and fixed to the cylinder block locking portion by pressing the second thrust / radial bearing provided on the side opposite to the cylinder block locking portion against the cylinder block side. That is the gist.

Therefore, in the first aspect of the present invention, when the second thrust / radial bearing is pressed against the cylinder block during assembly, the cylinder block engages with the cylinder block engaging portion provided on the shaft. Press. Then, a portion that comes into contact with the first thrust / radial dual-purpose bearing provided on the shaft presses the first thrust / radial dual-purpose bearing. Then, the first thrust / radial bearing is locked at a portion where the coaxial bearing is locked on the side opposite to the contact portion.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a hydraulic stepless transmission will be described in detail with reference to FIGS.

As shown in FIGS. 1 to 4, a case 11 of a hydraulic continuously variable transmission T is fixed to a substantially cylindrical main body case 12 having an open side and an opening of the main body case 12. And a lid 13. A holder 14 is inserted and fixed in a through hole 13 a provided in the lid 13, and a shim S is interposed between the flange 14 a of the holder 14 and the input side of the lid 13 as shown in FIG. Have been. The holder 14 is fastened and fixed to the lid 13 by screwing the bolt B into the lid 13 via the flange 14a.

The input side of the input shaft 15 of the hydraulic continuously variable transmission T is rotatably supported by a holder 14 via a conical roller bearing 16, and the output side is provided on the output side in the main body case 12. It is rotatably supported via a conical roller bearing 41 on the inner peripheral surface of the cylindrical yoke 38, and is a PTO shaft. In the present embodiment, the input shaft 15 corresponds to a shaft, and the conical roller bearing 16 corresponds to a second thrust / radial bearing. The yoke 38 is rotatably supported on the output side of the main body case 12 via the radial bearing 17.

The holder 14 has a through hole 14b through which the input shaft 15 passes. The input side of the through hole 14b is enlarged in diameter to form a seal member storage hole 18, and a seal member 19 is disposed in the seal member storage hole 18. The output side of the through hole 14b is also enlarged in diameter to form a bearing housing hole 20. The inner ring 16a of the conical roller bearing 16 is externally fitted and fixed to the input shaft 15, and the outer ring 16b is abutted and fixed to the stepped bottom surface and the peripheral surface of the enlarged diameter of the bearing housing hole 20.

A sleeve 21 is externally fitted and fixed to the input shaft 15 near the output side of the inner ring 16a.
The first input side surface is in contact with the inner ring 16a. The output side surface of the sleeve 21 is in contact with the input side surface of a cylinder block 25 described later. A bearing mounting step 22 (see FIG. 3) having a diameter larger than that of the bearing housing hole 20 is formed in the opening of the bearing housing hole 20, and a radial bearing 23 is mounted on the bearing mounting step 22. I have.

The radial bearing 23 has an outer ring 23a.
And an inner ring 23b. The outer ring 23a is fixedly abutted on the bottom surface and the peripheral surface of the stepped portion of the bearing mounting step 22 whose diameter is increased. As shown in FIG.
Is arranged so that its axis is inclined at a fixed angle with respect to the axis O of the cylinder block 25 described later, and its inner ring 23b slides the first switching valve 56 described later in the direction of the axis O at a predetermined timing. The cam has been. The output side surface of the inner ring 23b is a cam surface 58.

The hydraulic pump P includes an input shaft 15 and a cylinder block 25 provided integrally with the input shaft 15.
And a plurality of plungers 26 slidably disposed on the cylinder block 25, and a cradle 28 including a swash plate surface 27 that comes into contact with the plungers 26.

The cradle 28 is arranged on the outer periphery near the output end of the holder 14, and is attached to the lid 13. The cradle 28 can be tilted around a trunnion axis TR1 (see FIG. 3) orthogonal to the axis O of the cylinder block 25. On the input side of the cylinder block 25, the cylinder block 25 is spline-coupled to the input shaft 15. An output side surface of the cylinder block 25 is provided with a locking flange 15 as a cylinder block locking portion provided on the outer periphery of the input shaft 15.
a. In the cylinder block 25, a plurality of cylinder holes 29 are annularly arranged around the center of rotation, and extend in parallel with the axis O. Same cylinder hole 29
Has an opening formed on the input side. Each cylinder hole 29
, The plunger 26 is slidably disposed.

A steel ball 26a is rotatably fitted to the tip of the plunger 26.
a and a swash plate surface 27 via a shoe 30 to which a steel ball 26a is attached. The swash plate surface 27 in the inclined state reciprocates the plunger 26 with the rotation of the cylinder block 25, and gives an effect of a suction and discharge stroke.

The hydraulic motor M is connected to the cylinder block 2
5 includes a plurality of plungers 36 slidably disposed therein and a substantially trumpet-shaped yoke 38 having a rotating swash plate surface 37 that comes into contact with the plungers 36.

As shown in FIG. 4, on the inner periphery of the yoke 38, there are provided three enlarged diameter portions 38a, 38b and 38c whose diameters increase in order from the output side to the input side. A seal member 40 is disposed on the enlarged diameter portion 38a,
A conical roller bearing 41 is disposed on the enlarged diameter portion 38b.
The inner ring 41a of the conical roller bearing 41 is externally fitted and fixed to the input shaft 15, and its input side surface is in contact with a stepped portion 15b whose outer periphery of the input shaft 15 is reduced in diameter. In addition, conical roller bearing 4
The first outer ring 41b is fixedly abutted on the stepped bottom surface and the peripheral surface of the enlarged diameter portion 38b.

In the present embodiment, the conical roller bearing 41 corresponds to a first thrust / radial bearing, and the portion of the yoke 38 where the enlarged diameter portion 38b is formed is the first thrust / radial bearing.
This corresponds to a portion where the thrust / radial dual-purpose bearing is locked on the anti-contact portion side. In addition, the step 15b of the input shaft 15 corresponds to a portion that comes into contact with the first thrust / radial bearing.

In this embodiment, a hydraulic device is constituted by the input shaft 15, the cylinder block 25, the plungers 26 and 36, the conical roller bearings 16 and 41, the yoke 38 and the like.

A radial bearing 42 is provided on the enlarged diameter portion 38c.
Is arranged. The radial bearing 42 includes an outer ring 42a and an inner ring 42b, and the outer ring 42a is fixedly abutted on the stepped bottom surface and the peripheral surface of the enlarged diameter portion 38c. As shown in FIG.
2 is disposed so that its axis is inclined at a fixed angle with respect to the axis O of the cylinder block 25,
b indicates that the second switching valve 66 to be described later is moved to the axis O at a predetermined timing.
It is a cam for sliding in the direction. The inner ring 4
The input side surface of 2b is a cam surface 68.

A through-hole 12a is formed in the output side of the main body case 12, and a reduced-diameter portion 12b whose inner circumference is reduced in diameter is provided at the output end of the through-hole 12a. A sealing member 43 is disposed in the reduced diameter portion 12b,
The radial bearing 17, the sleeve 44, and the conical roller bearing 45 are arranged in this order from the output side to the input side. The inner ring 17a of the radial bearing 17 is externally fitted and fixed to the yoke 38, and the outer ring 17b is
b and is fixed to the peripheral surface of the through hole 12a.

The sleeve 44 is fixed to the outer race 17b of the radial bearing 17 and the peripheral surface of the through hole 12a. The inner ring 45a of the conical roller bearing 45 is a yoke 3
The input side surface is in contact with the side surface of a step portion 38 d provided on the outer periphery of the yoke 38. The outer ring 45b of the conical roller bearing 45 includes the sleeve 44 and the through hole 1
2a is fixed to the peripheral surface.

The output end of the yoke 38 slightly protrudes from the output side of the main body case 12, and an output shaft 47 is formed. The rotary swash plate surface 37 is held by the yoke 38 at a predetermined angle with respect to the axis O about a virtual trunnion axis TR2 (see FIG. 4) orthogonal to the axis O of the cylinder block 25.

In the cylinder block 25, the same number of cylinder holes 39 as the cylinder holes 29 are arranged annularly around the center of rotation, and extend in parallel with the axis O. The cylinder hole 39 is arranged on the same circumference as the cylinder hole 29. The cylinder block 2 is positioned so that each cylinder hole 39 is located between the cylinder holes 29 adjacent to each other.
In the circumferential direction of No. 5, the cylinder hole 29 is シ リ ン ダ of each other.
They are arranged shifted by a pitch (see FIGS. 5 and 6).

Further, the cylinder hole 39 is provided in the cylinder hole 29.
2 are arranged so as to overlap each other in the length direction (the direction of the axis O of the cylinder block 25), and an opening is formed on the yoke 38 side as shown in FIG. A plunger 36 is slidably disposed in each cylinder hole 39, and a steel ball 36a is rotatably fitted to the tip of the plunger 36. The plunger 36 is in contact with the rotating swash plate surface 37 via a steel ball 36a and a shoe 48 to which the steel ball 36a is attached. The plunger 36 reciprocates with the relative rotation between the rotary swash plate surface 37 and the cylinder block 25, and repeats the receiving and discharging processes.

A hydraulic circuit formed between the hydraulic pump P and the hydraulic motor M will be described. An annular first oil chamber 51 and a second oil chamber 52 are formed on the inner peripheral surfaces of both ends in the axial direction of the cylinder block 25. The first oil chamber 51 and the second oil chamber 52 are provided in the cylinder block 25.
Are provided along the axial direction of the cylinder block 25 in the same number as the number of the cylinder holes 29. The first oil chamber 51 is provided in the cylinder block 25.
The same number of second valve holes 54 as the cylinder holes 39 extend in the axial direction of the cylinder block 25.

The first valve holes 53 and the second valve holes 54 are concentric with the pitch circles of the cylinder holes 29 and 39 and are arranged on a pitch circle having a diameter smaller than the pitch circle. I have. Each of the first valve holes 53 and each of the second valve holes 54 are arranged so as to be adjacent to each other as shown in FIGS.

As shown in FIGS. 1 and 7, each first valve hole 53 has a pump in an oil passage 55 communicating between the first oil chamber 51 and the second oil chamber 52 and the corresponding cylinder hole 29. Port U is formed.

In each of the first valve holes 53, a spool type first switching valve 56 is slidably disposed. First switching valve 56
A coil spring 57 is arranged between the base end surface of the first valve hole 53 and the bottom surface of the first valve hole 53. Hereinafter, the space in which the coil spring 57 is disposed in the first valve hole 53 is referred to as a pressure applying chamber 53a. By the cooperation of the urging force of the coil spring 57 and the pressure of the hydraulic oil charged in the pressure applying chamber 53a described later, the tip of the first switching valve 56 always contacts the cam surface 58 of the inner ring 23b. Touched.

FIG. 7 shows a cam profile of the inner ring 23b of the radial bearing 23. As shown in the figure, the cam surface 58 of the inner ring 23b is connected to the pump port U and the first switching valve 56 around the port closed position n0.
A first opening position n1 for communicating with the oil chamber 51, and a second opening position n2 for communicating between the pump port U and the second oil chamber 52.
There are provided a region H and a region I which reciprocate between them so as to draw a sine curve.

As shown in FIG. 7, a plurality of plungers 26
Are located in the area H of the cam profile and any are located in the area I. And radial bearing 2
The suction stroke and the discharge stroke are given to the hydraulic pump P by the cam action of the third inner ring 23b.

In the present embodiment, as shown in FIGS.
When the cradle 28 is tilted counterclockwise with respect to the axis O, in the region H, the first switching valve 56 is moved to the first opening position n as the cylinder block 25 rotates.
1 to bring the pump port U into communication with the first oil chamber 51 and to be in a non-communication state with the second oil chamber 52. In the region H, the operating oil is sucked into the cylinder hole 29 through the first oil chamber 51, the pump port U, and the oil passage 55 by the plunger 26 performing the suction operation.

In the region I, the first switching valve 56 is moved to the second opening position n as the cylinder block 25 rotates.
2 so that the pump port U communicates with the second oil chamber 52 and the pump port U is disconnected from the first oil chamber 51. In the region I, the hydraulic oil is discharged from the cylinder hole 29 to the second oil chamber 52 through the oil passage 55 and the pump port U by the plunger 26 that performs the discharging operation.

When the cradle 28 is tilted clockwise with respect to the axis O, the hydraulic oil is discharged from the cylinder hole 29 to the first oil chamber 51 through the oil passage 55 and the pump port U in the region H. You. At this time, in the region I, the hydraulic oil is sucked into the cylinder hole 29 via the second oil chamber 52, the pump port U, and the oil passage 55.

As shown in FIGS. 1 and 7, each second valve hole 54 has a motor in an oil passage 65 communicating between the first oil chamber 51 and the second oil chamber 52 and the corresponding cylinder hole 39. A port W is formed.

In each of the second valve holes 54, a spool type second switching valve 66 is slidably disposed so as to be parallel to the plunger 36. A coil spring 67 is provided between the base end surface of the second switching valve 66 and the bottom surface of the second valve hole 54.
Is arranged. Hereinafter, the space in which the coil spring 67 is disposed in the second valve hole 54 will be referred to as the pressure application chamber 54.
a. By the cooperation of the urging force of the coil spring 67 and the pressure of the working oil charged in the pressure applying chamber 54a described later, the tip of the second switching valve 66 always contacts the cam surface 68 of the inner ring 42b. Touched.

FIG. 7 shows a cam profile of the inner ring 42b of the radial bearing 42. As shown in the drawing, the cam surface 68 of the inner ring 42b is connected to the motor port W and the second switching valve 66 around the port closing position m0.
A first opening position m1 for communicating with the oil chamber 52, and a second opening position m2 for communicating between the motor port W and the first oil chamber 51.
An area J and an area K are provided so as to reciprocate between them so as to draw a sine curve.

As shown in FIG.
Are located in the area J of the cam profile and any are located in the area K. Note that, in FIG.
The relative position between the cam bearing surface 8 and the cam surface 68 changes due to the rotation of the radial bearing 42 together with the yoke 38 (see FIG. 3), but they are shown together for convenience of explanation.

Then, with the relative rotation of the cylinder block 25, a receiving stroke and a discharging stroke are given to the hydraulic motor M by the cam action of the inner ring 42b. In the present embodiment, when the area H on the pump side is the suction stroke and the area I is the discharge stroke, in the area J, the second switching valve 66 is moved to the first opening position m1 with the relative rotation of the cylinder block 25. Thus, the motor port W and the second oil chamber 52 communicate with each other, and the first oil chamber 51 is disconnected. In the region J, the operating oil is sucked into the cylinder hole 39 via the second oil chamber 52, the motor port W, and the oil passage 65 by the plunger 36 performing the expansion operation.

In the region K, the second switching valve 66 is moved to the second opening position m2 with the relative rotation of the cylinder block 25, and the motor port W communicates with the first oil chamber 51. The second oil chamber 52 is not communicated. In the region K, the plunger 3 performing the contraction operation
6, the hydraulic oil is discharged from the cylinder hole 39 to the first oil chamber 51 via the oil passage 65 and the motor port W.

When the region H on the pump side is in the discharge stroke and the region J is in the suction stroke, the cylinder hole 39 in the region J
From the second oil chamber 52 through the oil passage 65 and the motor port W.
Hydraulic oil is discharged. At this time, in the region K, hydraulic oil is sucked into the cylinder hole 39 via the first oil chamber 51, the motor port W, and the oil passage 65.

The cylinder hole 29, the cylinder hole 39, the first oil chamber 51, the second oil chamber 52, the first valve hole 53, the second valve hole 54,
The oil passage 55, the oil passage 65, the pump port U and the motor port W constitute a hydraulic circuit, that is, a hydraulic closed circuit.

A shaft hole 70 is formed in the input shaft 15 along the axis O in order to charge the hydraulic circuit with hydraulic oil. The shaft hole 70 has an introduction oil passage 71 in the holder 14 in the radial direction. The introduction oil passage 71 is formed in the circumferential groove 72 formed on the inner peripheral surface of the holder 14 and the holder 14 in the radial direction. The oil passage 73 communicates with the oil passage 73. Lid 1
3 is provided with an oil passage 74 communicating with the oil passage 73.
4 is filled with hydraulic oil from a charge pump (not shown).

In the input shaft 15, a pair of charge valves 75 (check valves) for opening and closing a valve seat that can communicate with the shaft hole 70 is disposed at a portion facing the first oil chamber 51 and the second oil chamber 52. Have been. The charge valve 75 opens until the hydraulic circuit is filled with hydraulic oil, and supplies the hydraulic oil in the shaft hole 70 to the hydraulic circuit. In addition, the charge valve 75 has a hydraulic oil
To prevent backflow to

An oil passage 77 is formed in the input shaft 15 at a portion facing the coil springs 57 and 67 in the radial direction. A circumferential groove 78 communicating with the pressure applying chambers 53a and 54a is formed on the inner peripheral surface of the cylinder block 25, and the circumferential groove 78 communicates with the oil passage 77. The pressure applying chambers 53a, 54a
Is filled with hydraulic oil from a charge pump (not shown) via the shaft hole 70, the oil passage 77, and the circumferential groove 78.

Next, an example of a method of assembling the hydraulic continuously variable transmission T configured as in the present embodiment will be described. First, the main body case 12 is placed so that the input side of the main body case 12 is on the upper side and the output side is on the lower side. Next, the sealing member 4
3. The radial bearing 17, the sleeve 44, and the conical roller bearing 45 are arranged in the reduced diameter portion 12b and the through hole 12a of the main body case 12. Then, the yoke 38 to which the seal member 40, the conical roller bearing 41, and the radial bearing 42 are attached is connected to the conical roller bearing 45, the sleeve 44,
It is inserted into the radial bearing 17 and the seal member 43. Further, the input shaft 15 is inserted into the main body case 12 such that its output side is inserted into the radial bearing 42, the conical roller bearing 41, and the seal member 40.

At this point, the step 15 of the input shaft 15
b, conical roller bearing 41, output side surface of conical roller bearing 41 and yoke 38, step 38d of yoke 38 and conical roller bearing 45, conical roller bearing 45 and sleeve 44, sleeve 44
When the radial bearing 17 and the radial bearing 17 abut on the input side surface of the reduced diameter portion 12b, the movement of the input shaft 15 to the output side is restricted. Therefore, the input shaft 1 disposed in the main body case 12 can be mounted even when the components of the hydraulic type continuously variable transmission T are mounted.
It is not necessary to press 5 with a jig or the like so as not to move in the direction of the axis O.

Next, a plunger 26 having a shoe 30 at the tip and a plunger 36 having a shoe 48 at the tip
, Coil springs 57 and 67, and switching valves 56 and 66
Are attached to the cylinder block 25, and the cylinder block 25 is inserted into the input shaft 15. Then, the cylinder block 25 and the input shaft 15 are spline-connected,
The sleeve 21 is inserted through the input shaft 15, the cradle 28 is attached to the lid 13, and the lid 13 is fastened and fixed to the main body case 12 with a bolt (not shown).

Further, a conical roller bearing 16,
Radial bearing 23, shim S, and seal member 19
And the holder 14 is attached to the lid 1 via bolts B.
3 and fasten.

As described above, when the holder 14 is fastened to the lid 13 via the bolt B, the step bottom surface of the bearing receiving hole 20 of the holder 14 presses the outer ring 16 b of the conical roller bearing 16. Then, the inner ring 16a of the conical roller bearing 16 presses the input side surface of the cylinder block 25 via the sleeve 21, and the output side surface of the cylinder block 25 is
5 is pressed by the locking flange 15a. And input shaft 1
The step 15b of the fifth 5 presses the inner ring 41a of the conical roller bearing 41, and the outer ring 41b of the conical roller bearing 41 presses the bottom surface of the stepped portion 38b of the yoke 38.

Then, the side surface of the step portion 38d of the yoke 38 presses the inner ring 45a, the outer ring 45b, the sleeve 44 of the conical roller bearing 45, and the outer ring 17b of the radial bearing 17. The outer ring 17b is abutted and locked on the input side surface of the reduced diameter portion 12b.

That is, by fastening the holder 14 to the lid 13, the hydraulic continuously variable transmission T
Are assembled at the same time. As a result, the positioning of the conical roller bearing 16 and the conical roller bearing 41 in the axis O direction can be easily performed.

Therefore, according to the hydraulic continuously variable transmission T of the present embodiment, the following effects can be obtained. (1) In the hydraulic device of the hydraulic continuously variable transmission T of the present embodiment, the input shaft 1 is formed by the conical roller bearing 16 and the conical roller bearing 41 via the sleeve 21 and the cylinder block 25.
5 is mounted in the case 11 in a compressed state. Therefore, the conical roller bearing 16 is connected to the conical roller bearing 41.
By pressing the input shaft 15 toward the side, the input shaft 15 can be mounted in a compressed state in which the input shaft 15 is sandwiched between the conical roller bearing 16 and the conical roller bearing 41.

(2) Hydraulic continuously variable transmission T of this embodiment
In this configuration, the components constituting the hydraulic stepless transmission T are sequentially mounted from one side of the main body case 12. Also, when attaching another component constituting the hydraulic continuously variable transmission T to the input shaft 15 mounted in the main body case 12, the output side end of the input shaft 15 is moved in the direction of the axis O with a jig or the like. There is no need to fix to. Therefore, since the components constituting the hydraulic continuously variable transmission T can be sequentially mounted from one side of the main body case 12, the assembling work of the hydraulic continuously variable transmission T can be facilitated. (Other Embodiments) Each of the above embodiments may be modified and embodied in the following other embodiments.

In the hydraulic device of this embodiment, the input shaft 15 is pressed against the cylinder block 25 having the plungers 26 and 36 on both the input side and the output side by the conical roller bearings 16 and 41. The structure to attach was adopted. However, the present invention is not limited to this, and a hydraulic device having a plunger on one of the input side and the output side of the cylinder block 25, that is, a hydraulic pump P only, or a hydraulic motor M only, A structure in which the input shaft 15 is press-fitted by the roller bearing 16 and the conical roller bearing 41 may be adopted.

In this embodiment, the conical roller bearings 16 and 41 are used as the first thrust / radial dual-purpose bearing and the second thrust / radial dual-purpose bearing.
Not limited to this, the first thrust / radial dual purpose bearing,
Alternatively, an angular ball bearing may be used as the second thrust / radial bearing.

In the present embodiment, the input shaft 15 functions as the input shaft and the yoke 38 functions as the output shaft. However, the present invention is not limited to this, and the input shaft 15 functions as the output shaft and the yoke 38 functions as the input shaft. You may function as.

[0057]

According to the first aspect of the present invention, the second thrust / radial dual-purpose bearing is pressed toward the first thrust / radial dual-purpose bearing so that the second thrust / radial dual-purpose bearing and the second thrust / radial dual-purpose bearing are combined. Easy to assemble for both 1 thrust and radial.

[Brief description of the drawings]

FIG. 1 is a sectional view of a hydraulic continuously variable transmission according to an embodiment.

FIG. 2 is a cross-sectional view taken along line AA in FIG.

FIG. 3 is a cross-sectional view of a main part on the hydraulic pump side of the hydraulic continuously variable transmission according to the embodiment.

FIG. 4 is an essential part cross-sectional view of a hydraulic motor of the hydraulic continuously variable transmission according to the embodiment;

FIG. 5 is a sectional view taken along line BB in FIG. 1;

FIG. 6 is a sectional view taken along line CC in FIG. 1;

FIG. 7 is an explanatory view showing a cam action of inner rings 23b and 42b.

[Explanation of symbols]

Reference numeral 15: an input shaft as a shaft; 15a: a locking flange as a cylinder block locking portion; 15b: a stepped portion as a portion that comes into contact with a first thrust / radial bearing; 16: a second thrust / radial bearing Conical roller bearings, 25: cylinder blocks, 26, 36: plungers, 41: conical roller bearings as first thrust / radial bearings.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Hiroshi Matsuyama 1-32 Chaya-cho, Kita-ku, Osaka, Osaka Prefecture Yanmar Diesel Co., Ltd. (72) Inventor Norihiko Sakamoto 1-32, Chaya-cho, Kita-ku, Osaka, Osaka Yanmar Diesel Co., Ltd. (72) Inventor Goro Nozaki 1-32, Chayacho, Kita-ku, Osaka, Osaka Yanmar Diesel Co., Ltd. (72) Yukio Kubota, 1-32 Chayacho, Kita-ku, Osaka, Japan Yanma -Agricultural machinery F term (reference) 3H070 AA01 BB06 CC32 DD94 3H071 AA03 CC32 CC34 DD46 3H084 AA08 AA16 AA45 BB24 BB27 CC02 CC32 CC56 CC57 CC64 3J017 AA01 CA01 DB07

Claims (1)

[Claims] 1. A hydraulic device having a cylinder block which accommodates a plunger disposed parallel to a shaft and is rotatably supported, wherein a cylinder block locking portion is provided on one side of the shaft, and a cylinder block locking portion side is provided. A portion that abuts the first thrust / radial dual-purpose bearing provided on the coaxial portion is provided coaxially, and a portion that locks the coaxial receiver on the anti-contact portion side is provided.
A hydraulic device wherein a second thrust / radial bearing provided on a side opposite to the cylinder block locking portion is pressed against the cylinder block side to press and fix the cylinder block to the cylinder block locking portion.