JP2893553B2 - Hydrostatic continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Industrial application field The present invention has a pump cylinder of a hydraulic pump and a motor cylinder of a hydraulic motor on the same axis, and is rotatably supported by a casing. A cylinder block, an inner oil passage and an outer oil passage concentrically provided in the cylinder block between a number of cylinder holes provided in the pump cylinder in an annular arrangement and a number of cylinder holes provided in the motor cylinder in an annular arrangement, and the pump cylinder A large number of first distribution valves radially arranged in a cylinder block to alternately communicate the cylinder holes with the oil passages, and a cylinder block to alternately communicate the cylinder holes of the motor cylinder with the oil passages. And a plurality of second distribution valves radially arranged on the cylinder block, and are arranged on the cylinder block such that a short circuit can be made between the two oil passages. About hydrostatic continuously variable transmission and a latch valve.

(2) Prior art Conventionally, such a continuously variable transmission is disclosed in, for example, Japanese Patent Application Laid-Open No. 62-2095.
It is already known as disclosed in Japanese Patent Publication No. 9 and the like.

(3) Problems to be Solved by the Invention In the continuously variable transmission disclosed in the above publication, opening and closing between the inner and outer oil passages is performed to switch between the hydraulic pump and the hydraulic motor between the power transmission state and the power cutoff state. Are arranged radially on the cylinder block so as to reciprocate in the radial direction of the cylinder block, and each clutch valve is engaged with an eccentric wheel capable of adjusting the amount of eccentricity with the cylinder block. ing.

Thus, in the above-described conventional type, each clutch valve engaged with the eccentric wheel is reciprocated in the radial direction of the cylinder block in accordance with the rotation operation of the motor cylinder about its axis. The opening area of the valve changes when the outer oil passage and the inner oil passage communicate with each other, that is, when the clutch is off. For this reason, pressure pulsation occurs in each of the oil passages as a whole, and the clutch off performance is inferior.

Also, due to the actuation of the clutch valves in the radial direction of the cylinder block, it is difficult to increase the opening area of each clutch valve unless the cylinder block is enlarged, and therefore the number of clutch valves is increased. I have to do it.

The present invention has been made in view of such circumstances,
An object of the present invention is to provide a hydrostatic continuously variable transmission capable of improving clutch engagement / disengagement performance by avoiding occurrence of pulsation and contributing to reduction of the number of parts by reducing the required number of clutch valves. I do.

B. Configuration of the Invention (1) Means for Solving the Problems In order to achieve the above object, according to the present invention, the clutch valve is capable of moving along the axial direction of the cylinder block so that the first and second cylinder valves are adjacent to each other. It is arranged on the outer peripheral portion of the cylinder block so as to cross between the distribution valves and between the second distribution valves.

(2) Operation According to the above configuration, it is possible to arrange the clutch valve in a portion of the outer peripheral portion of the cylinder block where the distance between the respective distribution valves is large, and to make the opening area per clutch valve relatively large. As a result, the required number of clutch valves can be reduced, and since the clutch valve does not move in the axial direction due to rotation of the cylinder block, pressure pulsation does not occur when the clutch is off, and the clutch off performance is improved. Improvement can be achieved.

(3) Embodiment Hereinafter, an embodiment in which the present invention is applied to a hydrostatic continuously variable transmission for a motorcycle will be described with reference to the drawings.

1 shows an embodiment of the present invention. FIG. 1 is a cross-sectional plan view of a power unit for a motorcycle, FIG. 2 is a hydraulic circuit diagram showing a schematic configuration of a hydrostatic continuously variable transmission, and FIG. 4 is an enlarged cross-sectional plan view of the hydrostatic continuously variable transmission, and FIG.
FIG. 5 is a cross-sectional view taken along line IV-IV in FIG. 5, FIG. 5 is a cross-sectional view taken along line VV in FIG. 3, FIG. 6A is a cross-sectional view at the clutch-on position along line VI-VI in FIG. FIG. 6A is a cross-sectional view of a main part of FIG. 6A at a clutch off position, FIG. 6C is a cross-sectional view of a main part of FIG. 6A at a communication / release position, FIG. 7 is a cross-sectional view of FIG. The figure is
6A is a sectional view taken along line VIII-VIII of FIG. 6, FIG. 9 is a sectional view taken along line IX-IX of FIG. 3, and FIG. 10 is an enlarged transverse sectional view of the valve cylinder.

First, in FIG. 1, a power unit U of a motorcycle
Is composed of an engine E and a hydrostatic continuously variable transmission T. The crankshaft 1 and the hydrostatic continuously variable transmission T of the engine E are housed and supported in a common casing 4. The hydrostatic continuously variable transmission T is arranged in the casing 4 with the input cylinder shaft 5 and the output shaft 31 parallel to the crankshaft 1, and the crankshaft 1 is connected to the input cylinder via a primary reduction gear 2. An output shaft 31 is connected to a rear wheel (not shown) of the motorcycle via a secondary reduction gear 3.

In FIG. 2, in the hydrostatic continuously variable transmission T, a constant displacement type swash plate type hydraulic pump P and a variable displacement type swash plate type hydraulic motor M form a low pressure path during normal load operation. A hydraulic closed circuit is configured via an inner oil passage 52 that becomes a high pressure passage during reverse load operation, and an outer oil passage 53 that becomes a high pressure passage during normal load operation but becomes a low pressure passage during reverse load operation. A replenishing oil passage 47 connected to a replenishing pump 88 for pumping oil from an oil reservoir 87 is connected to the inner oil passage 52 via a first check valve 95 and a second The outer oil passage 53 is connected to the outer oil passage 53 via a stop valve 96, and is opened between the outer oil passage 53 and the inner oil passage 52 in accordance with the hydraulic pressure of the outer oil passage 53 being equal to or higher than a predetermined value. Pressure regulating valve 97 that guides a part of the hydraulic oil to the inner oil passage 52
Connected via Also, the inner oil passage 52 and the outer oil passage 53
A plurality of, for example, three clutch valves 69 that operate in response to a clutch operation by the driver are interposed therebetween. The clutch valves 69 are provided at a clutch-on position for disconnecting between the oil passages 52 and 53, A clutch-off position for communicating between the passages 52 and 53, and a communication for opening to the outside while the oil passages 52 and 53 are in communication.
The three positions of the discharge positions can be switched.

Next, the configuration of the hydrostatic continuously variable transmission T will be described in detail. In FIG. 3, a swash plate type hydraulic pump P is provided with an input cylinder shaft 5 having an output sprocket 2 a of a primary reduction gear 2.
A pump cylinder 7 rotatably supported on the inner peripheral wall of the input cylinder shaft 5 via a ball bearing 6, and a large number and odd number of annularly arranged pump cylinders 7 provided around the rotation axis of the pump cylinder 7. The plurality of pump plungers 9, 9 ... which are slidably fitted in the cylinder holes 8, 8 ... respectively.
When engaging the front to the pump plungers 9, 9 ... outer end of the pump swash plate 10 to abut around the imaginary trunnion axis O ₁ perpendicular to the pump swash plate 10 and the axis of the pump cylinder 7 A pump swash plate holder 12 that supports the swash plate 10 via a thrust bearing 13 and a radial bearing 14 so as to be maintained at a predetermined angle with respect to the axis of the pump cylinder 7. Thus, the pump swash plate holder 12
Are formed integrally with the input cylinder shaft 5.

When the input cylinder shaft 5 rotates, the pump swash plate 10 can reciprocate the pump plungers 9, 9,... To repeat the suction and discharge strokes.

The hydraulic motor M has a motor cylinder 17 disposed coaxially with the pump cylinder 7 on the left side of FIG. 3, and a cylinder hole 18 provided in the motor cylinder 17 so as to surround the rotation axis thereof. A plurality of motor plungers 19 slidably fitted, a motor swash plate 20 having a front surface engaged with and abutted on the outer end of each motor plunger 19, 19, a thrust bearing 27 and a radial bearing 28 A motor swash plate holder 22 that supports the motor swash plate 20 through a motor, and a motor swash plate anchor 23 that supports the back of the motor swash plate holder 22
It is composed of The same odd number of the cylinder holes 18, 18,... As the cylinder holes 8, 8,. Further, the opposing contact surfaces 22a of the motor swash plate holder 22 and the motor swash plate anchor 23 which are in contact with each other,
23a is formed in a spherical shape centered at the intersection of the axis and the trunnion axis O ₂ of the motor cylinder 17. Moreover the motor swash plate holder 22 is supported on the motor swash plate anchor 23 as allow relative rotation around the said trunnion axis O _2.

A cylindrical cylinder holder 24 is connected to an end of the motor swash plate anchor 23 on the side of the motor cylinder 17.
A ball bearing 25 is provided between the motor 24 and the outer periphery of the motor cylinder 17.

Motor swash plate 20, by the operator swash plate holder 22 is made to rotate around the trunnion axis O ₂ by the ball screw mechanism 79 that is connected to the pulse motor 80, an upright position at right angles to the axis of the motor cylinder 17 , And a maximum tilt position in which the motor plunger 19 is tilted at a certain angle. In the tilted state, the motor plungers 19, 19,. Can be repeated.

The pump cylinder 7 and the motor cylinder 17 are integrally connected to each other to form a cylinder block B, and the cylinder block B is provided with a coaxial output shaft 31 and a shaft 32 integrally. That is, the output shaft 31 is integrally provided from the center of the portion of the motor block 17 facing the motor swash plate 20 in the cylinder block B, and the pump swash plate of the pump cylinder 7 in the cylinder block B is provided.
A shaft 32 is integrally protruded from the center of the portion facing 10 so as to be coaxial with the output shaft 31.

The shaft 32 penetrates through the pump swash plate 10 and the pump swash plate holder 12, and a flange 34 for supporting the end of the pump swash plate holder 12 via an angular contact ball bearing 33 is provided at the end of the shaft 32. Fixed to A ball bearing 35 is provided between the pump swash plate holder 12 and the casing 4.

The output shaft 31 extends so as to penetrate the motor swash plate 20, the motor swash plate holder 22, and the motor swash plate anchor 23, and is provided on the outer periphery of the output shaft 31 on the outer side in the axial direction from the motor swash plate anchor 23. , The support cylinder 39 is connected via a spline 37 and fixed by a split cotter 38, and the output shaft 31 and the support cylinder
An angular contact ball bearing 41 is interposed between the motor 39 and the motor swash plate anchor 23, and an oil seal 42 is interposed between the casing 4 and the support cylinder 30. The input sprocket 3a of the secondary reduction gear 3 is attached to the output shaft 31 via the support cylinder 39.

The cylinder block B has, in order from the shaft 32 side to the output shaft 31 side, a first hole 44 and a second hole 44 having a smaller diameter than the first hole 44.
A hole 45 and a third hole 46 smaller in diameter than the second hole 45 are provided coaxially with the same axis as the rotation axis of the cylinder block B, and these holes 44, 45, 46 are refilled. An oil passage 47 is formed. The end of the third hole 46 is closed by a screw stopper 48.

With reference to FIGS. 4, 5, 6A to 6C, and 7, the group of cylinder holes 8, 8,... Of the pump cylinder 7 and the group of cylinder holes 18, 18,. Between the cylinder block B, an annular inner oil passage 52 and an annular outer oil passage 53 are formed concentrically about the rotation axis of the cylinder block B.

In a portion of the cylinder block B near the second hole 45 in the first hole 44, a valve cylinder 51 having a first annular groove 49 and a second annular groove 50 on the outer periphery and formed basically in a cylindrical shape is press-fitted. And
An inner oil passage 52 is formed by the inner surface of the first hole 44 and the first annular groove 49. A third annular groove 54 is provided on the outer periphery of the cylinder block B at a portion near the cylinder holes 8, 8... Between the cylinder holes 8, 8.
A large number of circles of the same number as the number of the cylinder holes 18, 18 are provided on the outer periphery of the cylinder block B at a portion near the cylinder holes 18, 18 between the group of the cylinder holes 8, 8 and the group of the cylinder holes 18, 18,. The recesses 55 are formed at equal intervals in the circumferential direction by counterboring so as to communicate with the third annular grooves 54, respectively. Thus, the third annular groove 54 and the large number of circular recesses 55,5
5 so that the ring body 56 covers the cylinder block B
The ring body 56 is brazed to the cylinder block B. Thus, an outer oil passage 53 concentric with the inner oil passage 52 is formed annularly between the cylinder block B and the cylinder body 56.

In addition, a third annular groove 54 and a large number of circular recesses 55, 55... Communicating with the third annular groove 54 are provided in the cylinder block B.
A ring body 5 that covers the annular groove 54 and a number of circular recesses 55, 55,.
6 is brazed to the cylinder block B, so that the area of the ring body 56 facing the cylinder block B is made relatively large, and the brazing is melted between the facing surfaces of the cylinder body. B can be firmly fixed to B.

An annular partition wall between the inner oil passage 52 and the outer oil passage 53 of the cylinder block B between the cylinder holes 8, 8... Group of the pump cylinder 7 and the cylinder holes 18, 18,. The same number of first and second valve holes 57, 58,... As the cylinder holes 8, 8,. Moreover, the first valve holes 57 are arranged on the cylinder holes 8, 8.
The second valve holes 58 are arranged on the group side of the cylinder holes 18, 18,.

The cylinder block B has a plurality of pump ports 59, 59 ... communicating with the adjacent cylinder holes 8, 8 ... and the first valve holes 57 ... along the axis thereof, and the cylinder holes B: , And a plurality of motor ports 60, 60 communicating with each other through the second valve holes 58.58.

The first valve holes 57, 57,.
61 are respectively slidably fitted in the second valve holes 56, 56, respectively. Are provided at the outer ends of the first distribution valves 61, 61,... And at the outer ends of the second distribution valves 61, 61,. Eccentric ring 64 surrounding the, 61 ...
Are engaged via ball bearings 65 and 66, respectively. Moreover, the outer ends of the first distribution valves 61, 61.
Are connected to each other by a first forcing wheel 67 concentric with the second distributing valves 61, 61..., And the outer ends of the second distributing valves 61, 61. Be linked.

First eccentric ring 63 is intended to be provided integrally with the input cylindrical shaft 5, is arranged eccentrically from the center of the cylinder block B by a predetermined distance epsilon ₁ along the imaginary trunnion axis O ₁ as shown in FIG. 4 . The second eccentric ring 64 is intended to be provided continuously to the cylinder holder 24, arranged in along the imaginary trunnion axis O ₂ eccentric from the center of the cylinder block B by a predetermined distance epsilon ₂ as shown in FIG. 5 Is done.

Here, the operation of the first distribution valve 61 will be described. The input cylinder shaft 5 and the pump cylinder 7, ie, the cylinder block B
When a relative rotation occurs between the first distribution valve 61 and the first distribution valve 61,
It is reciprocated between the radially inner position and outer position of the pump cylinder 7 to twice the eccentric distance epsilon ₁ as a stroke in the first valve hole 57 by the eccentric wheel 63. And the fourth
As shown in the figure, in the discharge area D of the hydraulic pump P, the first
The distributing valve 61 moves on the inward position to connect the corresponding pump port 59 to the outer oil passage 53 and not to the inner oil passage 52, so that the pump plunger 9 during the discharge stroke is moved.
As a result, hydraulic oil is pumped from the cylinder hole 8 to the outer oil passage 53. In the suction area S of the hydraulic pump P, the first distribution valve 61
Moves to the outer position side, and the corresponding pump port 59
Is communicated with the inner oil passage 52 and is cut off from the outer oil passage 53, so that the pump plunger 9 during the suction stroke sucks hydraulic oil from the inner oil passage 52 into the cylinder hole 8.

In addition, the operation of the second eccentric wheel 64 will be described. When the motor cylinder 17, that is, the cylinder block B rotates,
Each of the second distributing valve 62 is reciprocated between the radially inner position and outer position of the cylinder block B to twice the eccentric distance epsilon ₂ as stroke in the second eccentric ring 64 by the second valve hole 58 You. Thus, as shown in FIG.
In the expansion region Ex, the second distribution valve 62 moves on the inward position side, connects the corresponding motor port 60 to the outer oil passage 53, and disconnects between the motor port 60 and the inner oil passage 52. Accordingly, high-pressure hydraulic oil is supplied from the outer oil passage 53 to the cylinder hole 18 of the motor plunger 19 during the expansion stroke. In the contraction region Sh of the hydraulic motor M, the second distribution valve 62
Moves on the outer position side, connects the corresponding motor port 60 to the inner oil passage 52 and makes the motor port 60 and the outer oil passage 53 non-communicable, and thereby the cylinder hole of the motor plunger 19 during the contraction stroke. The hydraulic oil is discharged from 18 to the inner oil passage 52.

Thus, the cylinder block B includes the pump cylinder 7
Through the pump plunger 9 in the discharge stroke.
Of the motor cylinder 17 and the reaction torque received from the motor swash plate 20 via the motor plunger 19 during the expansion stroke, and the rotation torque is transmitted from the output shaft 31 to the secondary reduction gear 3. You.

In this case, the speed ratio of the output shaft 31 to the input cylinder shaft 5 is given by the following equation.

Therefore, if the capacity of the hydraulic motor M is changed from zero to a certain value, the gear ratio can be changed from one to a certain required value. In addition, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, the speed ratio can be steplessly controlled from 1 to a certain value by tilting the motor swash plate 20 from the upright position to a certain tilt position. can do.

8 and 9, the first valve holes 57 and 5 adjacent to each other are positioned at equal intervals in the circumferential direction, for example, at 120 ° intervals on the outer peripheral portion of the cylinder block B.
7 and between the second valve holes 58, 58, the clutch valves 69 are arranged in a direction parallel to the axis of the cylinder block B and outside the oil passage 53.
Are arranged so as to be able to reciprocate across the third annular groove 54. That is, three sliding holes 70... For slidably fitting a basically bar-shaped clutch valve 69 are formed in the outer peripheral portion of the cylinder block B in parallel with the axis of the cylinder block B. It is drilled at equal intervals in the circumferential direction. In the cylinder block B, the inner end is opened to the inner oil passage 52 and the outer end is closed by the ring body 56 so as to extend in the radial direction and cross the sliding holes 70.
And three recesses 72 formed by digging the third annular groove 54 in the outer oil passage 53 in a semicircular shape by spot facing.

The clutch valve 69 is provided with a first annular recess 69 communicating with the communication hole 71.
a and a second annular concave portion 69b communicating with the concave portion 72, that is, the outer oil passage 53, on the outer periphery.
Are connected to one end of an operating wheel 73 of the cylinder block B surrounding the pump cylinder 7 at equal intervals in the circumferential direction thereof. Further, a ring-shaped support member 74 having a substantially L-shaped vertical section is fixed to the operation wheel 73 so as to sandwich the inner ring of the ball bearing 75 therebetween. That is, on the inner periphery of the operating wheel 73, three projections 73b are provided at positions spaced apart from the connection projections 73a at equal intervals in the circumferential direction, and these projections 73b are provided. And one end of each of three pins 76 penetrating through the support member 74 at a portion corresponding to each of the projections 73b.
The operating wheel 73 and the support member 74 are integrated by crimping and engaging with each other. Further, an operation shaft 82 movable along the axial direction of the cylinder block B is supported on the motor swash plate anchor 23, and one end of the operation shaft 82 has a support ring 83 for supporting the outer ring of the ball bearing 75. The other end of the operating shaft 82 is connected to a rotating shaft 84 having an axis orthogonal to the axis of the cylinder block B and rotating in response to operation of a clutch lever (not shown).

By operating the clutch lever, the clutch valves 69 are brought into a clutch-on position (a position shown in FIG. 6A) for disconnecting between the communication holes 71 communicating with the inner oil passage 52 and the outer oil passage 53.
6A from the clutch-on position to the right in FIG. 6A to communicate between the communication holes 71... And the outer oil passage 53 (the position in FIG. 6B), and further advance from the clutch-off position. 6C and communicates between the communication holes 71 and the outer oil passage 53 and switches between a communication / discharge position (the position shown in FIG. 6C) that opens the communication holes 71 and the outer oil passage 53 to the outside. Will be.

Referring again to FIG. 3, the first hole 44 of the cylinder block B
, An oil filter 86 is fitted and fixed, and the oil filter 86 is supplied with hydraulic oil pumped from an oil reservoir 87 by a supply pump 88 via an oil filter 89,
88 is driven by the input cylinder shaft 5.

In FIG. 10, a communication hole 90 is formed in the valve cylinder 51 press-fitted into the first hole 44 of the cylinder block so as to avoid partitioning the replenishing oil passage 47 by the valve cylinder 51 between both ends in the axial direction. At the same time, a communication hole 91 for communicating the inside with the inner oil passage 52 is formed in the central portion in the axial direction. Moreover, between the valve cylinder 51 and the inner surface of the first hole 44, an inner oil passage 52 is formed by the first annular groove 49, and an annular oil passage 92 is formed by the second annular groove 50. A communication passage communicating with the outer oil passage 53
93 is drilled in the cylinder block B.

In the valve cylinder 51, a first check valve 95 for preventing backflow of hydraulic oil from the communication hole 91, that is, the inner oil passage 52 to the replenishing oil passage 47 is provided.
A second check valve 96 for preventing backflow of hydraulic oil from the outer oil passage 53, that is, the annular oil passage 92 to the replenishment oil passage 47, and an outer oil passage 53 for preventing an excessive increase in the hydraulic pressure of the outer oil passage 53. That is, the annular oil passage 92 and the pressure regulating valve 97 interposed between the communication hole 91, that is, the inner oil passage 52 are provided.

The first check valve 95 has a valve hole 101 communicating with the supply oil passage 47, is fitted and fixed to one end (the right end in FIG. 10) of the valve cylinder 51, and has a communication hole 91, that is, an inner oil passage 52. Valve room 102 leading to
Between the valve seat 51 and the valve cylinder 51;
A spherical valve element 104 housed in the valve chamber 102 so that the opening end of the valve chamber 102 side can be closed, and a valve chamber for exerting a spring force for urging the valve element 104 toward the valve seat member 103 side. The valve spring 105 is housed in the valve 102.

The second check valve 96 is basically cylindrical with a bottom, and is fitted and fixed to the other end (the left end in FIG. 10) of the valve cylinder 51 with its closed end in an axially inward position. Valve housing 107
And a valve chamber 108 formed between the valve housing 107 and a cylindrical valve seat member 109 fitted and fixed to an open end of the valve housing 107, and seating on the valve seat member 109 is enabled. Valve room 10
8 and a valve chamber 1 for exerting a spring force for urging the valve body 110 in a direction to be seated on the valve seat member 109.
08 and a valve spring 111 housed in the housing.

An annular path 112 communicating with the valve chamber 108 is formed between the outer periphery of the valve housing 107 and the inner periphery of the valve cylinder 51, and the annular path 112 is formed through a passage 113 formed in the valve cylinder 51. To the annular oil passage 92. That is, the valve chamber 108 communicates with the outer oil passage 53. The valve seat member 109 is provided with a valve hole 114 communicating with the supply oil passage 47.

Thus, during a normal load operation in which the hydraulic pump M hydraulically drives the hydraulic motor M, the pressure in the low-pressure side internal oil passage 52 becomes lower than the pressure in the supply oil passage 47 due to oil leakage from the hydraulic closed circuit therebetween. Is lowered, the first check valve 95 is opened and the supply oil passage 47 is opened.
The working oil is supplied to the inside oil passage 52 from the inside. On the other hand, at this time, the hydraulic oil in the high pressure side outer oil passage 53 is prevented from flowing out to the supply oil passage 47 by the second check valve 96.

Also, at the time of reverse load operation, that is, at the time of engine braking, the hydraulic motor M performs a pump action, and the hydraulic pump P performs a motor action. Therefore, the outer oil passage 53 changes to a low pressure, and the inner oil passage 52 changes to a high pressure. If the pressure in the outer oil passage 53 becomes lower than the pressure in the supply oil passage 47 due to oil leakage, the second check valve 96 opens to supply hydraulic oil from the supply oil passage 47 to the outer oil passage 53, and the inner oil passage. The outflow of hydraulic oil from 52 to the supply oil passage 47 is prevented by the first check valve 95.

The pressure regulating valve 97 includes a valve cylinder 51, a valve body 115, and a valve spring.

In the valve cylinder 51 between the first and second check valves 95 and 96, a first sliding hole 11 communicating with the communication hole 91 in order from the first check valve 95 side.
7 and a second sliding hole 119 coaxially arranged with the first sliding hole 117 with a communication hole 122 described later between the first sliding hole 117 and the second sliding hole 119. second sliding bore 119 through the section 120 and the guide hole 121 coaxially connected to is bored, the inner diameter D ₁ of the first slide hole 117 is slightly than the inner diameter D ₂ of the second slide hole 119 (D ₁ <D ₂ ). The inner diameter of the guide hole 121 is set larger than the inner diameter D ₂ of the second sliding hole 119.

The valve element 115 is basically formed in a cylindrical shape, and the first check valve 95 side sequentially includes a first check valve 95 side.
A valve portion 115a slidably fitted in the sliding hole 117; a valve rod portion 115b slidably fitted in the second sliding hole 119;
And a flange-shaped stopper portion 115c which can abut against the front end of the valve portion 115a.
The two notches 115d are provided, and the valve portion 115a and the valve rod portion 11 are provided.
An annular recess 115e is provided on the outer periphery between 5b. Valve cylinder 51
A communication hole for communicating the annular recess 115e with the annular oil passage 92
122 is bored, and the valve spring 116 is contracted between the valve housing 107 of the second check valve 96 and the stopper 115c.

In such a pressure regulating valve 97, an annular oil passage is provided in the annular recess 115e.
92, that is, the hydraulic pressure of the outer oil passage 53 acts,
Due to the difference between the inner diameters D ₁ and D ₂ of the sliding holes 117 and 119, a valve opening force (force toward the left side in FIG. 10) is applied to the valve body 115.
Under normal operating conditions where the oil pressure of 53 is below the specified value, the valve
Since the force of the valve spring 116 for urging the valve 115 in the valve closing direction is larger than the valve opening force, the valve body 115 is in the valve closed state, that is, the annular concave portion 1.
15 e and the communication hole 91 are kept in a state of being cut off. When the oil pressure of the outer oil passage 53 exceeds the specified value, the valve opening force becomes larger than the force of the valve spring 116, so that the valve body 115
The notch 115d of the valve portion 115a of the valve body 115 communicates between the communication hole 122 and the first sliding hole 117, and the excessive oil pressure of the outer oil passage 53 passes through the communication hole 91. Inside oil passage
Released to 52. Further, when the oil pressure in the outer oil passage 53 returns to the original state, the valve element 115 returns to the closed state by the spring force of the valve spring 116. Therefore, even when the vehicle suddenly starts or accelerates, the outer oil passage
Excessive increase in the hydraulic pressure of 53 can be suppressed.

Next, the operation of this embodiment will be described. The clutch valves 69 move along the axial direction of the cylinder block B in a portion where the distance between the distribution valves 61, 61; The opening area per one clutch valve 69 can be made relatively large, and the required number of clutch valves 69 can be reduced to a small number of about three. And the number of parts can be reduced.

Moreover, each of the clutch valves 69... Keeps its position fixed regardless of the rotation of the cylinder block B.
Therefore, the clutch valves 69 do not move back and forth in the axial direction to cause pressure pulsation in the inner oil passage 52 and the outer oil passage 53, and the clutch off performance can be improved.

In addition, each clutch valve 69 can open the inner oil passage 52 and the outer oil passage 53 to the outside at the communicating / discharging position, and can discharge a part of the relatively high-temperature hydraulic oil. By supplying relatively low temperature hydraulic oil from the first or second check valves 95 and 96 in accordance with the discharged amount, the hydraulic oil in the hydraulic closed circuit between the hydraulic pump and the hydraulic motor M is supplied. Cooling can be achieved.

Further, the first oil passage 52 is formed in the valve cylinder 51 which is press-fitted into the cylinder block B so as to form an inner oil passage 52 between the valve block 51 and the cylinder block B.
By providing the check valve 95, the second check valve 96, and the pressure regulating valve 97, the valves 95, 96, and 97 can be unitized.
The unitization makes it easy to check the function of each of the valves 95 to 97, and improves the assemblability and workability as compared with those provided at other positions in the cylinder block B.

C. Effects of the Invention As described above, according to the present invention, the clutch valve allows the cylinder block to move along the axial direction so as to cross between the first distribution valve and the second distribution valve adjacent to each other. Since the clutch valve is disposed on the outer peripheral portion of the cylinder block, it is possible to arrange the clutch valve in a portion where the distance between the respective distribution valves is wide and to make the opening area per clutch valve relatively large. The number of parts can be reduced by reducing the required number of parts, and the pulsation of pressure in the inner oil passage and the outer oil passage due to rotation of the cylinder block when the clutch is off prevents the clutch off performance from being improved. Can be planned.

[Brief description of the drawings]

1 shows an embodiment of the present invention. FIG. 1 is a cross-sectional plan view of a power unit for a motorcycle, FIG. 2 is a hydraulic circuit diagram showing a schematic configuration of a hydrostatic continuously variable transmission, and FIG. Is an enlarged cross-sectional plan view of the hydrostatic continuously variable transmission, FIG. 4 is a cross-sectional view taken along the line IV-IV of FIG. 3, FIG. 5 is a cross-sectional view taken along the line VV of FIG.
6A is a sectional view taken along the line VI-VI of FIG. 5 at the clutch-on position, FIG. 6B is a sectional view of a main part of FIG. 6A at the clutch-off position, and FIG. 6C is a sectional view at the communication / discharge position. FIG. 6A is a sectional view of a main part, FIG. 7 is a sectional view taken along line VII-VII of FIG. 6A, and FIG.
9 is a sectional view taken along line VIII-VIII of FIG. 9, FIG. 9 is a sectional view taken along line IX-IX of FIG. 3, and FIG. 10 is an enlarged transverse sectional view of the valve cylinder. 4 ... casing, 7 ... pump cylinder, 8, 18 ... cylinder hole, 17 ... motor cylinder, 61 ... first distribution valve, 62 ... second distribution valve, 69 ... clutch valve, B ... cylinder block, M ... hydraulic motor, P: hydraulic pump, T: hydrostatic continuously variable transmission

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-203959 (JP, A) JP-A-61-153056 (JP, A) JP-A-62-20959 (JP, A) JP-A-62-20959 177353 (JP, A) (58) Field surveyed (Int. Cl. ⁶ , DB name) F16H 39/02-39/14 F16H 61/38-61/64

Claims (1)

(57) [Claims] A pump cylinder (7) of a hydraulic pump (P)
A cylinder block (B) having a motor cylinder (17) of a hydraulic motor (M) coaxially and rotatably supported on a casing (4); and a number of annular blocks arranged on a pump cylinder (7). An inner oil passage (52) and an outer oil passage (53) provided concentrically in the cylinder block (B) between the cylinder hole (8) and a number of cylinder holes (18) provided in the motor cylinder (17) in an annular arrangement. A large number of first distribution valves (61) radially arranged in the cylinder block (B) so as to alternately communicate the cylinder holes (8) of the pump cylinder (7) with the two oil passages (52, 53).
And a number of second distribution valves (62) radially arranged in the cylinder block (B) to alternately communicate the cylinder holes (18) of the motor cylinder (17) with the two oil passages (52, 53). ) And a clutch valve (69) disposed in the cylinder block (B) so as to enable a short circuit between the two oil passages (52, 53).
9) allows the cylinder block (B) to move along the axial direction so as to cross between the first distribution valves (61, 61) and the second distribution valves (62, 62) adjacent to each other. A hydrostatic continuously variable transmission, which is disposed on the outer periphery of (B).