JPS6220959A - Clutch valve device for hydrostatic continuously variable transmission - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention A1 Objective of the Invention (1) Industrial Field of Application The present invention forms a hydraulic closed circuit between a fixed displacement swash plate hydraulic pump and a variable displacement swash plate hydraulic motor. The present invention relates to a clutch valve device that controls power transmission from the hydraulic pump to the hydraulic motor by preventing short circuits and interruptions between the discharge side and the suction side of the hydraulic pump in a hydrostatic continuously variable transmission.

(2) Conventional technology Conventionally, such a clutch valve device
As shown in Publication No. 7, a high-pressure oil chamber connected to the discharge boat of the hydraulic pump and a low-pressure oil chamber connected to the suction boat of the same pump are formed at the end of the hydraulic motor, and there is a gap between the two oil chambers. A clutch valve that short-circuits and disconnects the hydraulic motor is arranged in the center of the support shaft of the hydraulic motor.

(3) Problems to be solved by the invention In the conventional structure, the clutch valve and its operating system protrude in the axial direction from the end of the hydraulic motor, increasing the overall length of the transmission, which hinders the downsizing of the transmission. It becomes. Particularly when a hydraulic pump and a hydraulic motor are arranged coaxially, if a conventional clutch valve device is employed, the overall length of the transmission becomes even longer.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide the clutch valve device that can shorten the overall length of a transmission.

B1 Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention provides a pump cylinder of a hydraulic pump that is adjacent to a group of annularly arranged cylinder holes in a pump cylinder of a hydraulic pump. A first annular oil chamber connected to the hole and a second annular oil chamber connected to the cylinder hole of the suction stroke are formed concentrically in the pump cylinder, and a plurality of oil chambers are used to open and close the two oil chambers by radial movement. Clutch valves are arranged radially around the pump cylinder, and a clutch control wheel that surrounds these clutch valves and engages with them so that they can rotate relative to each other is arranged such that the control wheel closes all the clutch valves in the radial direction of the pump cylinder. The clutch valve is pivotally supported on a fixed structure so as to be able to move between the clutch-off position in which the clutch valve is opened and the clutch-off position in which some of the clutch valves are opened.

(2) Operation When the clutch control wheel is moved to the clutch-off position, some clutch valves short-circuit between the high-pressure first oil chamber and the low-pressure second oil chamber. Hydraulic oil leaks into the oil chamber, making it impossible to supply pressure oil from the hydraulic pump to the hydraulic motor, and cutting off power transmission between the two.

Return the control wheel to the Clasonao 7 position.

The short circuit between both oil chambers is broken by the full clutch valve, and power transmission from the hydraulic bonnet to the hydraulic Tanabata is resumed.

A plurality of clutch valves are arranged in the radial direction of the pump cylinder, and a clutch valve surrounding the clutch valves is arranged in the radial direction of the pump cylinder.
The control wheel is swung by Bondo...su/da's superhuman strength i+1, so 1, 2, and 5. Therefore, the overall length of the transmission will not be extended.

In addition, when the inner ends of all clutch valves face the oil chamber in the inner position, the oil pressure of the oil pressure chamber always acts equally on the inner ends of all clutch valves, so the clutch control wheels of all clutch valves are The pressing forces exerted are balanced, so the oil pressure in the oil chamber does not challenge the operation of the clutch control wheel.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Examples of the present invention will now be described with reference to the drawings. First, in FIG. 1 showing a first embodiment of the present invention, the power of the engine of a motorcycle is transmitted from its crankshaft 1 to a chain-type primary reduction gear 2) a hydrostatic continuously variable transmission T and a chain 2.
The signal is sequentially transmitted to the rear wheels (not shown) through the next reduction gear 3.

The continuously variable transmission T consists of a constant displacement swash plate type hydraulic cylinder, a supporting variable displacement type swash plate type hydraulic motor M, and a crankshaft 11 supporting the crankshaft 1 as a casing. be accommodated.

The hydraulic pump P includes a cup-shaped input member 5 integrally equipped with an output cusp 2a of the primary speed reduction device 2, and a needle-shaped input member 5 on the inner circumferential wall of the input member 5. The pump cylinder 7 is fitted to be relatively rotatable through the pump cylinder 7, and the pump cylinder 7 is slidably fitted into a plurality of odd number cylinder holes 8, 8... in an annular arrangement surrounding the rotation center of the pump cylinder 7. pump plungers 9, 9...
It is composed of a pump swash plate 10 that comes into contact with the outer ends of these pump plungers 9, 9, . . . .

The pump swash plate 10 is aligned with a virtual trunnion axis 0.0, which is orthogonal to the axis of the pump cylinder 7. Pump cylinder 7 centered on
The back side is rotatably supported by the inner end wall of the input member 5 via a thrust roller bearing 11 in a posture tilted at a certain angle with respect to the axis of the input member 5, and when the human power member 5 rotates, the pump plunger 9, 9... The suction and exhalation strokes can be repeated by applying motion.

In order to improve the ability of the pump plunger 9 to follow the pump diagonal 4FilO, a spring that biases the pump plunger 9 in the expansion direction may be compressed in the cylinder hole 8.

The input member 5 has a thrust roller bearing 1 on its back side.
It is supported by the support cylinder 13 via 2.

On the other hand, the hydraulic motor M includes a motor cylinder 17 disposed coaxially with the pump cylinder 7 and to the left thereof, and a plurality of odd number of cylinder holes arranged in an annular arrangement surrounding the rotation center of the motor cylinder 17. 18. Motor plungers 19, 19... are slid together with 18, 18..., respectively.
and these motor plungers 19. ．． 19..., a swash plate holder 22 that supports the back surface and outer peripheral surface of this motor swash plate 20 via a thrust roller bearing 21 and a radial roller bearing 21', and It is composed of a camp-shaped swash plate anchor 23 that supports a swash plate holder 22.

The motor swash plate 20 can be tilted between an upright position perpendicular to the axis of the motor cylinder 17 and an inclined position inclined at an angle. Accompanying motor plunger 19.
19...G reciprocating motion can be applied to repeat the expansion and contraction strokes.

Incidentally, in order to improve the followability of the motor plunger 19 with respect to the motor swash plate 20, a spring that biases the motor plunger 19 in the extension direction may be compressed in the cylinder hole 18.

The pump cylinder 7 and the motor cylinder 17 constitute an integrated cylinder block B, and the output shaft 25 is passed through the center of the cylinder block B.

The outer end of the Morch cylinder 17 is brought into contact with the flange 25a integrally formed on the outer periphery of the output shaft 25, the pump cylinder 7 is spline-fitted to the output shaft 25, and the circlip is brought into contact with the outer end of the pump cylinder 7. By locking 26 to the output shaft 25, the cylinder block B is fixed to the output shaft 25.

The output shaft 25 also passes through the input member 5 and rotatably supports the member 5 on the needle via seven rings 27.

The support cylinder I3 is connected to the key 28 on the outer periphery of the right end of the output shaft 25.
and is secured with a nut 30. The right end portion of the output shaft is rotatably supported by the crankcase 4 via the support tube 13 and the roller hair ring 3I.

Further, the output shaft 25 is connected to the motor swash plate 20 and the swash plate holder 22.
and a thrust roller bearing 3 that passes through the center of the swash plate anchor 23, and a thrust roller bearing 3 that connects the back surface of the swash plate anchor 23 to the left end thereof.
A support cylinder 33 supported via 2 is spline fitted,
The output shaft 25 is fixed with a nut 34 together with the cassprocket 3a containing the secondary reduction gear 30, and the left end of the output shaft 25 is rotatably supported by the crankcase 4 via the support cylinder 33 and roller hair ring 35.

A hemispherical centering body 36 that engages with the inner circumferential surface of the pump swash plate 10 so as to be tiltable in all directions is slidably fitted onto the output shaft 25 by a spline. This centering body 36 presses the pump swash plate 10 against the thrust roller bearing 11 by the force of the plural disc springs 38, and thereby the pump swash plate 1
0 is always given an alignment effect.

Also, the output shaft 25 has 4. A hemispherical centering body 37 that engages with the inner circumferential surface of the motor swash plate 20 so as to be tiltable in all directions relative to it is slidably spline-fitted. This centering body 37 is?
, 3YB plate springs 39 press the motor swash plate 20 against the thrust roller ring 21, thereby constantly applying an aligning action to the motor swash plate 20.

The alignment action of each swash plate 10, 20 is strengthened, and the rotation direction between the pump swash plate 10 and pump plungers 9, 9... groups, and the motor swash plate 20 and motor plungers 19, 19... groups is enhanced. To prevent slippage, each swashplate 10.20 is provided with a spherical end 9a, 19a of the corresponding plunger 9.19.
Spherical recesses 10a and 20a are respectively formed to engage the spherical recesses 10a and 20a. At this time, the spherical recesses 10a, 20a are formed on the swash plate 10.
In any rotational position of 20, the spherical ends 9a, 1
The radius of curvature is set larger than that of the spherical ends 9a, 19a to ensure proper engagement with the spherical ends 9a.

A hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M as follows.

The cylinder block B has cylinder holes 8.1 (... group) of the pump/cylinder 7 and cylinder holes 1 of the motor cylinder 17.
Between the groups 8 and 18, an annular inner oil chamber 40 and an outer oil chamber 41 are arranged concentrically around the output shaft 25.
and the same number of first valve holes 42 as the cylinder holes 8.8, 18, 18, . ,4
2... and the second valve holes 43, 43... and the adjacent cylinder holes 8, 8... and the first valve holes 4g, 42..., a large number of pump boats a, a..., adjacent cylinder holes 18°18... and second valve holes 43, 43
A large number of motor ports b, b... which communicate with each other.
・And is provided.

At that time, the inner oil chamber 40 is formed between the opposing peripheral surfaces of the cylinder block B and the output shaft 25, and the outer oil chamber 41 is fitted with the cylinder blower rim B and its outer periphery and welded. It is formed between the opposing circumferential surfaces of the sleeve 44.

A first distribution valve 45°4 is provided in the first valve holes 42, 42...
5, and second distribution valves 46, 46, . . . are slidably engaged with the second valve holes 43, 43, .

Each of the first distribution valves 45 is formed in a spool shape,
When the first valve hole 42 occupies the radially outer position, the corresponding pump port a is communicated with the outer oil chamber 41 and disconnected from the inner oil chamber 40, and the corresponding cylinder hole 8 is connected only to the outer oil chamber 41. When the first valve hole 42 is in communication and occupies the radially inner position of the first valve hole 42, the corresponding pump port 1-a is communicated with the inner oil chamber 40 and disconnected from the outer oil chamber 41, and the corresponding cylinder hole 8 is moved inward. It communicates only with the oil chamber 40.

In order to impart such a movement to each first distribution valve 45, a first eccentric 47 is engaged around the group of first distribution valves 45, 45... at their outer ends; A follower shaft 47' that is concentric with the first distribution valve 45, 45... is disposed inside the group and engages the engagement grooves 45a, 45a, 45a, 45a, 45a, 45a, 45a, 45a, 45a, 45a, 45a, etc.
... (see Figure 3). The follower shaft 47' is formed from steel wire, and the first distribution valves 45, 45...
It has one cut D in order to spring it in the direction of engagement with the first eccentric wheel 47.

The first eccentric 47 is constituted by the inner race of a hole hair ring 48 attached i+X to the manpower member 5, and as shown in FIG. 3, the imaginary trunnion axis 0. It is disposed at a position iδ eccentric by a certain distance ε from the center of the output shaft 25 along the line. therefore,
When relative rotation occurs between the input member 5 and the pump cylinder 7, each first distribution valve 45 rotates in the first eccentric 4 in its valve hole 42.
The strobe is set at a distance twice the eccentricity ε1 of ζ and reciprocates between the outer position and the inner position.

Each second distribution valve 46 is formed in a spool shape like the first distribution valve 45, and when it occupies a position radially outward of the second valve hole 43, it pushes the corresponding motor boat b outward. When communicating with the oil chamber 41 and not communicating with the inner oil chamber 40, communicating the corresponding cylinder 18 only with the outer oil chamber 41, and occupying the radially inner position of the second valve hole 43, the corresponding motor The boat b is communicated with the inner oil chamber 40 and disconnected from the outer oil chamber 41, and the corresponding cylinder hole 18 is communicated only with the inner oil chamber 40.

In order to give such an operation to each second distribution valve 46...
1', a second eccentric 49 surrounds the second distribution valves 46, 46... and is engaged with their outer ends;
The concentric follower 49' is the second distribution valve 46, 46...
- an engagement groove 46a disposed inside the group and at the inner end thereof;
46a... (see FIG. 4). The follower 49' is formed from steel wire, and the second distribution valve 46.4
6... in the direction of engagement with the second eccentric wheel 49.
It has two sides.

The second eccentric shaft 49 is constituted by an inner race of a ball hair ring 50 fitted into the crankcase 4, and as shown in FIG.
The output shaft 25 is located at a position offset from the center of the output shaft 25 by a predetermined distance ε2.

Therefore, when the motor cylinder 17 rotates, each second
The distribution valve 46 reciprocates between the outer position and the inner position within its valve hole 43 with a stroke that is twice the eccentricity ε2 of the second eccentricity 49.

As shown in FIG. 2, at both ends of the swash plate holder 22,
A pair of trunnion shafts 80 and 80' aligned on the tilting axis 0 of the motor swash plate 20 are integrally bored.

These trunnion shafts 80, 80' are rotatably supported by the swash plate anchor 23 via needle bearings 81 and roller hair rings 81', respectively. In other words, the tilting axis O is defined by these trunnion shafts 80° and 80'.

An actuation lever 82 is fixed to the outer end of one trunnion shaft 80. When the trunnion shaft 80 is rotated using the operating lever 82, the swash plate holder 22 integrated therewith also rotates, and the swash plate holder 22 can be freely tilted even while the motor swash plate 20 is rotating.

The swash plate anchor 23 is supported on the outer periphery of the motor cylinder 17 via a needle bearing 78, and is supported by a pair of positioning pins 49 so as not to rotate around the output shaft 25.
．． It is connected to the crankcase 4 via 49.

In the above configuration, when the input member 5 of the hydraulic pump P is rotated from the primary reduction gear 2, the pump swash plate 10 alternately applies suction and discharge strokes to the pump plungers 9, 9, etc. The first distribution valve 45 adjacent to the entering pump plunger 9 is connected to the first eccentric 47 and the follower 4.
The first distribution valve 45 adjacent to the pump plunger 9 entering the discharge stroke is operated to the outer position by the cooperation of the first eccentric 47 and the follower 47'. . Therefore, each pump plunger 9 sucks hydraulic oil from the inner oil chamber 40 into the cylinder hole 8 during the suction stroke, and from the cylinder hole 8 to the outer oil chamber 41 during the discharge stroke.
Hydraulic oil is pumped to.

The high-pressure hydraulic oil sent to the outer oil chamber 41 enters the second cylinder hole 18 that accommodates the motor plunger 19 in the expansion stroke.
Hydraulic oil in the cylinder bore 18 accommodating the motor plunger 19 on the retraction stroke is fed through the second distribution valve 46 which is controlled to an outward position by the eccentric wheel 49 and the follower wheel 49'. The inner oil chamber 40-
・It is discharged.

During this period, the pump cylinder 7 receives reaction torque from the pump swash plate 10 via the pump plunger 9 in the discharge stroke, and the motor cylinder 17 receives reaction torque from the motor plunger 1 in the expansion stroke.
The cylinder block B is rotated by the sum of the reaction torque received from the motor swash plate 20 via the motor 9, and the rotational torque is transmitted from the output shaft 25 to the secondary reduction gear 3.

In this case, the gear ratio of the output shaft 25 to the input member 5 is given by the following equation.

Therefore, by changing the capacity of the hydraulic motor M to a value of zero, the gear ratio can be changed to a required value of one.

By the way, the capacity of the hydraulic motor M is the motor plunger 19.
Therefore, by tilting the motor swash plate 20 from an upright position to an inclined position, the gear ratio can be controlled steplessly up to a value of 1.

During such operation of the hydraulic pump P and the hydraulic motor M, the pump swash plate 10 moves from the group of pump plungers 9.9...
Further, the motor swash plate 20 is connected to the motor plunger 19, 1.9.
... Each group receives a thrust load in the opposite direction, but the thrust load that the pump swash plate 1O receives is transmitted through the thrust roller bearing 11, input member 5, thrust roller hair ring 12) support cylinder 13 and The thrust load supported by the output shaft 25 and received by the motor swash plate 20 is carried out by the thrust roller hair ring 21 and the swash plate holder 22.
) A swash plate anchor 23 , a thrust roller bearing 32 ) A support cylinder 33 , a subroket 3 a ) and a nut 34 are similarly supported on the output shaft 25 . Therefore, the above-mentioned thrust load only causes tensile stress on the output shaft 25,
It does not act at all on the crankcase 4 that supports the shaft 25.

In FIGS. 1 and 5, cylinder block B includes:
Further, the first and second valve holes 42, 42...; 43,
A plurality of third valve holes 51, 51, . .52... are rubbed together.

Each clutch valve 52 is formed in a spool shape as shown in FIG. 5B, and the land portion 52a on the inner end side has two chamfered portions 52b over its entire length.

52b is provided. Therefore, the clutch valve 52
Radial intermediate position or inner position of valve hole 5°1
When occupying the radially outward position (clutch-off position), the third valve hole 51 is closed to isolate the two sleeve chambers 40, 41, and when occupying the radially outward position (clutch-off position), the chamfered portions 52b, 52
The oil chambers 40 and 41 can be communicated via b.

In order to control the clutch valves 52, 52..., a clutch control wheel 54 surrounding them is engaged with the outer ends of the clutch valves 52, 52... via a release ring 55, and the clutch valves 52, 52... .52...inner end engagement i$5
2c, 52c, . . . are engaged with a follower shaft 54' that is concentric with the clutch control wheel 54.

This follower shaft 54' is formed from steel wire and has one cut end for urging the clutch valves 52, 52, . . . in the direction of engagement with the inner race of the release bearing 55.

The clutch control wheel 54 is protruded from the outer surface of the control wheel 54 so as to be able to swing between a clutch on position N concentric with the output shaft 25 and a clutch off position F eccentric with respect to the output shaft 25. The bent ear portion 54a is supported by the crankcase 4 via the pivot shaft 56.

A stopper 57 that supports one side of the clutch control wheel 54 and defines its clutch-off position N is integrally formed with the crankcase 4, and the other side is supported by the elastic force of a spring 58 that moves in the direction of the stopper 57. The piston 59 to be pressed is a boss 60 that is integrated with the crankcase 4.
It is rubbed together.

The clutch control wheel 54 has a projection 54b integrally formed on the outer surface opposite to the ear portion 54a.
One end of a hell crankshaft 62 which is supported 61 on the crankcase 4 is connected to b, and the other end is connected to a clutch operating wire W.

Further, the protrusion 54b is attached to the bolt 7 on the crankcase 4 in order to prevent the clutch control port 54 from falling to the side.
It is slidably engaged with the base circular groove 76a of the guide plate 76 fixed at 5.

When the clutch control wheel 54 is pushed by the clutch spring 58 as shown in FIG. It swings around the pivot shaft 56 to the clutch off position F against the pressing force of the piston 59, and cooperates with the release bearing 55, follower shaft 54', etc. to move the clutch valves 52, 52... on the output shaft 25. Make it eccentric to the axis.

As a result, the several clutch valves 52 of the piston 59 are moved from the outer position to the clutch-off position, and via the clutch valves 52 the low pressure inner oil chamber 40 and the high pressure outer oil chamber 41 are moved.
Due to the short circuit between the two, hydraulic oil flows out from the outer oil chamber 41 to the inner oil chamber 40, and supply of pressure oil to the hydraulic motor M becomes impossible. That is, power transmission between the hydraulic pump P and the hydraulic motor M can be interrupted.

When the traction of the clutch operation wire W is released, the clutch control wheel 54 returns to the clutch-on position N in FIG. 5 due to the action of the clutch spring 58, and the clutch valves 52, 52, and
...Holds the group in a concentric position with the output shaft 25. As a result, the short circuit between the oil chambers 40 and 41 is broken, and power transmission from the hydraulic pump P to the hydraulic motor M is restarted.

By the way, since the oil pressure of the inner oil chamber 40 is always acting equally on the inner ends of all the clutch valves 52, 52..., the pressing force exerted by all the clutch valves 52, 52... on the clutch control shaft 54 is Balanced. Therefore, the clutch control shaft 54 is not resisted by the oil pressure in the inner oil chamber 40.
This can be easily swung at all times.

Referring again to FIG. 1, a pair of flange plates 53.53 are fixed to the outer periphery of the sleeve 44 by light press-fitting so as to intervene between the three hair rings 48.55 that surround it. Ru. These flange plates 53.53
According to this method, it is possible not only to prevent the hair rings 48, 50, 55 from interfering with each other, but also to strongly reinforce the sleeve 44, thereby suppressing deformation of the sleeve 44 due to high oil pressure in the outer oil chamber 41. , answer 45, 46, 52 can be ensured to operate smoothly.

In addition, in FIGS. 1 and 2, the output shaft 25 has an oil passage 63 with a dead end at the center thereof, and the open end of the oil passage 63 is connected to the side wall of the crankcase 4. A fuel supply pipe 64 supported by the fuel pipe 64 is inserted. This oil supply pipe 64 is
It communicates with the inside of the oil pan 69 at the bottom of the crankcase 4 via an oil passage 65 formed in the side wall of the crankcase 4, a filter 66 attached to the same side wall, a replenishment pump 67, and a strainer 68. It is driven from the input member 5 via gears 70, 71. Therefore, oil in the oil pan 69 is supplied to the oil passage 63 by the supply pump 67 while the input member 5 is rotating.

The oil passage 63 communicates with the inner oil chamber 40 via a radial replenishment hole 72 formed in the output shaft 25. Further, a check valve 73 is installed in the core oil passage 63 to prevent oil from flowing back into the oil supply pipe 64 .

Therefore, if hydraulic oil leaks from the hydraulic closed circuit between the hydraulic pump P and the hydraulic motor M during normal load operation, the hydraulic oil is replenished from the oil passage 63 to the inner oil chamber 40 through the replenishment hole 72.

During reverse load operation, that is, during engine braking, the hydraulic motor M performs a pumping action and the hydraulic pump P performs a motor action, so that the outer oil chamber 41 is at low pressure and the inner oil chamber 4 is at low pressure.
0 changes to high pressure, and the hydraulic oil attempts to flow back from the inner oil chamber 40 to the oil passage 63, but the back flow is blocked by the check valve 73.

Therefore, reverse S3 from hydraulic motor M to hydraulic pump P
．． Load can be transmitted reliably and a good engine braking effect can be obtained.

In order to lubricate the sliding surface of the pump plunger 9 and the inside of the manual member 5, a thin oil hole 77 is bored in the pump plunger 9 to communicate between the inside and outside of the pump plunger 9, and the sliding surface of the motor plunger 9 and the inside of the swash plate anchor 23 For lubrication, the motor plunger 19 is also provided with a thin oil hole 79 that communicates between the inside and outside of the motor plunger 19.

In FIGS. 2, 6, and 7, the motor swash plate 2
For the zero tilting operation, a shift control device 83 is connected to the operating lever 82 of the trunnion shaft 80.

The speed change control device 83 includes a cylinder 84 fixed to the crankcase 4 and a piston 85 slidably engaged with the cylinder 84. A window 86 is formed in the side wall of the cylinder 84, and a connection hole 87 is formed in the center of the piston 85, passing through it laterally and facing the window 86. , is engaged with the connecting hole 87 through the window 86, so that the piston 85 can be slid in accordance with the rotation of the trunnion shaft 80.

In FIG. 6, the left movement of the piston 85 (actuating lever 82) brings the motor swash plate 20 upright, and a first oil chamber 88 is also formed between the piston 85 and the left end wall of the cylinder 84. Piston 85 and cylinder 84
A second oil chamber 89 is defined between the right end wall of the first oil chamber 88 and a return spring 90 that urges the piston 85 toward the second oil chamber 89.

The first and second oil chambers 88 and 89 are provided with a speed change control valve 91 in the middle.
They communicate with each other via a hydraulic conduit 92 interposed therebetween, and their interiors are filled with hydraulic oil.

The speed change control valve 91 includes a valve case 93 installed at a suitable position in the vehicle's control device and interposed in the middle of a hydraulic conduit 92, and a first valve case 93 interposed in series with an oil passage 94 within this valve face 93. It is composed of second check valves 95 and 96. These first and second
The check valves 95 and 96 are arranged so that their forward directions are opposite to each other, and are always urged in the valve closing direction by valve springs 97 and 98, respectively.

The first and second check valves 95 and 96 are provided with first and second electromagnetic actuators S, S, so that they can be forcibly opened at the appropriate time.
Two operating rods 120 and 121 are connected to each other. 1st
and a second electromagnetic actuator SI.

S2 includes movable cores 122, 123 integrally equipped with the operating rods 120, 121 at their tips, and movable cores 122, 1.
Solenoids 124 and 125 surrounding the valve surface 93 and bolts 12 holding the solenoids 124 and 125 are attached to the valve surface 93.
Actuator body 128,1 fixed with 6 and nut 127
29, return springs 130, 131 that bias the movable cores 122, 123 toward the upper inoperative position, and the valve surface 93.
A stopper plate 133 is fixed to the movable iron cores 122 and 123 with bolts 132 to restrict the non-operating positions of the movable iron cores 122 and 123.

In the first and second electromagnetic actuators St and Sz, when the solenoids 124 and 125 are demagnetized, the movable iron core 122,
123 is held in the inoperative position by the force of the return spring 130.131, spacing the actuating rod 120.121 from the first and second check valves 95, 96, thereby
The check valves 95 and 96 can remain closed. When the solenoids 124 and 125 are energized, the movable cores 122 and 123 return to the spring 130°131 due to the action of the magnetic force.
Since it moves downward against the force of the first. The second check valves 95 and 96 can be forcibly opened.

By the way, since the number of motor plungers 19, 19... is odd, during the rotation of the motor cylinder 17,
Motor plunger 19.19... group is motor swash plate 20
The thrust load exerted on the tilting axis O of the motor swash plate 20 is
The strength alternates between one side and the other side, and vibratory tilting torque acts on the motor swash plate 20. This vibratory tilting torque acts as a pressing force on the piston 85 alternately in the left and right directions via the actuating lever 82.

Therefore, if only the first electromagnetic actuator S is actuated, the first
Since the check valve 95 is opened, the second check valve 96 allows oil to flow from the first oil chamber 88 to the second oil chamber 89, but prevents oil from flowing in the opposite direction. Oil flows from the first oil chamber 88 to the second oil chamber 89 only when a leftward pressing force acts on the piston 85 from the operating lever 82. As a result, the piston 85 moves toward the first oil chamber 88,
The operating lever 82 is rotated in the direction of inclination of the motor swash plate 20, that is, a deceleration operation is performed.

Next, if only the second electromagnetic actuator S2 is operated, the second check valve 96 is opened, so the first check valve 95
This allows oil to flow from the second oil chamber 89 to the first oil chamber 88, but prevents oil from flowing in the opposite direction, and only when a rightward pressing force is applied to the piston 85 by the actuating lever 82. Oil flows from the second oil chamber 89 to the first oil chamber 88. As a result, the piston 85 moves toward the second oil chamber 89, causing the operating lever 82 to rotate in the direction in which the motor swash plate 20 is raised, that is, a speed increasing operation is performed.

When both electromagnetic actuators Sl and S2 are returned to the inoperative state, both check valves 95 and 96, which are closed, cooperate to close the valve surface 93.
The piston 85 becomes immovable, holding the actuating lever 82 in its current position, fixing the motor swash plate 20 in the upright or tilted position, and It is possible to hold the gear ratio.

Furthermore, if both electromagnetic actuators S+ and Sz are activated, oil can freely flow between both sleeve chambers 88 and 89, so if you do this when the engine is stopped, for example, the piston 85 will move to the left. Even if the motor is in this position, it can be quickly moved to the rightward limit with the elastic force of the return spring 90, and the operating lever 82 can be rotated to the maximum tilt position of the motor swash plate 20 to prepare for re-starting.

As shown in FIG. 7, the cylinder 84 is arranged at or near a right angle to the axis of the output shaft 25. As shown in FIG. In this way, when the actuating lever 82 presses the piston 85, the reaction force can be prevented from acting on the swash plate anchor 23 in the axial direction of the output shaft 25 via the trunnion shaft 80.

In FIG. 6, a reserve tank 109 is installed at the top of the cylinder 84, and a relief port 110 and a supply port 111 are bored in the upper wall of the cylinder 84 to communicate the reserve tank 109 with the inside of the cylinder 84.

On the outer periphery of the left and right ends of the piston 85, there are first grooves having a one-way sealing function that closely contact the inner circumferential surface of the cylinder 84.
and second cup seals 105 and 106 are attached to the inner periphery of the cylinder 84, and an O-ring 10 that is in close contact with the outer circumferential surface of the intermediate portion of the piston 85 on both the left and right sides of the window 86.
7,108 is installed.

Therefore, when the piston 8.5 is at the rightward movement limit, the relief port 110 opens to the first hydraulic chamber 88 just before the first cup seal 105, and the supply port 111 always opens to the second cup seal 106 and the O-ring. 108 and opens to the inner surface of the cylinder 84.

Therefore, when the piston 85 is located at the right shift limit, if a pressure increase occurs in the first oil chamber 88 due to an increase in oil temperature, etc.
The pressure is from the relief boat 11° to the reserve tank 1.
Released to 09. Further, when the piston 85 moves to the left, the first oil chamber 88 is pressurized by the piston 85 from the time when the first cup seal 1.5 passes through the opening of the relief port 110, and the first oil chamber 88 is moved from the first oil chamber 88 to the second oil chamber 89. allow oil flow to. At that time, if the pressure in the second hydraulic chamber 89 is reduced to a predetermined pressure or less, the inside of the reserve tank 109 and the second hydraulic chamber 89 are
Due to the pressure difference between the two, the oil in the reserve tank 109 passes from the supply port 111 through the sliding gap between the cylinder 84 and the piston 85, causing the second cup seal 106 to flow into the second oil chamber 8.
It is supplied to the chamber 89 while being bent toward the 9 side.

Note that if the reserve tank 109 is maintained at a high pressure state, the hydraulic conduit 92 is pretensioned by hydraulic pressure, so that the rigidity of the hydraulic conduit 92 against changes in hydraulic pressure accompanying the operation of the piston 25 is strengthened, and the piston 85 operation can be stabilized.

FIG. 8 shows an example of an automatic control circuit for the solenoids 124 and 125 of the first and second electromagnetic actuators St and S2. As shift control factors, the engine's Nurosotor opening, its boost pressure, the input rotation speed and the output rotation speed of the transmission are determined by the throttle opening sensor 140, boost pressure sensor I41, input rotation speed sensor 142, and output rotation speed sensor 143. Each is detected, and a signal corresponding to each detected value is input to the computer 144. Then, the computer 144 outputs an activation signal to the solenoid 124 of the first electromagnetic actuator SI when it determines that the transmission T should be operated to decelerate based on the pre-programmed values; When it is determined, an activation signal is output to the solenoid 125 of the second electromagnetic operation nS2, and when it is determined that the gear ratio should be held, the output to both is stopped. In this way, the transmission T is automatically controlled.

On the other hand, if the driver operates the shift mode setter 145 depending on road conditions, emphasis on low fuel consumption, emphasis on high output, etc., the judgment reference value of the computer 144 increases or decreases based on the corresponding input signal, and the shift characteristics can be freely adjusted. It can be changed.

Next, a second embodiment of the present invention will be explained with reference to FIGS. 9 to 11. A sleeve 4 defining an outer oil chamber 41
4 is oil-tightly fitted to the outer periphery of the cylinder block B via a pair of seal members such as O-rings 150, 150, and is fixed via a knock pin 151. And each 1st. The second distribution valve 45.46 and the clutch valve 52 have valve portions 45A, 46A, 52A that slide into the valve holes 42, 43.51 on the cylinder block B side, and valve holes 42, 43.51 on the sleeve 44 side. The operation unit 45B.

The valve portion 45A is divided into 46B and 52B.

46A, 52A and operating parts 45B, 46B, 52B are slidably abutted against each other.

In this way, in each valve hole 42, 43.51,
Even if the axes of the holes on the cylinder block B side and the holes on the sleeve 44 are slightly misaligned due to machining errors, the misalignment will be absorbed by the lateral sliding between the valve part and the operating part, so Answer 45.46 .52 is the valve hole 42 without being pried in any way.
, 43.51 can be slid smoothly. Moreover, each operation part 45B, 46B, 52B is each valve part 45A.

Since it can be formed into a sufficiently small diameter regardless of 46A or 52A,
The valve holes 4.2.43.51 on the sleeve 44 side can also be made small in diameter to reduce the reduction in strength of the sleeve 44 due to these valve holes.

In this case, the valve portion 45A of the first and second distribution valves 45,46
', 46A has first and second valve holes 42, 43 in the middle part.
Guide runts 45b and 46b in the shape of a protruding circle are provided to slide on the inner wall of the valve holes 42 and 4 (see FIG. 10).
It is possible to prevent the valve parts 45A and 46A from falling down without interfering with the flow of oil at the valve parts 3.

The oil circulation portion of the valve portion 52A of the clutch valve 52 consists of only two chamfered portions 52b, 52b as shown in FIG.

1st. Following widths 47', 49' engage the inner ends of the second distribution valve 45, 46 and the clutch valve 52, respectively.

54' is formed from a spring steel plate, and these follow widths 47'
, 49', 54' are interposed with washers 152, 153 to avoid mutual interference. These following widths 47', 49', 54' and the W7 shear 152,
153 is provided with cutouts or small holes at appropriate locations to prevent these from interfering with the flow of oil in the inner oil chamber 40.

The rest of the structure is the same as that of the previous embodiment, and in FIGS. 9 to 11, parts corresponding to those of the previous embodiment are given the same reference numerals.

FIG. 12 shows a third embodiment of the present invention, in which clutch valves 52, 52, and
An annular reinforcing rib 99 passing through is integrally provided so as to be sandwiched between the eccentric wheels 47 and 49, and an annular reinforcing flange plate 1 is provided on the outer peripheral surface of both ends of the sleeve 44.
00.100 are press-fitted and fixed so that they sandwich both eccentrics 47 and 49, thereby strengthening the rigidity of the sleeve 44 and preventing both eccentrics 47 and 49 from falling. Otherwise, the structure is basically the same as that of the first embodiment, and in FIG. 12, the same reference numerals are given to the parts corresponding to those of the first embodiment.

C0 Effects of the Invention As described above, according to the present invention, an annular first oil chamber connected to a cylinder hole in a discharge stroke and a first oil chamber in a suction stroke are provided adjacent to a group of cylinder holes arranged in an annular manner in a pump cylinder of a hydraulic pump. A second annular oil chamber connected to the cylinder hole is formed concentrically in the pump cylinder, and a plurality of clutch valves that open and close the oil chambers by radial movement are arranged radially in the pump cylinder. A clutch control wheel that surrounds and relatively rotatably engages the clutch valves is set in the radial direction of the pump cylinder between a thalassotion position in which all the clutch valves are closed and a portion of the clutch valves in the open position. Since it is pivotally supported on a fixed structure so as to be able to swing between a valve state and a thalasso-off position, a plurality of clutch valves arranged in the radial direction of the pump cylinder, and surrounding these clutch valves, the pump cylinder A clutch control wheel that swings in the radial direction enables control of short-circuits and cut-offs between oil chambers.
Since the overall length of the transmission is not extended by these clutch valves and clutch control wheels, they can greatly contribute to the compactness of the transmission.

As in the above embodiment, if the inner ends of all the clutches face the oil chamber at the inner position, the pressing force of each clutch valve against the clutch control wheel due to the oil pressure in the oil chamber will be balanced, so the clutch control will be effective. The 't+B wheel can always be easily rocked without being resisted by the oil pressure in the oil chamber.

[Brief explanation of drawings]

1 to 8 show a first embodiment of the present invention, in which FIG. 1 is a longitudinal cross-sectional plan view of a hydrostatic continuously variable transmission installed in a power transmission system of a motorcycle, and FIG. Partial longitudinal cross-sectional rear views of the transmission, Figures 3, 4, and 5 are l-11 in Figure 1.
1 line, IV-IV line and V-V line, Fig. 5A is the operation diagram of Fig. 5, Fig. 5B is a perspective view of the clutch valve in Fig. 5, and Fig. 6 is the vr of Fig. 2. 7 is a plan view of the -vr line of the transmission, FIG. 8 is an automatic control circuit diagram of the transmission, and FIG. 9 is a hydrostatic continuously variable transmission showing a second embodiment of the present invention. A longitudinal sectional view of the main parts of the machine, Figure 10 is the first part in Figure 9.
(Second) A perspective view of the distribution valve, FIG. 11 is a perspective view of the clutch valve in FIG. 9, and FIG. It is a diagram. T...Continuously variable transmission, P...Hydraulic pump, M...Hydraulic motor, B...Cylinder block, ε,...First
Eccentricity of the eccentric 47, ε2... Eccentricity of the second eccentric 49, a... Pump boat, b... Motor boat ■.
... Crankshaft, 4... Crankcase as a fixed structure, 5... Manpower member, 7... Pump cylinder, 8... Cylinder hole, 9... Pump plunger,
10...Pump boat, 17...Motor cylinder,
18... Cylinder hole, 19... Motor plunger,
20... Motor swash plate, 25... Output shaft, 40...
Inner oil chamber as second oil chamber, 41... Outer oil chamber as first extraction chamber, 42... First valve hole, 43... Second valve hole, 44... Sleeve, 45...・・First distribution valve, 46・
...Second distribution valve, 47...First eccentric valve, 47'...
Follow-up axis, 49... second eccentric shaft, 49'... follow-up axis,
52... Clutch valve, 54... Clutch control wheel patent application person Honda Motor Co., Ltd. Figure 4 Figure 3 Figure 5 A Figure 5 Figure 7 Figure 6 Figure 8 Figure 12

Claims (2)

[Claims] (1) In a hydrostatic continuously variable transmission in which a closed hydraulic circuit is formed between a fixed displacement swash plate hydraulic pump and a variable displacement swash plate hydraulic motor, the pump cylinders of the hydraulic pump are arranged in an annular manner. Adjacent to the cylinder hole group, a first annular oil chamber connected to the cylinder hole in the discharge stroke and a second annular oil chamber connected to the cylinder hole in the suction stroke are formed concentrically in the pump cylinder, and both oil chambers are formed concentrically in the pump cylinder. A plurality of clutch valves are arranged radially around the pump cylinder, and the clutch control wheel surrounds these clutch valves and engages them in relative rotation. A shaft is supported on a fixed structure so that it can swing in the radial direction of the pump cylinder between a clutch-on position in which all clutch valves are closed and a clutch-off position in which some clutch valves are opened. A clutch valve device for a hydrostatic continuously variable transmission. (2) In what is stated in claim (1),
A clutch valve device for a hydrostatic continuously variable transmission, in which an inner end of each of the clutch valves faces the oil chamber at an inner position.