JPH0788882B2 - Hydraulic transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Objects of the Invention (1) Field of Industrial Application The present invention relates to a hydraulic pump, a large number of motor plungers slid on a motor cylinder, and a motor swash plate for receiving those motor plungers. The present invention relates to a hydraulic transmission in which a sliding surface is connected to a hydraulic motor to which oil in a motor cylinder is supplied so as to lubricate the sliding surface in a closed hydraulic circuit.

(2) Conventional Technique Conventionally, such an oil chamber type transmission device is disclosed in, for example, Japanese Patent Laid-Open No. 57-76.
It is known from, for example, Japanese Patent No. 357.

(3) Problems to be Solved by the Invention In such a device, when the number of rotations of the hydraulic motor increases, the amount of heat generated on the sliding surfaces of the motor swash plate and the motor shoe increases, resulting in the motor swash plate and the motor shoe. Problems such as seizure and abrasion occur.

In order to eliminate such inconvenience, as disclosed in Japanese Patent Laid-Open No. 61-118566, in particular, FIG. 8, a lubricating chamber surrounding the sliding surfaces of the shoe and the swash plate is provided, and the replenishing pump is provided in the lubricating chamber. It is considered that the cooling oil is pressure-fed.

By the way, a replenishment pump for lubrication conventionally used in a general hydraulic transmission is directly connected to an engine so that each part of the transmission can be constantly lubricated and lubricated even when a driven body (for example, a vehicle) driven by a hydraulic motor is stopped. Alternatively, the structure is such that it is interlocked with the input shaft of the hydraulic pump, and if such a structure is used as it is for supplying oil to the lubricating chamber, there are the following problems. That is, in the hydraulic transmission, the first operating state in which the number of revolutions on the input side becomes significantly higher than that on the output side (for example, in the case of an automobile when accelerating or when engine braking), the input side and It has a second operating state in which the difference in the number of revolutions on the output side is small (for example, when traveling at high speed in the case of an automobile), but in determining the pump capacity of the replenishment pump driven on the input side. In particular, it is necessary to set a large pump capacity so that a sufficient cooling effect can be obtained even in the second operating state where the operating conditions of the pump become severe. However, if the pump capacity is set to be large in this way, especially in the first operating state, the replenishment pump is driven at a high speed even though the amount of heat generated on the sliding surface of the motor swash plate and the motor shoe is relatively small. As a result, the sliding surface becomes overcooled, the temperature of the sliding surface falls too much, and the viscosity of the oil increases, so there is the inconvenience of reducing the mechanical efficiency.

The present invention has been proposed in view of such circumstances, and provides a hydraulic transmission device capable of rational cooling and lubrication according to heat generation of a sliding surface between a motor plunger and a motor swash plate. It is an object.

B. Structure of the Invention (1) Means for Solving the Problems According to the present invention in order to achieve the above object, according to the present invention, the oil tank is surrounded by the sliding surface between the motor swash plate and the motor plunger and through the throttle. There is a lubrication chamber open to the
The output shaft of the hydraulic motor is connected to a supply pump that increases the amount of discharged oil according to the increase in the rotation of the output shaft so as to pump up the oil for lubrication and cooling, and the discharge port of the supply pump is connected to the lubrication chamber. Connected.

(2) Action When the rotation speed of the hydraulic motor is low, the discharge amount of the supply pump is small and a relatively small amount of oil is supplied to the lubrication chamber, while when the rotation speed of the hydraulic motor is high, the discharge amount of the supply pump is large. As a result, a relatively large amount of oil is supplied to the lubrication chamber.

(3) Embodiment Hereinafter, an embodiment in which the present invention is applied to a hydraulic type continuously variable transmission for a vehicle will be described with reference to the drawings. First, referring to FIG. The transmission CVT includes a constant displacement hydraulic pump P and a variable displacement hydraulic motor M connected in a closed hydraulic circuit to form a transmission case 1 in which two case halves 1a and 1b are connected. Housed in.

The hydraulic pump M includes a pump cylinder 4 connected to the input shaft 2 by a spline 3, and a large number of cylinder holes arranged in an annular array in the pump cylinder 4 so as to surround the input shaft 2.
A large number of pump plungers 6,6 that are respectively fitted to 5,5 ...
... and. Power from an engine (not shown) is transmitted to the input shaft 2 via a flywheel 7.

On the other hand, the hydraulic motor M is provided with a motor cylinder 8 concentrically surrounding the pump cylinder 4 of the hydraulic pump P so as to be able to rotate relative thereto, and the motor cylinder 8
, A large number of motor plungers 10, which are slidably fitted into a large number of cylinder holes 9, 9 ...
10 and are provided.

Support shafts 11 and 12 are provided on both ends of the motor cylinder 8 in the axial direction so as to project on the same axis. One support shaft 11 is provided on an end wall of one case half body 1a via a needle bearing 13 and The other support shaft 12 is supported by the end wall of the other case half body 1b via ball bearings 14, respectively.

The input shaft 2 penetrates the end wall of the one case half 1a in an oil-tight manner and is arranged concentrically within the support shaft 11. Moreover, a plurality of needle bearings are provided between the inner surface of the support shaft 11 and the outer surface of the input shaft 2.
15 is interposed so that the input shaft 2 and the pump cylinder 4, and the support shaft 11 and the motor cylinder 8 can rotate relative to each other.

The support shaft 11 functions as an output shaft of the hydraulic motor M, and is rotatably supported by both end walls of the transmission case 1 in parallel with the support shaft 11 via roller bearings 16 and ball bearings 17. A forward and reverse gear unit G is provided between the shaft 18 and the support shaft 11.

The forward and reverse gear device G includes a pair of drive gears 19 and 20 fixed to the support shaft 11 and one drive gear 19 that meshes with the counter shaft 18.
Driven gear 21 rotatably supported on the other side and the other drive gear
Driven gear 22 rotatably supported by counter shaft 18 corresponding to 20
And an intermediate gear 23 that meshes with the drive gear 20 and the driven gear 22.
And a driven clutch toothed wheel 24 fixed to the auxiliary shaft 18 between drive clutch toothed wheels 21a and 22a that are integrally provided at opposing portions of the driven gears 21 and 22, respectively, and the driven clutch 24 and both driving clutch toothed wheels. A clutch member 25 for selectively connecting 21a and 22a is provided, and a shift fork 26 is engaged with each clutch member 25 so as to be selectively operated.

A gear 28 meshed with the input gear 27 of the differential device D is attached to the counter shaft 18.
Are integrally provided, and the differential device D is switched and driven in the forward direction and the reverse direction of the vehicle in accordance with the operation of the clutch member 25.

In FIG. 2, an oil-tight chamber 31 is defined between the motor cylinder 8 and the pump cylinder 4 of the hydraulic pump P. Inside the oil-tight chamber 31, inside the motor cylinder 8, the end face of the pump cylinder 4 is formed. Opposing pump swash plates 32 are supported. The pump swash plate 32 is in sliding contact with an annular pump shoe 33.

Each pump plunger 6, 6 and the pump shoe 33 are swingably connected via a connecting rod 44, and the inner peripheral step of the pump shoe 33 is connected to the motor cylinder 8 via a roller bearing 42. The presser ring 34 supported is abutted,
Further, a spring holder 35 connected to the input shaft 2 via a spline 36 abuts on the holding ring 34 in order to allow axial movement and prevent rotation of the tank body. Also spring holder 35
A coil spring 37 surrounding the input shaft 2 is interposed between the pump cylinder 4 and the pump cylinder 4. The spring force of the coil spring 37 causes the spring holder 35 to press the pump shoe 33 through the press ring 34.
Is elastically pressed toward the pump swash plate 32. Moreover, the spring holder 35 and the pressing ring 34 are in spherical contact with each other, and the spring holder 35 is evenly contacted with the pressing ring 34 to transmit the elastic force of the coil spring 37 to the pressing ring 34.

The oil-tight chamber 31 is partitioned by the pump shoe 33, the pressing ring 34 and the spring holder 35 into a first chamber 31a on the pump swash plate 32 side and a second chamber 31b on the pump cylinder 4 side.

The inner peripheral side of the sliding surface between the pump swash plate 32 and the pump shoe 33 faces the first chamber 31a, and the lubricating oil leaking from the sliding surface flows out into the first chamber 31a. By the way, in order to achieve lubrication between the pump swash plate 32 and the pump shoe 33, an annular hydraulic pocket 38 is provided on the front surface of the pump shoe 33. The hydraulic pocket 38 includes the pump shoe 33 and the connecting rod 44.
And each of the pump plungers 6 and the pump cylinders 4 through the oil holes 39, 40, 41 formed in the pump plungers 6.
It communicates with the pump chamber 45 defined between them. Therefore, the pressure oil in the pump chamber 45 is supplied to the hydraulic pocket 38 through the oil holes 41, 40, 39. As a result, the sliding surfaces of the pump shoe 33 and the pump swash plate 32 are lubricated. At the same time, the hydraulic pressure of the hydraulic pocket 38 exerts pressure on the pump shoe 33 so as to receive the projecting thrust of the pump plunger 6, so that the contact pressure between the pump shoe 33 and the pump swash plate 32 is reduced.

On the other hand, the motor cylinder 8 and the pump swash plate 3 are arranged so as to face the outer peripheral side of the sliding surface between the pump swash plate 32 and the pump shoe 33.
2.By pump shoe 33 and roller bearing 42,
An annular lubricating chamber 43 surrounding the sliding surface is defined, and the lubricating chamber 43 constitutes a part of the second chamber 31a.

In the lubrication chamber 43, the pressure oil in the hydraulic pocket 38 is
The oil constantly leaks through the sliding surface between the pump 33 and the pump swash plate 32, and the leaked oil fills the lubricating chamber 43 and then flows through the roller bearing 42 to the second chamber 31b side. Therefore, new lubricating oil is always retained in the lubrication chamber 43, and the sliding surface of the pump shoe 33 and the pump swash plate 32 can be reliably lubricated from the outside of the pump shoe 33 by the oil.

In addition to the oil from the lubrication chamber 43, the oil leaked from the sliding surfaces of the pump plunger 6 and the cylinder hole 5 and the sliding surfaces of the pump cylinder 4 and the distribution board 46 flows into the second chamber 31b. .

A communication passage 47 that communicates between the first chamber 31a and the second chamber 31b is bored in the spring holder 35. Further, a first discharge path 48 communicating with the first chamber 31a is formed between the support shaft 11 of the motor cylinder 8 and the input shaft 22, and the first discharge path 48 is formed by the second discharge path 4
9. Connected to the third discharge passage 51 via the pressure control valve 50.

In FIG. 3, the pressure control valve 50 includes a bottomed cylindrical spool valve body 52 for switching communication and disconnection between the second and third discharge passages 49 and 51, and a spool valve body 52 provided in the closing direction. And a biasing spring 53. A bottomed hole 54 parallel to the input shaft 2 is formed on the end side of the case half 1a in the mission case 1, and the spool valve body 52 is provided with an oil chamber 55 between the closed end of the bottomed hole 54 and the spool valve body 52. And is fitted into the bottomed hole 54. Further, a support member 57 whose movement toward the open end side of the bottomed hole 54 is restricted by a retaining ring 56 fitted in the bottomed hole 54 is inserted into the bottomed hole 54. A spring 53 is interposed between the spool valve element 52 and the spool valve element 52. Therefore, the spool valve element 52 is
It slides due to the balance between the force in the valve opening direction due to the hydraulic pressure of 55 and the force in the valve closing direction due to the spring 53.

The oil chamber 55 is communicated with the second discharge passage 49 formed in the end wall of the case half 1a. In the middle of the bottomed hole 54, there is provided an annular groove 58 for switching between the communication with the oil chamber 55 and the shutoff state by the spool valve body 52, and the third discharge passage 51 formed in the end wall is provided. It communicates with the annular groove 58.

Therefore, the pressure control valve 50 has an oil chamber 55, that is, an oil tight chamber 31.
When the hydraulic pressure of is greater than the value set by the spring 53, the valve is opened to regulate the hydraulic pressure of the oil-tight chamber 31 to a predetermined value.

Bevel gears 61, 62 meshing with each other are fixedly provided at the opposite ends of the pump cylinder 4 and the pump shoe 33. These bevel gears 61, 62 are formed as synchronous gears having the same number of teeth, and when the pump cylinder 4 rotates together with the input shaft 2, the pump shoe 33 is driven to rotate synchronously via the bevel gears 61, 62. It As a result, the pump plunger 6 running on the upside of the inclined surface of the pump swash plate 32 is given a discharge stroke from the pump swash plate 32 via the connecting rod 44, and the pump plunger 6 running on the downside of the inclined surface is Given an inhalation stroke.

In the hydraulic motor M, an annular motor swash plate 63 that faces the motor cylinder 8 is fitted to an annular swash plate holder 64. The swash plate holder 64 integrally includes a pair of trunnion shafts 65 projecting to both outer sides thereof, and the trunnion shafts 65 are pivotally supported by the mission case 1. Therefore, the motor swash plate 63 can be tilted around the axis of the trunnion shaft 65 together with the swash plate holder 64.

The tip of each motor plunger 10 is swingably connected to a plurality of motor shoes 66 that are in sliding contact with the motor swash plate 63. Moreover, in order to maintain the sliding contact state of each motor shoe 66 with the motor swash plate 63, a holding plate that presses the back surface of each motor shoe 66.
67 is rotatably supported by a ring 69 fixed to the swash plate holder 64 with bolts 68. The connecting portion between each motor shoe 66 and each motor plunger 10 has a holding plate at a plurality of circumferential positions.
It penetrates through 67, so that the holding plate 67 rotates together with the motor shoe 66.

Each motor shoe 66 is provided with a hydraulic pocket 70 on the front surface that is in sliding contact with the motor swash plate 63. On the other hand, each cylinder hole 9
A hydraulic chamber 71 defined between the closed end of the motor plunger 10 and each motor plunger 10 is communicated with the hydraulic pocket 70 through a series of oil holes 72, 73 formed in the motor plunger 10 and the motor shoe 66. . Therefore, the pressure oil in the hydraulic chamber 71 is
It is supplied to the hydraulic pocket 70 through 3 and exerts pressure on the motor shoe 66 so as to receive the protruding thrust of the motor plunger 10. As a result, the motor shoe 66 and the motor swash plate 63 are
The contact pressure therebetween is reduced, and the sliding surfaces of the motor shoe 66 and the motor swash plate 63 are lubricated.

On the inner peripheral surface of the swash plate holder 64, a cylindrical partition wall body 74 that is opposed to the inner peripheral surface of the pressing plate 67 with a small gap is fitted, and the partition wall body 74, the swash plate holder 64, and the pressing plate. Lubrication chamber 75 surrounding the sliding surface of motor shoe 66 and motor swash plate 63 by 67
Is defined. Thus, the gaps around the presser plate 67 around the pressing plate 67 form a throttle 75a, and the lubrication chamber 75 is connected to the oil tank T via the throttle 75a.
Will be open to the public.

Thus, the pressure oil in each hydraulic pocket 70 is stored in the motor shoe 66.
Also, the oil constantly leaks through the sliding surface of the motor swash plate 63, and the leaked oil fills the lubricating chamber 75 as lubricating oil and then leaks from the throttle 75a around the holding plate 67. Therefore, new lubricating oil is always held in the lubricating chamber 75, and the sliding surface of the motor shoe 66 and the motor swash plate 63 can be reliably lubricated from the outside of the motor shoe 66 by the oil.

In this case, when the pressure in the lubrication chamber 75 approaches the pressure in the hydraulic pocket 70, the fluid bearing function of the hydraulic pocket 70 with respect to the motor shoe 66 is impaired, so the lubrication chamber 75 retains oil while maintaining a pressure state close to atmospheric pressure. Hydraulic pocket 70 to
The clearances around the pressing plate 67 are appropriately selected according to the amount of oil leaked from the.

The mission case 1 is provided with a servomotor 81 for tiltably driving the swash plate holder 64, that is, the motor swash plate 63. The servo motor 81 includes a servo cylinder 82 fixed to the mission case 1 and a servo cylinder 82 for dividing the servo cylinder 82 into a left oil chamber 83 and a right oil chamber 84.
Servo piston 85 sliding on 82 and servo piston 85
Piston rod 86 that is integrally provided in the oil cylinder and pierces the end wall of the servo cylinder 82 on the left oil chamber 83 side in an oil-tight and movable manner.
And the tip portion is slid into a valve hole 87 formed in the servo piston 85 and the piston rod 86, and the servo cylinder
And a pilot valve 88 penetrating an end wall of the right side oil chamber 84 side of 82 in an oiltight and movable manner.

The piston rod 86 is connected to the swash plate holder 64 via a pin 89. An oil passage 90 provided in the servo cylinder 82 is always in communication with the left oil chamber 83, and the hydraulic pressure supplied from the oil passage 90 acts on the servo piston 85. In the servo piston 85 and the piston rod 86, a passage 91 for communicating the right side oil chamber 84 with the valve hole 87 according to the right movement of the pilot valve 88, and the right side oil chamber 84 for the left side oil chamber with the left movement of the pilot valve 88. A passage 92 communicating with 83 is provided. Further, the valve hole 87 communicates with the oil tank at the bottom of the mission case 1 via the return path 93.

The servo piston 85 performs an amplification operation by the hydraulic pressure supplied from the oil passage 90 so as to follow the leftward and rightward movements of the pilot valve 88, whereby the swash plate holder 64, that is, the motor swash plate 63, is at the maximum tilt position shown in the figure. And a right-angled position that is perpendicular to each motor plunger 10. At this time, the motor swash plate 63 reciprocates each motor plunger 10 as the motor cylinder 8 rotates to repeat expansion and contraction. The stroke of the motor plunger 10 depends on the inclination of the motor swash plate 63. Is adjusted steplessly.

A hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M via the distribution board 46 and the distribution ring 97. Thus, when the pump cylinder 4 is rotated by the input shaft 2, the pump chamber of the cylinder 5 accommodating the pump plunger 6 in the discharge stroke
The high-pressure hydraulic oil discharged from 45 is fed to the hydraulic chamber 71 of the cylinder hole 9 accommodating the motor plunger 10 in the expansion stroke. On the other hand, the hydraulic oil discharged from the hydraulic chamber 71 of the cylinder hole 9 accommodating the motor plunger 10 in the contraction stroke returns to the pump chamber 45 of the cylinder hole 5 accommodating the pump plunger 6 in the suction stroke. During this time, the plunger of the discharge stroke
The motor cylinder 8, that is, the support shaft 11 is rotationally driven by the sum of the reaction torque that 10 applies to the motor cylinder 8 via the pump swash plate 32 and the reaction torque that the motor plunger 10 receives from the motor swash plate 63 during the expansion stroke.

In this case, the motor cylinder 8 with respect to the pump cylinder 4
The gear ratio of is given by the following equation.

As is clear from this equation, if the displacement of the hydraulic motor M determined by the stroke of the motor plunger 10 is changed from zero to a certain value, the gear ratio can be changed from 1 to a certain required value.

The motor cylinder 8 is composed of first to fourth portions 8a to 8d divided in the axial direction. The support shaft 11 is integrally provided in the first portion 8a, and the pump swash plate 32 is provided in the first portion 8a. A cylinder hole 9 is provided in each of the second, third and fourth portions 8b-8d. The third portion 8c constitutes the distribution board 46, and the support shaft 12 is integrally provided on the fourth portion 8d.

The first and second portions 8a, 8b are connected by a plurality of bolts 98. Further, the second, third and fourth portions 8b to 8d are integrally coupled by a plurality of bolts 101 in a state where knock pins 99 and 100 are fitted into their respective joints and positioned relative to each other.

The inner end of the input shaft 2 is supported at the center of the distribution board 46 via a needle bearing 105, and the pump cylinder 4 is elastically brought into sliding contact with the distribution board 46 by a spring 37.

A support plate 107 is fixed to the outer surface side of the end wall of the case half 1b with a bolt 106, and a cylindrical fixed shaft 108 protruding into the support shaft 12 of the motor cylinder 8 is attached to the support plate 107. Are fixedly connected. At the inner end of the fixed shaft 108, a distribution ring 97 that slidably contacts the distribution board 46 is eccentrically supported, and the distribution ring 97 allows the fourth portion 8d of the motor cylinder 8 to be supported.
The hollow portion 109 provided in the inner space is partitioned into an inner chamber 110 and an outer chamber 111. On the other hand, the distribution board 46 is provided with discharge and suction ports 112 and 113. The discharge port 112 communicates the pump chamber 45 of the pump plunger 6 with the inner chamber 110, and the suction port 113 sucks the suction stroke. The pump chamber 45 of the pump plunger 6 and the outer chamber 111 are communicated with each other. The distribution board 46 also has a large number of communication ports 114,114.
Are bored, and the hydraulic chambers 71 of the motor cylinder 8 are communicated with the inner chamber 110 or the outer chamber 111 by these communication ports 114, 114.

Therefore, when the pump cylinder 4 rotates, the high-pressure hydraulic oil generated by the discharge stroke of the pump plunger 6 flows into the inner chamber 110 from the discharge port 112, and
The thrust is applied to the motor plunger 10 by causing it to flow into the hydraulic chamber 71 of the motor plunger 10 in the expansion stroke via the communication port 114 in communication with the 110. On the other hand, the hydraulic oil discharged by the motor plunger 10 in the contraction stroke returns to the pump chamber 45 of the pump plunger 6 in the suction stroke via the communication port 114 and the suction port 113 communicating with the outer chamber 111, and By lubricating the hydraulic oil as described above, the hydraulic pump P as described above is provided.
Is transmitted to the hydraulic motor M.

The side wall of the fixed shaft 108 is provided with, for example, two short-circuit ports 115 capable of communicating between the inner chamber 110 and the outer chamber 111,
Cylindrical clutch valve that opens and closes those short-circuit ports 115 1
16 is rotatably fitted in the fixed shaft 108. The clutch valve 116 is provided with a valve hole 117 corresponding to the short-circuit port 115 on a side wall near the tip thereof, and an operation connecting portion 119 to which an operation shaft 118 connected to a clutch control device (not shown) is connected to a base end portion thereof. To be

Rotate the clutch valve 116 to open the valve hole 117 to the short circuit port 11
When the valve is fully opened, the clutch is off and the valve hole 117
The clutch-on state is obtained when the valve is shifted from the short-circuit port 115 and fully closed, and the half-clutch state is obtained when the valve hole 117 and the short-circuit port 115 are slightly shifted to the half-open state. That is, in the clutch off state, the discharge port 11
The hydraulic oil discharged from 2 to the inner chamber 110 is immediately short-circuited to the outer chamber 11 and the suction port 113 through the short-circuit port 115, and the hydraulic motor M becomes inoperable. In the clutch-on state, the hydraulic oil short-circuits as described above. Is prevented, a circulating action of hydraulic oil from the hydraulic pump P to the hydraulic motor M occurs, and normal transmission is performed.

The clutch valve 116 has a built-in hydraulic servomotor 121 operated by the pilot valve 120.
A valve rod 123 having a diameter smaller than the inner diameter of the clutch valve 116 is provided at the tip portion of 22. The valve rod 123 projects into the inner chamber 110, and has a closing valve 124 for the discharge port 112 at its tip.
Is attached so that it can swing freely. Then, the servo piston 12
The discharge port 112 can be closed by bringing the closing valve 124 into close contact with the distribution board 46 by the left movement of 2. This closing is performed when the motor swash plate 73 is placed in the upright state and the gear ratio is set to 1, whereby the pump plunger 6 is hydraulically locked and the pump cylinder 4 to each pump plunger 6 and the pump swash plate 32 are locked. The motor cylinder 8 can be mechanically driven via the motor, and as a result, the thrust of the motor plunger 10 on the motor swash plate 63 disappears, and the load on the bearings of each part is removed by the thrust.

The fixed shaft 108 and the support plate 107 have an oil passage communicating with the inner chamber 10.
An oil passage 140 communicating with the outer chamber 111 is bored.
Further, the support plate 107 is provided with an oil passage 141 communicating with the oil passage 90 communicating with the servo motor 81, and a switching valve for selectively switching the communication state between the oil passage 141 and the both oil passages 139, 140. 142 is provided. This switching valve 142 is provided on both oil passages 139 and 140.
It operates so that the one with the higher hydraulic pressure is communicated with the oil passage 141. Therefore, the servomotor 81 for tilting the motor swash plate 63 of the hydraulic motor M is supplied with the hydraulic pressure from the higher hydraulic pressure of the inner chamber 110 and the outer chamber 111.

One ends of links 127 and 128 are connected to the pilot valves 88 and 120 of both servo motors 81 and 121, and the other ends of the links 127 are linked and connected to a rotating shaft 129 rotated by an operating means (not shown). Further, a cam 130 is provided on the rotating shaft 129, and a cam follower 131, which is in sliding contact with the cam 130, is provided at the other end of the link 128. As a result, when the servo motor 81 is operated to put the motor swash plate 63 in the upright state, the servo motor 121 operates so that the discharge port 112 is blocked by the blocking valve 124.

A supply pump F is provided outside the end wall of the case half 1a. The replenishment pump F is driven by the input shaft 2 and pumps oil from an oil tank (not shown) at the inner bottom of the mission case 1 to generate hydraulic oil having a constant pressure. The discharge port 136 of the replenishment pump F communicates with an oil passage 137 provided in the input shaft 2, the oil passage 137 communicates with the inner chamber 110 via a check valve 138, and a check valve (not shown) is provided. It communicates with the outer chamber 111 via. Therefore, when the hydraulic oil leaks from the closed hydraulic circuit between the hydraulic pump P and the hydraulic motor M, the leaked amount is compensated for by the supplementary pump F.
Can be automatically replenished from.

A cover 150 that covers the support plate 107, the links 127 and 128, the cam 130, and the like is attached to an end wall of the case half body 1b, and a supply pump 151 that is linked and linked to the output shaft 11 of the hydraulic motor M is used for lubrication and cooling. It is attached to the cover 150 for pumping oil.

The supply pump 151 is, for example, a trochoid pump,
In the pump chamber 154 defined between the cover 150 and the housing 153 mounted on the outer surface of the cover 150 via the seal member 152, the internal gear 155 that is in sliding contact with the inner surface of the pump chamber 154 rotates. Can be stored freely and has internal gear 1
An external gear 156 meshing with 55 is eccentrically housed. On the other hand, a shaft 157 that penetrates the cover 150 in an oil-tight and rotatably manner is integrally provided at the tip of the auxiliary shaft 18 protruding from the end wall of the case half body 1b, and the external gear 156 is attached to the shaft 157. It is fixed. Moreover, the housing 153 is connected to the pump chamber 154.
Two ports 158 and 159 are provided.

The counter shaft 18 rotates in opposite directions when the vehicle is moving forward and when moving backward. Therefore, when one of the ports 158 and 159 functions as an inlet, the other functions as an outlet.

Both ports 158 and 159 are connected to the oil tank 16 via check valves 160 and 161.
Connected to 2. Check valves 160 and 161, ports 158 and 159
The oil is prevented from flowing from the oil tank 162 to the oil tank 162. The oil tank 162 may be provided at the bottom of the mission case 1 or may be provided outside the mission case 1.

The port 158 and the check valve 160, and the port 159 and the check valve 161 are connected to the oil passage 164 via the shuttle valve 163. The shuttle valve 163 operates so as to connect the higher hydraulic pressure of the ports 158 and 159 to the oil passage 164,
Therefore, the oil discharged from the supply pump 151 is guided to the oil passage 164.

On the other hand, in the hydraulic motor M, a notch 76 communicating with the lubricating chamber 75 is provided at the inner peripheral edge of the swash plate holder 64 on the motor swash plate 63 side, and the oil passage 164 is connected to the notch 76.
The oil passage 164 is formed by the trunnion shaft 65 and the trunnion shaft 6.
It is arranged so as to communicate with the notch 76 via the swash plate holder 64 that is integral with the 5, and the oil from the supply pump 151 is supplied to the oil passage 1.
It will be fed to the lubrication chamber 75 via 64 and the notch 76.

Explaining the operation of this embodiment, when the vehicle is traveling at a high speed, that is, when the rotational speed of the hydraulic motor is high, the supply pump 151 is also rotating at a high speed, and a relatively large amount of oil is supplied to the lubricating chamber. Supplied to 75. Therefore, when the amount of heat generated on the sliding surface between the motor swash plate 63 and the motor shoe 66 is large, the sliding surface is cooled and lubricated with a relatively large amount of oil, and the occurrence of wear and seizure is minimized. It can be suppressed.

Further, when the vehicle is traveling at a low speed, that is, when the rotation speed of the hydraulic motor M is low, the amount of oil discharged from the supply pump 151 is small. Therefore, the sliding surface between the motor swash plate 63 and the motor shoe 66 is not excessively cooled.

Such an action is the same when the vehicle is moving backward, and cooling and lubrication can be performed according to a change in the amount of heat generated on the sliding surface according to the number of rotations of the hydraulic motor M.

FIG. 4 shows another embodiment of the present invention, in which the oil passage 16
A cooler 165 is provided in the middle of 4. The capacity of the cooler 165 is set by the flow rate and temperature of the oil passing through the cooler 165 and the proper temperature of the sliding surfaces of the motor swash plate 63 and the motor shoe 66. This is effective when the appropriate temperature is low.

C. Effects of the Invention As described above, according to the present invention, the lubrication chamber that surrounds the sliding surface between the motor swash plate and the motor plunger and is opened to the oil tank through the throttle is provided, and the output of the hydraulic motor is provided. A supply pump that increases the amount of discharge oil according to the rotation increase of the output shaft is linked and connected to the shaft so as to pump up oil for lubrication and cooling, and the discharge port of the supply pump is connected to the lubrication chamber. Even if the amount of heat generated on the sliding surfaces of the motor swash plate and the motor plunger of the hydraulic motor increases as the rotation speed of the motor increases, the amount of oil corresponding to the rotation speed of the hydraulic motor is supplied to the lubrication chamber. Therefore, the cooling and lubrication can be reasonably performed according to the change in the amount of heat generated on the sliding surface, and the overcooling of the sliding surface, which causes a decrease in mechanical efficiency, can be avoided. Further, in the stopped state of the hydraulic motor, the operation of the supply pump can be stopped even if the hydraulic pump is rotating, so that the power loss can be reduced accordingly.

[Brief description of drawings]

1 to 3 show an embodiment of the present invention.
1 is a vertical sectional side view of a vehicle hydraulic continuously variable transmission to which the present invention is applied, FIG. 2 is a partially enlarged view of a hydraulic pump and a hydraulic motor in FIG. 1, and FIG. 3 is an enlarged view of a III part in FIG. 4 is a vertical sectional side view corresponding to FIG. 1 of another embodiment of the present invention. 8 ... Motor cylinder, 10 ... Motor plunger, 11 ...
… Output shaft, 63 …… Motor swash plate, 75 …… Lubrication chamber, 75a ……
Throttle, 151 …… Supply pump, M …… Hydraulic motor, P ……
Hydraulic pump

Continuation of the front page (56) Reference JP-A-61-118566 (JP, A) JP-A-54-134253 (JP, A) JP-A-54-141948 (JP, A)

Claims (1)

[Claims] 1. A sliding surface between a hydraulic pump (P), a large number of motor plungers (10) slid on a motor cylinder (8), and a motor swash plate (63) for receiving those motor plungers (10). In a hydraulic transmission in which a hydraulic motor (M) to which oil in a motor cylinder (8) is supplied to lubricate the hydraulic cylinder (8) is connected in a closed hydraulic circuit, a motor swash plate (63) and a motor plunger ( A lubrication chamber (75) is provided which surrounds the sliding surface between 10) and is opened to the oil tank (T) through a throttle (75a), and the output shaft (11) of the hydraulic motor (M) includes: A supply pump (151) that increases the amount of oil discharged according to the increase in the rotation of the output shaft (11) is linked and linked to pump up oil for lubrication and cooling, and the discharge port of the supply pump (151) is a lubricating chamber. A hydraulic transmission characterized in that it is connected to (75).