JPH073219B2 - Swash plate type hydraulic system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of Industrial Application The present invention relates to a swash plate type hydraulic device applied to a hydraulic pump or a hydraulic motor, and in particular, parallel to and surrounding a rotation axis. A cylinder having a large number of cylinder holes arranged annularly;
A large number of plungers that are slidably fitted into the cylinder holes and project a spherical end portion from one end surface of the cylinder; a swash plate holder that is arranged to face the one end surface of the cylinder and is rotatable relative to the cylinder; The present invention relates to an improvement of a swash plate type hydraulic device having one end surface rotatably supported, and the other end surface having a swash plate having a large number of spherical recesses that engage with the spherical ends of the plungers.

(2) A conventional swash plate type hydraulic device is known, for example, from Japanese Patent Application Laid-Open No. 61-274166.

In such a swash plate type hydraulic device, the swash plate can rotate synchronously without causing slippage with the plunger group due to the engagement between the spherical recess of the swash plate and the spherical end of the plunger. Since the spherical end of each plunger may get over the partition between the spherical recesses due to the rotational torque between the swash plate and the plunger group, the conventional spherical recesses have a sufficient depth.

(3) Problems to be Solved by the Invention However, in order to form the spherical recess sufficiently deep,
It is necessary to use a swash plate having a relatively large plate thickness, which is an obstacle to reducing the weight of the swash plate and thus the entire device.

The present invention has been made in view of such circumstances, and it is possible to obtain a deep effective engagement depth between the spherical concave portion and the spherical end portion of the plunger without forming the entire swash plate to have a special thick wall. It is an object of the present invention to provide the swash plate type hydraulic device described above.

B. Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention forms a partition between each spherical concave portion of a swash plate into a mountain shape protruding toward the center in the radial direction. It is characterized by

(2) Operation According to the above configuration, the effective engagement depth between the spherical concave portion and the spherical end portion of the plunger can be increased without forming the entire swash plate to be thick, and therefore even under high load. The synchronous rotation of the swash plate and the plunger group can be reliably performed without the spherical end portion sliding out of the spherical concave portion.

(3) Embodiment One embodiment of the present invention will be described below with reference to the drawings.
First, referring to FIG. 1, a power unit U of a motorcycle
Includes an engine E and a hydrostatic continuously variable transmission T. The crankshaft 1 and the transmission T of the engine E are housed and supported in a common casing 4. The continuously variable transmission T is arranged such that the input cylinder shaft 5 and the output shaft 31 are parallel to the crankshaft 1, the crankshaft 1 drives the input cylinder shaft 5 via the primary reduction gear device 2, and the output shaft 31 is A rear wheel (not shown) of the motorcycle is driven via the secondary reduction gear 3.

A kick-type starter St is installed adjacent to the right end of the crankshaft 1.

2 and 3, the continuously variable transmission T comprises a constant displacement type swash plate hydraulic pump P and a variable displacement type swash plate hydraulic motor M, and the hydraulic motor is the hydraulic system of the present invention. Correspond.

The hydraulic pump P is an output sprocket 2a of the primary speed reducer 2.
Is connected by a rivet 16, an input cylinder shaft 5, a pump cylinder 7 which is relatively rotatably fitted to an inner peripheral wall of the input cylinder shaft 5 via a needle bearing 6, and a rotation axis line of the pump cylinder 7. A large number of pump plungers 9, 9 ... Sliding in a large number of odd-numbered cylinder holes 8, 8 ... Arranged so as to surround the pump plungers 9, 9 ... Pump swash plate 10
And the back surface of the swash plate 10 is angularly fixed to keep the pump swash plate 10 inclined at a constant angle with respect to the axis of the pump cylinder 7 about the virtual trunnion axis O ₁ orthogonal to the axis of the pump cylinder 7. And a pump swash plate holder 12 supported via a contact bearing 11. The pump swash plate holder 12 is also connected to the input cylinder shaft 5 by the rivets 16. The angular contact bearing 11 is configured to cooperate with the pump swash plate holder 12 to provide the pump swash plate 10 with an aligning action.

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

In order to improve the followability of the pump plunger 9 with respect to the pump swash plate 10, a coil spring 15 that biases the pump plunger 9 in the extension direction is housed in the cylinder hole 8.

On the other hand, the hydraulic motor M includes a motor cylinder 17 coaxially arranged to the left of the pump cylinder 7 and a large number of odd-numbered cylinder holes arranged in the motor cylinder 17 so as to surround its rotation axis. A large number of motor plungers 19, 19 ... that are respectively slidably attached to 18, 18 ... And a motor swash plate 2 that abuts the outer end front surfaces of these motor plungers 19, 19 ...
0, and a motor swash plate holder 22 that supports the back surface of the motor swash plate 20 via angular contact bearings 21,
Further, it is composed of a motor swash plate anchor 23 that supports the back surface of the motor swash plate holder 22.

As clearly shown in FIG. 14, the facing surfaces f ₁ and f ₂ of the motor swash plate holder 22 and the motor swash plate anchor 23 that are in contact with each other are centered on the intersection of the axis of the motor cylinder 17 and the trunnion axis O _2. It is formed on a spherical surface.

Further, the motor swash plate holder 22 is integrally provided with a pair of semi-cylindrical trunnion shafts 22a, 22a arranged on a trunnion axis O ₂ orthogonal to the rotation axis of the motor cylinder 17 at both ends. A pair of semi-cylindrical recesses 23a, 23a formed at both ends of 23 are rotatably engaged with each other. The trunnion shaft 22a and the recess 23a have shapes other than a semi-cylindrical shape as long as they can prevent the rotation of the motor swash plate holder 22 around the axis other than the trunnion axis O ₂ by their engagement. However, it may be, for example, a semi-conical shape.

The angular contact bearing 21 is configured to cooperate with the motor swash plate holder 22 to provide the motor swash plate 20 with an aligning action.

The motor swash plate anchor 23 is fixed to the left side wall of the casing 4 with a bolt 27 together with a cylindrical cylinder holder 24 connected to the right end thereof. This cylinder holder 24 is a needle bearing
The outer peripheral surface of the motor cylinder 17 is rotatably supported via 25 and a ball bearing 26.

The motor swash plate 20 is configured to move by rotation of the motor swash plate holder 22 between an upright position that is perpendicular to the axis of the motor cylinder 17 and a maximum tilt position that tilts at a certain angle. In the tilted state, the motor plungers 19, 19 ... Can be reciprocally moved with the rotation of the motor cylinder 17 to repeat the expansion and contraction strokes.

In order to improve the followability of the motor plunger 19 with respect to the motor swash plate 20, a coil spring 30 that biases the motor plunger 19 in the extension direction is housed in the cylinder hole 18.

The pump cylinder 7 and the motor cylinder 17 are integrally connected to each other to form a cylinder block B, and the output shaft 31 is passed through the center of the cylinder block B. Then, the outer end of the pump cylinder 7 is abutted against the halved stopper ring 33 locked to the outer periphery of the output shaft 31, and the motor cylinder 17 is spline-fitted to the output shaft 31 by the spline fitting 32. The cylinder block B is fixed to the output shaft 31 by locking the circlip 35, which is in contact with the outer end of the cylinder via the seat plate 34, with the output shaft 31.

The right end of the output shaft 31 is the pump swash plate 10 and the pump swash plate holder.
A flange 37 having a large rigidity is also integrally provided, which also penetrates 12 and supports the back surface of the pump swash plate holder 22 via a thrust roller bearing 40. The output shaft 31 rotatably supports the pump swash plate holder 22 via a needle bearing 42.

The left end of the output shaft 31 is the motor swash plate 20 and the motor swash plate holder 22.
And extending so as to penetrate the motor swash plate anchor 23,
A retainer 46 and a thrust roller bearing 47 are sequentially interposed from the swash plate anchor 23 side between the support cylinder 45, which is splined 43 on the outer periphery of the left end portion and fixed by the two-divided cotter 44, and the motor swash plate anchor 23. To be dressed. The output shaft 31 is rotatably supported by the swash plate anchor 23 via the needle bearing 48 and the retainer 46.

In this way, split cotter from output sprocket 2a
Since all components up to 44 of the transmission T are assembled on the output shaft 31 as one assembly, the transmission T can be easily attached to and detached from the casing 4.

When mounting the transmission T on the casing 4, the pump swash plate holder
12 is supported on the right side wall of the casing 4 via a ball belling 41, the input cylinder shaft 5 is supported on a separable intermediate support wall 4a of the casing 4 via a ball bearing 39, and the motor swash plate anchor 23 is a casing. It is fixed to the left side wall of No. 4 by a bolt 27. And on the right side wall of the casing 4,
The cap 50 that closes the maintenance hole 49 opening there is a bolt
It is fixed at 51, and on the left side wall of the casing 4, there is a support cylinder.
An oil seal 56 that is in close contact with the outer peripheral surface of 45 is fitted. Further, the input sprocket 3a of the secondary speed reducer 3 is fixed to the outside of the casing 4 with bolts 38. At that time, the input sprocket 3a presses the outer circumference of the split cotter 44 and functions as a stopper for the sprocket.

In order to rotate the pump swash plate 10 synchronously with the pump cylinder 7, the pump swash plate 10 is formed with a spherical recess 10a with which the spherical end 9a of the corresponding pump plunger 9 is engaged.

Further, in order to rotate the motor swash plate 20 in synchronization with the motor cylinder 17, the motor swash plate 20 is formed with a spherical recess 20a with which the spherical end 19a of the corresponding motor plunger 19 is engaged.

The spherical concave portions 10a, 20a are formed with a radius larger than the radius of the corresponding spherical end portions 9a, 19a, and the engagement state with the spherical end portions 9a, 19a is secured at any position. It is like this.

Further, in the hydraulic motor M, in order to particularly ensure the torque transmission between the motor plunger 19 and the motor swash plate 20,
The partition wall 20b between the spherical recesses 20a, 20a is formed in a mountain shape protruding toward the central portion in the radial direction (see FIGS. 11 to 13). Incidentally, such a structure may be adopted also on the hydraulic pump P side.

2 to 5, in the cylinder block B, the output shaft 31 is centered between the cylinder holes 8, 8 ... Group of the pump cylinder 7 and the cylinder holes 18, 18 ... Group of the motor cylinder 17. Cylinder holes 8, 8 ... and 18, 18 radially penetrating the concentric annular inner oil passage 52 and outer oil passage 53, and the annular partition wall between both oil passages 52, 53 and the outer peripheral wall of the outer oil passage 53.
The same number as the first valve holes 54, 54 and the second valve holes 55, 5 respectively.
5 ..., the cylinder ports 8, 8 ... And the first valve holes 54, 54 ... Which communicate with each other, and the pump ports a, a ..., The cylinder holes 18, 18 ... And the second valve hole 55 which are adjacent to each other. A large number of motor ports b, b ... Which communicate with each other, are provided.

The inner oil passage 52 is formed as an annular groove on the inner peripheral surface of the cylinder block B, and the open surface thereof is closed by the outer peripheral surface of the output shaft 31.

The first valve holes 54, 54 ... Have spool-type first distribution valves 61, 61.
, And the second valve holes 55, 55 are also slidably fitted with spool type second distribution valves 62, 62, respectively. And
The first eccentric ring 63 surrounding the first distribution valves 61, 61 ...
However, a second eccentric ring 64 surrounding the second distribution valves 62, 62 ... Is engaged via ball bearings 65, 66, respectively. Distribution valve
The outer ends of the 61, 61 ... Are connected to each other by a first compulsory wheel 67 that is concentric with the first eccentric ring 63, and the outer ends of the second distributing valves 62, 62 ... Are the second eccentric wheels 62, 62. Second forced wheel 68 concentric with ...
Are connected to each other by.

The first eccentric wheel 63 is fixed to the outer periphery of the input cylinder shaft 5 via a connecting pin 69, and as shown in FIG. 4, the virtual trunnion axis O ₁
Is held at a position eccentric by a predetermined distance ε ₁ from the center of the output shaft 31.

When a relative rotation occurs between the input cylinder shaft 5 and the pump cylinder 7, each first distribution valve 61 is moved to the first eccentric ring 63 by the first eccentric ring 63.
The valve hole 54 is reciprocated between the radially inner position and the outer position of the pump cylinder 7 with a stroke that is twice the eccentricity ε ₁ . Then, as shown in FIG. 4, in the discharge region D of the hydraulic pump P, the first distribution valve 61 moves toward the inner position side and the corresponding pump port a is moved to the outer oil passage 53.
To the inner oil passage 52 and the pump plunger 9 during the discharge stroke from the cylinder hole 8 to the outer oil passage 53.
Oil is pumped to the first distribution valve in the suction area S.
Reference numeral 61 moves to the outer position side so that the corresponding pump port a communicates with the inner oil passage 52 and does not communicate with the outer oil passage 53. The pump plunger 9 during the suction stroke causes the inner oil passage 52 to move.
The hydraulic oil is sucked into the cylinder hole 8 from.

The second eccentric ring 64, as shown in FIGS. 5 and 6,
The cylinder holder 24 is connected via a pivot 30 parallel to the output shaft 31 so as to be swingable between a clutch-on position n and a clutch-off position f. The second eccentric wheel 64 occupies a position eccentric by a predetermined distance ε ₂ from the center of the output shaft 31 along the trunnion axis O ₂ at the clutch-on position n, and at the clutch-off position f from the center of the output shaft 31 to the above. A distance ε ₃ larger than the eccentricity ε ₂ occupies an eccentric position, and notches 71 are provided on the outer peripheral surface of the second eccentric ring 64 for restricting the position, and both inner end surfaces of the notch 71 are provided. A stopper 72 capable of contacting is integrally formed with the casing 4.
That is, the clutch-on position n of the second eccentric wheel 64 is brought into contact with one inner end surface of the notch 71, and the clutch on position n of the second eccentric wheel 64 is brought into contact with the other inner end surface of the notch 71. The off position f is regulated, respectively.

The output shaft is formed in the through hole 73 formed in one side of the second eccentric ring 64.
The cam shaft 74, which is arranged in parallel with 31, is inserted through the cam shaft 74.
A slipper plate 75 engaging with 74 is fixed to the second eccentric ring 64 with a bolt 76 so as to cover one side surface of the through hole 73.

As shown in FIG. 3, the cam shaft 74 is supported by the casing 4 via a pair of left and right ball bearings 77, and is rotated by the operation of a clutch lever (not shown) to rotate the slipper plate.
By pushing 75, the second eccentric wheel 64 can be swung to the clutch-off position f.

As shown in FIG. 5, the second eccentric wheel 64 is connected to a clutch spring 78 that biases the second eccentric wheel 64 toward the clutch-on position n. Therefore, if the cam shaft 74 is operated so as to retract from the slipper plate 75, the second eccentric wheel 64 will move to the clutch spring 78.
Can be swung to the clutch-on position n.

Thus, when the second eccentric wheel 64 occupies the clutch-on position n (see FIG. 5), when the motor cylinder 17 rotates, each second distribution valve 62 causes the second eccentric wheel 64 to move the second valve hole. At 55, the stroke is made to reciprocate between the radially inner position and the outer position of the motor cylinder 17 with a stroke that is twice the eccentric amount ε ₂ . In the expansion region Ex of the hydraulic motor M, the second
The distribution valve 62 moves to the inner position side so that the corresponding motor port b communicates with the outer oil passage 53 and the inner oil passage 52 does not, so that the motor plunger in the expansion stroke from the outer oil passage 53 is closed.
High-pressure hydraulic oil is supplied to the cylinder hole 18 of 19, and in the contraction region Sh, the second distribution valve 62 moves to the outer position side so that the corresponding motor port b communicates with the inner oil passage 52. The hydraulic fluid is discharged from the cylinder hole 18 of the motor plunger 19 to the inner oil passage 52 during the contraction stroke by making the outer oil passage 53 incommunicable.

Further, when the second eccentric wheel 64 occupies the clutch-off position f (see FIG. 6), when the motor cylinder 17 rotates, each second distribution valve 62 causes the second eccentric wheel 64 to move in the second valve hole 55. The distance between the eccentricity ε _{3 and} the double stroke is reciprocated between the radially inner position and the outer position of the motor cylinder 17, and at the inner and outer positions of the motor cylinder 17, the second distribution valve 62 has the outer oil passage 53. Is opened to the outside of the cylinder block B.

In the above configuration, the second eccentric wheel 64 is connected to the clutch on position n.
When the input cylinder shaft 5 of the hydraulic pump P is rotated from the primary reduction gear device 2 while being held at 1, the discharge and suction strokes are alternately given to the pump plungers 9, 9 ... By the pump swash plate 10.

The pump plunger 9 pumps the working oil from the cylinder hole 8 to the outer oil passage 53 while passing through the discharge region D, and sends the working oil from the inner oil passage 52 to the cylinder hole 8 while passing through the suction region S. Inhale.

The high-pressure hydraulic oil sent to the outer oil passage 53 is in the expansion hole Ex of the hydraulic motor M and is located in the cylinder hole 18 of the motor plunger 19.
On the other hand, the hydraulic oil is discharged from the cylinder hole 18 to the inner oil passage 52 by the motor plunger 19 existing in the contraction area Sh.

During this time, the reaction torque that the pump cylinder 7 receives from the pump swash plate 10 via the pump plunger 9 in the discharge stroke,
The cylinder block B is rotated by the sum of the reaction torque that the motor cylinder 17 receives from the motor swash plate 20 via the motor plunger 19 in the expansion stroke, and the rotation / torque is transmitted from the output shaft 31 to the secondary reduction gear 3. It

In this case, the gear 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 1 to a certain required value. Moreover, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, the motor swash plate is
The gear ratio can be controlled steplessly from 1 to a certain value by tilting from 20 upright positions to a certain tilt position.

During operation of the transmission T, the pump swash plate 10 moves to the pump plunger 9,
9 ... from the group, and the motor swash plate 20 is the motor plunger 19,19
… Thrust loads in opposite directions from the group,
The thrust load received by the pump swash plate 10 is supported by the output shaft 31 via the angular contact bearing 11, the pump swash plate holder 12, the thrust roller bearing 40 and the flange 37, and the thrust load received by the motor swash plate 20 is the angular contact bearing. 21, the motor swash plate holder 22, the motor swash plate anchor 23, the thrust roller bearing 47, the support cylinder 45, and the cotter 44 are supported by the output shaft 31. Therefore, the thrust load only causes tensile stress on the output shaft 31, and does not act on the casing 4 supporting the shaft 31 at all.

In this case, the motor swash plate holder 22 is
Is supported via the thrust roller bearing 21 and the back surface is supported by the motor swash plate anchor 23, so that even if a thrust load is applied from the motor plungers 19, 19 ... There is no. Moreover,
The motor swash plate holder 22 and the motor swash plate anchor 23 oppose the spherical surfaces f ₁ and f ₂ centering on the intersection of the axis of the motor cylinder 17 and the trunnion axis O ₂ , so that the interaction of these spherical surfaces causes the motor to move. The swash plate holder 22 has a centering function. As a result, the motor swash plate holder 22 is
It can smoothly rotate around O _2, and the tilt angle of the motor swash plate 20 can be easily controlled. At that time, the trunnion shaft 22a of the motor swash plate holder 22 and the recess 2 of the motor swash plate anchor 23
The engagement with 3a prevents rotation of the motor swash plate holder 22 around axes other than the trunnion axis O ₂ . Further, since the motor swash plate anchor 23 having the concave spherical surface f ₂ becomes thicker from the central portion toward the peripheral edge and has high rigidity, it can sufficiently withstand a large load from the motor swash plate holder 22 and the thrust roller bearing 47. be able to.

Further, the partition wall 20b between the spherical recesses 20a, 20a on the motor swash plate 20 is separated.
Is formed in a mountain shape, the spherical recess 20a and the motor plunger 1 can be formed without forming the entire motor swash plate 20 to be thick.
The effective engagement depth of the spherical end 19a of 9 can be set to a large value, so that the motor plunger 19
Can reliably rotate and drive the motor swash plate 20 without slipping out of the spherical recess 20a.

Furthermore, in the hydraulic pump P and the hydraulic motor M, each swash plate 10,20 has a spherical end 9a, 19 of the corresponding plunger 9,19.
Since a and the angular contact bearings 11 and 21 are subjected to the centering action from the front and the rear, it is possible to precisely rotate in synchronization with the cylinder block B while maintaining a fixed position in any inclined state.

During the hydraulic transmission from the hydraulic pump P to the hydraulic motor M, if the second eccentric wheel 64 is swung to the clutch off position f, the second distribution valve 62 opens the high pressure outer oil passage 53 to the outside of the cylinder block B. Therefore, high-pressure hydraulic oil is not supplied to the hydraulic motor M, and power transmission between the hydraulic pump P and the hydraulic motor M is cut off. That is, a so-called clutch-off state is obtained.

In FIGS. 1, 2, and 10, the trunnion shaft is shown.
A gear change control device C for controlling the angle of the motor swash plate 20 is connected to 22a.

The speed change control device C includes a reversible electric motor 80 such as a pulse motor or a DC motor, a reduction gear device 81 connected to the electric motor 80, and a ball nut mechanism connected to the reduction gear device 81. Equipped with 82. The ball nut mechanism 82 includes a screw shaft 83 and a nut 85 that is screwed onto the screw shaft 83 via a circulating ball 84.
It is connected to the output gear of the reduction gear device 81, and both ends thereof are rotatably supported by the casing 4 via ball bearings 86, 86 '. The nut 85 has a connecting arm 87 on one side, and the connecting arm 87 and a pair of connecting arms 88, 88 projecting from one side of the motor swash plate holder 22 and sandwiching the connecting arm 87 form a trunnion axis O ₂ . They are connected to each other by parallel connecting pins 89. By such a connection, the nut 85 is prevented from rotating around the screw shaft 83.

By rotating the electric motor 80 in the normal direction, the screw shaft 83
When the nut is rotated normally, the nut 85 moves to the left in FIG.
And 88 to connect the motor swash plate holder 22 to the trunnion axis O ₂
It is possible to rotate around and raise the motor swash plate 20,
On the contrary, if the electric motor 80 is rotated in the reverse direction, the nut 85 moves to the right and the motor swash plate 20 can be tilted.

In FIGS. 3 and 10, a rotary potentiometer 111 for detecting the tilt angle of the motor swash plate 20 and sending a control signal to various control devices is attached to the casing 4. The potentiometer 111 is provided with a lever 113 at the tip of a rotary shaft 112, and the lever 113 is engaged with an engagement groove 114 formed in one trunnion shaft 22a of the motor swash plate holder 22. Therefore, when the motor swash plate holder 22 is rotated to tilt the motor swash plate 20, the rotary shaft 112 is rotated via the lever 113 accordingly, and the potentiometer 111 controls according to the angle of the motor swash plate 20. The signal is output.

In FIGS. 2, 3, and 9, a central oil passage 90 is bored in the center of the output shaft 31, one end of which is closed by the bolt 49 and the other end is opened as an inlet. The oil filter 91 facing the is attached to the cap 50.

The inlet of the central oil passage 90 is an oil passage 92 formed in the casing 4.
Through the oil reservoir 93 at the bottom of the casing 4 through the oil passage 92
In the middle of, the gears fixed to the pump swash plate holder 22
A replenishment pump 95 driven by 94 is provided. Therefore, while the engine E is rotating, the oil in the oil sump 93 is continuously supplied to the central oil passage 90 by the replenishment pump 95.

A valve cylinder 100 having both ends opened is fitted in the central portion of the central oil passage 90, and the valve cylinder 100 is fixed to the output shaft 31 by penetrating a fixing pin 101 press-fitted on its diameter line. The fixed pin 101 is a hollow portion 102 having both ends open to the inner oil passage 52,
And a plurality of through holes for communicating the hollow portion 102 with the inside of the valve cylinder 100.
It has 103, 103 ... Therefore, the central oil passage 90 and the inner oil passage 52 are communicated with each other via the valve cylinder 100 and the fixing pin 101.

On the outer peripheral surface of the valve cylinder 100, chamfered portions 104, 104 that connect the upstream side and the downstream side of the central oil passage 90 are formed.

Further, in the valve cylinder 100, a pair of first check valves 105, 105 that prevent the reverse flow of oil from the inner oil passage 52 to the central oil passage 90 are provided on the fixed pin 1.
The check valves 105 are arranged symmetrically with respect to 01, and each check valve 105 has a valve spring 106.
Is always urged in the valve closing direction.

In addition, the output cylinder 31 and the cylinder block B have a valve cylinder 100
A series of replenishment oil passages 107 that connect the more upstream central oil passage 90 and the outer oil passages 53 are provided. In the middle of the replenishment oil passages 107, oil from the outer oil passages 53 to the central oil passages 90 is provided. A second check valve 108 for preventing backflow is interposed, and the check valve 108 is a valve spring 109.
Is always urged in the valve closing direction.

Further, the output shaft 31 is provided with radial orifice holes 110 for supplying lubricating oil from the central oil passage 90 to the respective parts of the transmission T in appropriate positions.

Thus, during normal load operation in which the hydraulic motor P is hydraulically driven by the hydraulic pump P, the pressure in the low-pressure side inner oil passage 53 is changed to the pressure in the central oil passage 90 due to oil leakage from the hydraulic closed circuit between them. When the pressure drops below the lower limit, the first check valves 105, 105 open and the central oil passage
The hydraulic oil is supplied from 90 to the inner oil passage 52. 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 central oil passage 90 by the second check valve 108.

Further, during reverse load operation, that is, during engine braking, the hydraulic motor M acts as a pump and the hydraulic pump P acts as a motor, so that the outer oil passage 53 changes to a low pressure and the inner oil passage 52 changes to a high pressure. Therefore, if the pressure in the outer oil passage 53 becomes lower than the pressure in the central oil passage 90 due to the oil leakage, the second check valve 108 opens and the working oil is replenished from the central oil passage 90 to the outer oil passage 53, so that the inner oil Outflow of hydraulic oil from the passage 52 to the central oil passage 90 is blocked by the first check valves 105, 105.

Further, since the oil in the central oil passage 90 is supplied to each part of the transmission T while the flow rate is restricted by the orifice hole 110, the pressure in the central oil passage 90 does not excessively decrease due to the supply, and therefore Oil passage 90 to inner oil passage 52 and outer oil passage
It does not hinder the supply of hydraulic oil to 53.

The cylinder block B is also provided with an inflation pressure valve 120 that prevents the hydraulic pressure in the outer oil passage 53 from rising excessively.

The pressure regulating valve 120 includes a valve cylinder 121, a valve body 122 and a valve spring 123.

The valve cylinder 121 includes a partition between the inner and outer oil passages 52 and 53 and an outer oil passage 53.
Are press-fitted into the peripheral walls of the so as to penetrate them radially. This valve cylinder 121 has a lateral hole 124 that opens to the outer oil passage 53,
A vertical valve hole 1 communicating between the lateral hole 124 and the outer oil passage 53.
25, and slightly larger than this valve hole 125, from the lateral hole 124 to the valve hole 125
A guide hole 126 extending in the opposite direction and a large diameter spring chamber 127 connected to the guide hole 126 are provided.

The valve body 122 may abut a valve portion 122a that faces the lateral hole 124 and slides in the valve hole 125, a valve rod portion 122b that slides in the guide hole 126, and a step portion between the guide hole 126 and the spring chamber 127. It has a flange-shaped stopper portion 122c, and the stopper portion 122c is normally held at the contact position with the step portion by a valve spring 123 housed in a spring chamber 127. The spring chamber 127 communicates with the inner oil passage 52 so as not to interfere with the operation of the valve body 122.

Thus, the oil pressure of the outer oil passage 53 is applied to the step surface between the valve portion 122a and the valve rod portion 122b, and the valve opening force is given to the valve body 122, but the oil pressure of the outer oil passage 53 is below a specified value. In a normal operating state, the force of the valve spring 123 for urging the valve body 122 in the valve closing direction is larger than the valve opening force.
That is, the valve hole 125 is kept closed. When the oil pressure in the outer oil passage 53 exceeds the specified value, the valve opening force increases more than the force of the valve spring 123, so the valve body 122 slides while compressing the valve spring 123 to open the valve, that is, the valve. The hole 125 is opened, and the excessive hydraulic pressure of the outer oil passage 53 is discharged to the outside of the cylinder block B through the valve hole 125. Then, when the oil pressure in the outer oil passage 53 returns to the specified value, the valve body 122 returns to the closed state again by the force of the valve spring 123. Therefore, even when the vehicle suddenly starts and accelerates, it is possible to suppress an excessive increase in the hydraulic pressure in the outer oil passage 53.

The cylinder block B is further provided with a throttle hole 128 that communicates between the inner oil passage 52 and the central oil passage 90 in order to prevent the hydraulic pressure of the inner oil passage 52 from rising excessively. Therefore, it is possible to prevent the oil pressure in the inner oil passage 52 from rising excessively even during sudden engine braking.

Referring again to FIG. 2, the flange 37 integral with the output shaft 31 is
A large number of teeth 117 are engraved on the outer circumference and are also used as a pulse motor, and a pickup coil 118 facing the outer circumference is screwed to the casing 4. The pickup coil 118 generates a pulse according to the rotation of the output shaft 31, which is converted into a current or a voltage and displayed as a vehicle speed on a speedometer (not shown).

2 and 15 to 18, the starting device St
Has a kick shaft 130 rotatably supported on the casing 4 via a needle bearing 131 coaxially with the crankshaft 1 of the engine E, and a kick pedal 132 is connected to the outer end of the shaft 130.

At the inner end of the kick shaft 130, a carrier 134 that is supported by the casing 4 via a ball bearing 133 is integrally connected, and the three planetary gears 135 that are axially supported by the carrier 134 are provided with them. Ring gear 136 surrounding
And the sun gear 137 surrounded by them meshes with each other. The ring gear 136 is fixed to the casing 4 with a bolt 138, and the sun gear 137 is integrally formed with a starting shaft 140 slidably fitted in a guide hole 139 provided at the center of the kick shaft 130. Therefore, sun gear 137 is planetary gear 1
Can slide axially with respect to 35 ...

A drive ratchet 141 that can be engaged and disengaged with a driven ratchet 142 that is fixed to the right end of the crankshaft 1 is fixed to the tip of the sun gear 137. An annular groove 1 is formed on the outer circumference of the drive ratchet 141.
43 is provided, and the control plate 144 is engaged with the groove 143 so as to be relatively rotatable. Such engagement is performed through the important notch 145 reaching from the outer peripheral surface of the control plate 144 to the center thereof. Further, three small notches 146 are provided at equal intervals on the outer periphery of the control plate 144, and these small notches 146 ,.
The three leg pieces 147 protruding from the carrier 134 are engaged with each other so as to be slidable in the axial direction.

Further, the control plate 144 has an arm portion 144a that projects outward in the radial direction.
And is adapted to be engaged with and disengaged from the cam surface 148a of the cam plate 148. The cam plate 148 is fixed to the inner wall of the casing 4 by the bolt 148, and its cam surface 148a.
Has an inclined surface that allows the control plate 144 to move in the axial direction toward the crankshaft 1 side as the control plate 144 rotates in the cranking direction R of the crankshaft 1.

A return spring 150 is connected to the kick shaft 130 to urge the kick shaft 130 to rotate in the counter cranking direction R.
A pushing spring 151 for urging the starting shaft 140 toward the crankshaft 1 is contracted between the starting shaft 140 and the starting shaft 140.

Then, if the kick shaft 130 is rotated in the cranking direction R against the force of the return spring 150 by the operation of the kick pedal 132, the planetary gear 1 rotates as the carrier 134 rotates.
35 ... rotates while revolving along the ring gear 136, and drives the sun gear 137 to speed up in the cranking direction R.
The starting shaft 140 and the drive ratchet 141 are similarly driven.

On the other hand, the control plate 144 rotates in the cranking direction R together with the carrier 134, and when the arm portion 144a is disengaged from the cam surface 148a of the cam plate 148, the starter shaft 140 advances toward the crankshaft 1 by the force of the pushing spring 151. Then, the drive ratchet 141 is engaged with the driven ratchet 142. Therefore both ratchets 1
The rotational force of the starting shaft 140 is transmitted to the crankshaft 1 via 41 and 142 and cranks it, so that the engine E can be started.

When the engine E is started, the driven ratchet 142 bounces the drive ratchet 141 in the axial direction, so that the rotation of the crankshaft 1 is not transmitted to the starting shaft 140 side. Thereafter, when the kick pedal 132 is released, the kick shaft 130, the carrier 134 and the control plate 144 are rotated in the anti-cranking direction by the returning force of the return spring 150, and the arm portion 144a of the control plate 144 is moved to the cam surface 1.
When engaged with 48a, the control plate 144 is retracted by the guiding action of the cam surface 148a, and at the same time, the drive ratchet 141 and the starting shaft 140 are retracted against the force of the pushing spring 151, so that the drive ratchet 141 is driven. It can be completely removed from 142.

As described above, the adoption of the planetary gear mechanism 152 including the planetary gear 135, the sun gear 137, and the ring gear 136 allows the kick shaft 130 coaxially arranged with the crank shaft 1 to drive the crank shaft 1 at an increased speed.
Can be compactly laid on one side of the engine E without interfering with the continuously variable transmission T.

C. Effects of the Invention As described above, according to the present invention, since the partition walls between the spherical concave portions of the swash plate are formed in a mountain shape protruding toward the central portion in the radial direction, the entire swash plate is not formed to be thick. It is possible to increase the effective engagement depth between the spherical concave portion and the spherical end of the plunger, thus ensuring the synchronous rotation of the swash plate and the plunger group, and at the same time, the swash plate and thus the entire device. It is possible to contribute to the weight reduction of.

[Brief description of drawings]

The drawings show one embodiment of the present invention. Fig. 1 is a plan view of a power unit for a motorcycle, Fig. 2 is an enlarged vertical plan view of an essential part of Fig. 1, and Fig. 3 is III of Fig. 2. -III sectional view, FIG. 4 is a sectional view taken along the line IV-IV of FIG. 3, and FIG. 5 is a sectional view taken along the line VV of FIG.
The drawing is a sectional view similar to FIG. 5 showing the clutch off state, FIG. 7 is a front view of the second distributing valve, and FIG. 8 is VIII-VI of FIG.
II line sectional view, FIG. 9 is an enlarged view of a main part of FIG. 3, FIG. 10 is a sectional view taken along line XX of FIG. 3, FIG. 11 is a plan view of a motor swash plate, FIG. Figure 13 shows lines XII-XII and XIII- in Figure 11.
XIII line sectional view, FIG. 14 is an exploded perspective view of the main part of FIG.
15 and 16 are sectional views taken along line XV-XV and XVI-XVI in FIG. 2, FIG. 17 is sectional view taken along line XVII-XVII in FIG. 16, and FIG.
FIG. 17 is an exploded perspective view of a main part of FIGS. 15 and 16. M: hydraulic motor as a hydraulic device, 17: cylinder,
18 ... Cylinder hole, 19 ... Plunger, 19a ... Spherical end, 20 ... Swash plate, 20a ... Spherical recess, 20b ... Partition wall

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mitsuru Saito 1-4-1 Chuo, Wako-shi, Saitama Inside the Honda R & D Co., Ltd. (72) Inventor Kenji Sakakibara 1-4, Chuo, Wako-shi, Saitama No. 1 Stock Company Honda Technical Research Institute

Claims (1)

[Claims] 1. A cylinder having a large number of cylinder holes arranged in parallel to and surrounding the axis of rotation and annularly surrounding the same; a plurality of plungers slidably fitted in the cylinder holes to project spherical ends from one end surface of the cylinder. And a swash plate holder that is arranged to face one end surface of the cylinder and is rotatable relative to the cylinder; one end surface of the swash plate holder is rotatably supported by the swash plate holder;
In a swash plate type hydraulic device equipped with a swash plate having a large number of spherical recesses that engage with the spherical ends of the plungers on the other end surface, a partition wall between the spherical recesses in the swash plate is raised toward the center in the radial direction. A swash plate type hydraulic system characterized by being formed in a mountain shape.