JPH02102968A - Oil pump drive structure - Google Patents

Abstract

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

Description

Detailed Description of the Invention A00 Purpose of the Invention (Field of Industrial Application) The present invention relates to an oil pump used for supplying make-up oil to a hydraulic transmission, and more specifically, to an oil pump for supplying supplementary oil to a hydraulic transmission. The present invention relates to a drive structure for an oil pump in which a governor valve for generating governor oil pressure in response to rotation of the drive shaft is attached to the drive shaft.

(Prior art) In a hydraulic transmission, etc., hydraulic oil is supplied to a hydraulic closed circuit including a hydraulic pump and a hydraulic motor that make up the transmission mechanism, and furthermore, hydraulic oil is supplied to hydraulic actuators for controlling each plate, etc. A replenishment pump is provided for such purposes. Such replenishment pumps are disclosed in, for example, Japanese Patent Laid-Open No. 56-52859 and Japanese Patent Laid-Open No. 63-145886.

These replenishment pumps are usually driven by an engine that drives a hydraulic transmission. However, in such transmissions, governor oil pressure corresponding to engine rotation may be used for control purposes, and the governor valve that produces governor oil pressure for this purpose is also arranged so as to be rotationally driven by the engine. It is normal to do so. Therefore, it is preferable to arrange the replenishment pump and the governor valve together so that they are simultaneously driven by the engine using one drive shaft, from the standpoint of making the device more compact.

(Problem to be Solved by the Invention) However, when a replenishment pump and a governor valve are arranged on one drive shaft, a drive gear for transmitting engine rotation must also be arranged on the drive shaft, and the drive shaft There is a problem in that it is difficult to arrange these members upward and to arrange the bearings that rotatably support the drive shaft. for example,
If this arrangement and bearing lubrication are not sufficiently considered, an uneven load may act on the shaft, increasing rotational resistance or causing the shaft to become stiff. There is also a risk that the durability of the bearing will decrease due to insufficient lubrication.

In view of these circumstances, the present invention has been developed to provide an oil pump and a governor valve on one drive shaft so that they can be driven simultaneously. The purpose is to provide a drive structure that will not run out.

1. Structure of the invention (means for solving the problem) In the present invention, as a means to achieve this object,
The drive gear, oil pump, and governor valve are attached to the drive shaft in this order, and the supply of oil to the governor valve and the extraction of oil with governor hydraulic pressure from the governor valve are driven from a port formed between the oil pump and the governor valve. The drive shaft is operated via an oil passage formed within the shaft, and three bearings are installed between the drive gear and the oil pump, between the oil pump and the port, and between the boat and the governor valve. It is configured to rotatably support.

(Function) When the oil pump drive structure with the above configuration is adopted, the drive shaft is supported by the bearings arranged between the drive gear, oil pump, and governor valve nozzle, and the drive shaft and each bearing are biased. It is less likely to be subjected to heavy loads. Additionally, leakage oil from the oil pump and leakage oil from the boat leading to the governor valve ensure that each bearing is lubricated.

(Embodiments) Hereinafter, preferred embodiments of the present invention will be described based on the drawings.

FIG. 1 is a hydraulic circuit diagram of a continuously variable transmission having an oil pump drive structure according to the present invention. Volume type swash plate axial plunger type hydraulic pump P
and a variable displacement swash plate axial plunger type pressure motor M that drives wheels (not shown) via a forward/reverse switching device 20. These hydraulic pump P and hydraulic motor M have a first oil passage La that communicates the discharge port of the pump P and the suction port of the motor M, and a second oil passage Lb that communicates the suction port of the pump P and the discharge port of the motor M. The two oil passages form a hydraulic closed circuit and are connected. These 2
Of the main oil passages La and Lb, the first oil passage La is used when the pump P is driven by the engine E and the motor M is rotationally driven by the oil pressure from the pump P to drive the wheels. When the wheels are driven via the continuously variable transmission T, the pressure becomes high (at this time, the second oil passage Lb is at low pressure), while the second oil passage Lb is used to control the wheels when the vehicle is decelerating, etc. The pressure becomes high when the engine brake is applied by receiving driving force from the engine (at this time,
The first oil passage La is at low pressure).

A direct coupling clutch valve DC that can connect and disconnect this oil passage La is disposed within the first oil passage La.

A discharge port of a charge pump (replenishment pump) 10 driven by the engine E via a pair of gear sets 9a and 9b is
Regulator valve 120 via pump discharge oil path Lj
Further, a control oil path Lp branches from this discharge oil path Lj. The regulator valve 120 operates according to the oil pressure in the discharge oil passage Lj, and adjusts the oil pressure in the discharge oil passage Lj and the control oil passage Lp to a predetermined control line pressure Pc.
, and hydraulic oil having this line pressure Pc is supplied from the control oil passage Lp to a control valve (not shown) and the like.

The amount of oil supplied from this control oil path Lp to the control valve and the like is smaller than the discharge amount of the charge pump 10, so the remaining oil is sent to the first charge oil path Lk by the operation of the regulator valve 120. In addition, the first charge oil path L
If there is still an excess amount of oil even after being sent to k, it is returned to the sump 17 from the drain oil path Lm. The oil thus sent to the first charge oil passage Lk passes through the centrifugal oil filter 50 and is purified, and then passes through the second charge oil passage Lh, which has a pair of check valves 3, 3. 3rd oilway L
c, and by the action of this check valve 3.3,
It is supplied to the lower pressure side of the first and second oil passages La and Lb.

Note that a first lubricating oil passage Li that connects to the internal space of the motor cylinder 70 that constitutes the pump case branches from the second charge oil passage Lh, and a portion of the oil supplied to the second charging oil passage Lh is The lubricating oil passes through a check valve 18 disposed in the first lubricating oil passage Li and is supplied into the internal space via this oil passage Li. The oil supplied to this internal space lubricates the pump parts and is sent to the outside from the second lubricating oil path Ln for lubrication. Note that when the oil pressure in this internal space increases, it is discharged directly to the sump 17 from the check valve 19.

A governor valve 8 is attached coaxially with the charge pump 10. Hydraulic oil at a predetermined pressure is supplied to this governor valve 8 from a control valve (not shown), and the governor valve 8 converts the pressure of this hydraulic oil into governor oil pressure corresponding to the rotational speed of the engine E. Note that the input and output oil passages connected to the governor valve 8 are not shown in this figure.

A fourth oil passage Ld having a shuttle valve 4 is connected to the closed circuit. This shuttle valve 4 has a high pressure and a low pressure relief valve 6.7t and an oil sump 1.
The fifth and sixth oil passages Le+Lf connected to No. 7 are connected. The shuttle valve 4 is a 2-point/3-position switching valve, and operates according to the oil pressure difference between the first and second oil passages L a + L b.
The oil passage on the high pressure side of b is made to communicate with the fifth oil passage Le, and the oil passage on the low pressure side is made to communicate with the sixth oil passage Lt'. As a result, the relief oil pressure in the oil passage on the high pressure side is regulated by the high pressure relief valve θ, and the relief oil pressure in the oil passage on the low pressure side is regulated by the low pressure relief valve 7.

A seventh oil passage Lg that short-circuits both passages is also provided between the first and second oil passages La and Lb, and this seventh oil passage Lg has a variable throttle that controls the opening degree of this oil passage. A main clutch valve CL consisting of a valve is provided.

An output shaft 28 is arranged parallel to the rotating shaft 2 of the hydraulic motor M, and a forward/reverse switching device 20 is provided between both shafts 2 and 28. This device 20 includes first and second drive gears 21 and 22 disposed on a rotating shaft 2 with a spacing in the axial direction, and rotatably supported by an output shaft 28 and a first drive gear 2
1, a second driven gear 25 that meshes with the second drive gear 22 via an intermediate gear 24 and is rotatably supported on the output shaft 28, and the first and second wave gears. A clutch hub 26 is fixed to the output shaft 28 between 23.25 and a clutch gear 23a or 25a which is slidable in the axial direction and formed on the side surfaces of the clutch hub 26 and the driven gears 23 and 25, respectively. A sleeve 27 that is selectively connected is provided, and this sleeve 27 is moved left and right by a shift fork 29. The specific structure of this forward/reverse switching device 20 is shown in FIG. In this forward/reverse switching device 20, when the sleeve 27 is slid leftward in the drawing by the shift fork 29 and the clutch gear 23a of the first driven gear 23 and the clutch hub 26 are connected as shown in the drawing, the output is The shaft 28 is rotated in the opposite direction to the rotating shaft 2, and the wheels are rotated in the forward direction as the continuously variable transmission T is driven. On the other hand, when the sleeve 27 is slid to the right by the shift fork 29 and the clutch gear 25a of the second driven gear 25 and the clutch hub 26 are connected, the output shaft 28 is rotated in the same direction as the rotating shaft 2, The wheels are rotated in the reverse direction.

Next, the concrete structure of the continuously variable transmission T will be briefly explained using FIG. 2.

This continuously variable transmission T is configured such that a hydraulic pump P and a hydraulic motor M are disposed together in a space surrounded by first to fourth cases 5a to 5d. An input shaft 1 of the hydraulic pump P is coupled to a crankshaft Es of the engine E via a flywheel 1a. A centrifugal filter 50 is disposed within the recess on the inner peripheral side of the flywheel 1a.

Further, a drive gear 9a is connected to the input shaft 1 by a spline, and a driven gear 9b meshes with the drive gear 9a. The driven gear 9b is coaxially connected to the drive shaft 11 of the charge pump 10, and the rotation of the engine E is transmitted to the drive shaft load l of the charge pump 10 through the pair of gears 9a and 9b, so that the charge pump 10 Driven. This drive shaft 11 passes through the charge pump 10 and protrudes to the side opposite to the gear 9b, and is also connected to the governor valve 8. Therefore, the rotation of the engine E is also transmitted to this governor valve 8, and the governor valve 8 causes the engine E to rotate.
The governor hydraulic pressure corresponding to the rotation of is created.

The hydraulic pump P includes a pump cylinder 60 spline-coupled to the input shaft 1, and a plurality of pump plungers e2 slidably engaged with a plurality of cylinder holes 61 formed in the pump cylinder 60 at equal intervals on the circumference. It is rotationally driven by the power of the engine E transmitted through the input shaft 1.

The hydraulic motor M includes a motor cylinder 70 provided surrounding the pump cylinder 60, and a plurality of motor plungers 72 that slide into a plurality of cylinder holes 71 formed in the motor cylinder 70 at equal intervals on the circumference. It is designed to be able to rotate relative to the pump cylinder 60 coaxially.

The motor cylinder 70 is composed of first to fourth parts 70a to 70d that are aligned in the axial direction and are integrally coupled.

The first portion 70a has a bearing 7 at its left end outer periphery.
The pump swash plate ring 63 is rotatably supported by the case 5b via the pump 9a, and the right inner surface is inclined with respect to the input shaft 1 to form a pump swash plate member. is provided. Second portion 70b
The plurality of cylinder holes 71 are formed in the third portion 70c, and the third portion 70c has a distribution plate 80 in which an oil passage to each cylinder hole 61.71 is formed. The fourth portion 70d includes the first
A gear member GM having second drive gears 21 and 22 is press-fitted and rotatably supported by the case 5c via a bearing 79b.

An annular pump shoe 84 is rotatably and slidably attached to the pump swash plate puffer 63, and the pump shoe 64 and the pump plunger 62 are connected to each other via a connecting rod 65 so as to be able to swing freely to some extent. . Pump shoe 8
4 and the pump cylinder 80 have bevel gears 68 that mesh with each other.
a, 68b are formed. Therefore, input shaft 1
When the pump cylinder 60 is rotationally driven, the pump shoe 64 is also rotated at the same time, and the pump plunger 62 is reciprocated according to the inclination of the pump swash plate ring 63, sucking oil from the suction port and discharging oil from the discharge port. will be done.

Also, a swash plate member 73 facing each motor plunger 72
The second case 5b is connected to the second case 5b via a pair of trunnion shafts (swing shafts) 73a that protrude from both outer ends in a direction perpendicular to the paper surface.
It is swingably supported by. A motor swash plate ring 73b is disposed on the surface of the swash plate member facing the motor plunger 72, and a motor shoe 74 is attached along the motor swash plate ring 73b. The motor shinny 74 is swingably connected to the end of each motor plunger 72. The swash plate member 73 is connected to the piston rod 33 of the transmission servo unit 30 via a link member 39 at a position away from the trunnion shaft 73a. When moved in the direction, the swash plate member 7
3 is swung around the trunnion shaft 73a.

The fourth portion 70d of the motor cylinder 70 is formed hollow, and a fixed shaft 91 fixed to the pressure distribution board 18 is inserted into the center thereof. A distribution ring 92 is fluid-tightly fitted to the left end of the fixed shaft 91, and the left end surface of the distribution ring 92 in the axial direction is eccentric so that it can come into sliding contact with the distribution plate 80.

This distribution ring 92 allows the fourth part ? A hollow portion formed in Od is divided into an inner oil chamber and an outer oil chamber, the inner oil chamber forming a first oil passage La, and the outer oil chamber forming a second oil passage Lb. Note that the pressure distribution board 18 is connected to the shuttle valve 4.
, high pressure and low pressure relief valves 6.7, etc., are attached to the right side of the third case 5c, and
It is covered by a fourth case 5d.

A pump discharge port and a pump suction port are bored in the distribution board 80, and the cylinder hole 61 of the pump plunger 62 in the discharge stroke and the inner oil chamber are connected through the discharge port and the discharge path connected thereto. 1st oil passage La
The cylinder hole 61 of the pump plunger 62 in the suction stroke and the second oil passage Lb, which is made up of an outer oil chamber, are in communication with each other through the pump suction port and the suction passage connected thereto.
is communicated. Furthermore, a communication path communicating with the cylinder hole (cylinder chamber) 71 of each motor plunger 72 is formed in the distribution panel 80, and the opening of this communication path is formed in the distribution ring 9.
2, the motor cylinder 70 communicates with the first oil passage La or the second oil passage Lb according to the rotation of the motor cylinder 70. Therefore, the cylinder hole 71 of the motor plunger 72 in the expansion stroke and the first oil passage La communicate with each other via the communication passage, and the cylinder hole 71 of the motor plunger 72 in the contraction stroke and the second oil passage Lb communicate with each other via the communication passage. Ru.

In this way, a hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M via the distribution panel 80 and the distribution ring 92. Therefore, when the pump cylinder 60 is driven from the input shaft 1, the high-pressure hydraulic oil generated by the discharge stroke of the pump plunger 62 is transferred from the pump discharge port to the pump discharge passage, the first oil passage La (inner oil chamber), and the like. It flows into the cylinder hole 71 of the motor plunger 72 which is in the expansion stroke through the first communication path which is in communication with the motor plunger 72, and gives a thrust to the motor plunger 72.

On the other hand, the hydraulic oil discharged by the motor plunger 72 in the contraction stroke is transferred to the pump in the suction stroke via the second communication path communicating with the second oil path Lb (outer oil chamber), the pump suction path, and the pump suction port. It flows into the cylinder hole 61 of the plunger 62.

Due to this circulation of hydraulic oil, the reaction torque that the pump plunger 62 in the discharge stroke applies to the motor cylinder 70 via the pump swash plate ring 83, and the reaction torque that the motor plunger 72 in the expansion stroke receives from the motor swash plate member 73. The motor cylinder 70 is rotationally driven by the sum of .

The gear ratio of the motor cylinder 70 to the pump cylinder 60 is given by the following equation.

Rotation speed of motor cylinder 70 Capacity of hydraulic motor MAs can be seen from the above equation, if the swash plate member 73 is oscillated by the gear shifting servo unit 30 and the capacity of the hydraulic motor M is changed from 0 to a certain value, the gear ratio can be changed. can vary from 1 (minimum value) to some desired value (maximum value).

On the other hand, as described above, the gear member GM having the first and second drive gears is press-fitted and fixed into the fourth portion 70d of the motor cylinder 70. Therefore, the rotational driving force of the motor cylinder 70 is transmitted to the output shaft 28 via the forward/reverse switching device 20. This output shaft 28 is connected to the differential device 1 via the finer 2 legia set 28a, 29.
00, and the rotational driving force of the output shaft 28 is transmitted to the differential device 100. The rotational driving force divided between the left and right drive shafts 105 and 106 by the differential device 100 is transmitted to left and right wheels (not shown) to drive the vehicle.

In addition, a short-circuit path between the first oil passage La and the second oil passage Lb is formed in the fixed shaft 91 inserted into the hollow part of the fourth portion 70d, and this short-circuit path is controlled from fully closed to fully open. A direct coupling clutch valve DC capable of controlling the main clutch valve CL1 and the first oil passage La on and off is provided.

First, the main clutch valve CL will be explained. A short-circuit boat that can communicate the first oil passage La and the second oil passage Lb is bored in the peripheral wall of the fixed shaft 91, and a cylindrical main clutch valve body 95 is installed in the hollow part of the fixed shaft 91. It has been inserted. The valve body 95 is rotatable relative to the fixed shaft 91, and has a short-circuit hole that can be aligned with the short-circuit port. An arm 95a formed at the right end of this valve body 95
By rotating the valve body 95, the amount of alignment (overlapping) between the short circuit boat and the short circuit hole can be adjusted. The size of this matching part becomes the opening degree of the short-circuit passage between the first oil passage La and the second oil passage Lb, and therefore, by controlling the rotation of the valve body 95, the opening degree of the short-circuit passage is changed from fully open to fully closed. can be controlled up to. If the opening degree of the short-circuit passage is fully open, the hydraulic oil discharged from the pump discharge boat to the first oil passage La flows directly into the second oil passage Lb from the short-circuit port and the short-circuit hole, and also flows into the pump suction port. Therefore, the hydraulic motor M becomes inactive and the clutch becomes OFF. Naturally, on the contrary, if the opening degree of the short-circuit passage is fully closed, the clutch ON state is realized.

A direct coupling clutch valve DC is disposed within the hollow portion of this main clutch valve body 95. This direct-coupled Clara valve DC includes a piston shaft 85 that is fitted within the valve body 95 so as to be movable in the axial direction, a shoe 86 that is attached to the tip of the piston shaft 85, and a shoe 86 that is inserted into the piston shaft 85. The pilot spool 84 is composed of a pilot spool 84.
By moving in the axial direction, the piston shaft 85 can be moved in the axial direction to follow this movement. Therefore, the pilot spool 84 is moved to the left, the piston shaft 85 is moved to the left, and the shoe 86 at the tip of the piston shaft 85 is used to block the discharge path of the pump that opens to the end face of the distribution board 80, thereby blocking the first oil path La. is now possible. In this state where the pump discharge passage is closed, the pump plunger 62 is hydraulically locked, and the hydraulic pump P and the hydraulic motor M are directly connected.

Note that this direct connection state is performed at the minimum gear ratio position with the swash plate member 73 of the motor M upright, that is, at the top position. In addition to improving efficiency, the thrust force exerted by the motor plunger 72 on the swash plate member 73 is reduced,
It is possible to reduce frictional resistance and reduce the load applied to bearings and the like.

The surrounding structure of the replenishment pump in the hydraulic continuously variable transmission having the above configuration and the flow of oil from this pump will be explained using FIG. 3.

The replenishment pump 10 includes a pump housing 10a coupled to a second case 5b, gears 12a and 12b disposed inside the pump housing 10a that mesh with each other, and an input shaft 1 via the pair of gears 9a and 9b. The drive shaft 11 is driven according to the rotation of the drive shaft 11. The drive shaft 11 is connected to a gear 12a, and the input shaft 1 by the engine E
When the drive shaft 11 is rotated in accordance with the rotation of the gear 12a
, 12b pump up hydraulic oil from the oil sump 17 and discharge it from the discharge port to the discharge oil path Lj.

On the pump housing 10a is a regulator valve 1.
20 valve housings 121 are connected and arranged,
The drive shaft 11 protrudes through the housing 121, and the governor valve 8 is attached to the end thereof.

Further, the valve housing 121 includes a governor valve 8.
an oil passage 8a for supplying hydraulic oil at a predetermined pressure to the oil passage 8a, and an oil passage 8d for taking out the governor pressure regulated by the governor valve 8.
is formed. Therefore, as shown by arrow A1, the hydraulic oil supplied to the oil passage 8a is sent from the inlet port 8e through the outer oil passage 8b in the drive shaft 11 to the governor valve 8, where it reaches the rotational speed of the engine E. The oil pressure is converted into the corresponding governor oil pressure, and then passes through the inner oil passage 8c in the drive shaft 11, and from the oil passage 8d via the outlet port (8f) toward the control valve (not shown) as shown by arrow A2. sent to.

In this way, the replenishment pump 10 and the governor valve 8 are both connected to the drive shaft 11, and are driven by receiving the driving force from the engine transmitted through the drive gears 9a, 9b. In this case, the drive shaft 11 includes a first drive shaft 11a that is integrally formed with the drive gear 9b and rotatably supported by a pair of ball bearings 5a and 5b, and a first drive shaft 11a that is rotatably supported by a pair of ball bearings 5a and 5b.
The second drive shaft 11b is fitted into the drive shaft 11a and is key-coupled to the drive shaft 11a. Further, the second drive shaft flb extends rightward and has a governor valve 8 attached to its right end.
It has the above-mentioned outer and inner oil passages 8b+8c communicating with. Both passages 8b, 8C communicate with the inlet and outlet ports 8e, 8f, respectively;
f and the governor valve 8, this second drive shaft 1
1b is rotatably supported by a ball bearing 5c.

According to such a drive structure of the replenishment pump 10 and the governor valve, the drive gear 9b1 that applies a load to the drive shaft 11
Support bearings 5a, 5b, and 5c are disposed between each of the replenishment pump 10 and the governor valve 8, so that the drive shaft 11 is firmly supported. In particular, the first drive shaft 11a is held by bearings 5a and 5b on both sides of the replenishment pump 10, and the load from the drive gear 9b and the replenishment pump 10 is mainly applied to the first drive shaft 11.
It is reliably supported by bearings 5a and 5b via a. Therefore, the first drive shaft 11a and the bearing 5a
, 5b will not be subjected to too uneven a load.

Further, the second drive shaft 11b is supported by a bearing 5c almost at its right end, and its left end extends to the position of the drive gear 9b and is coupled to the first drive shaft 11a. Therefore, the second drive shaft 11b is also firmly supported, and even if it receives an unbalanced force due to the rotation of the governor valve 8, no vibration occurs.

Note that leak oil from the replenishment pump 10 is guided to the left and right bearings 5a+5b along the first drive shaft 11a, so this bearing 5a.

5b is reliably lubricated. Also, leak oil from the inlet and outlet ports) 8e and 8f is removed from the second drive shaft fib.
It is guided along the top to the bearings 5b, 5c to ensure lubrication of these bearings 5b, 5c. Furthermore, this leaked oil is removed from the first drive shaft 11a and the second drive shaft 11a.
It is also guided into the fitting gap with b, and this part is lubricated to prevent wear of this part.

The regulator valve 120 having the valve housing 121 is disposed next to the oil passages 8a, 8a, as shown in FIG. The regulator valve 120 includes the above-mentioned valve housing 121, a spool 122 slidably disposed within the housing 121,
It consists of a spring 123 that applies a downward biasing force to the spool 122 in the figure. The housing 121 includes first and second boats 120a connected to the pump discharge oil path Lj,
120b, a third port 120C connected to the first charge oil passage Lk, and a fourth port 120 connected to the drain oil passage Lm.
d. The hydraulic pressure in the pump discharge oil passage Lj that is supplied as shown by arrow B1 and acts on the spool 122 from the spring first port 120a is caused by the pressure of the spring 123.
The control line pressure Pc is maintained at a level that balances the urging force of the control line pressure Pc.

This control line pressure Pc is sent to the control valve from a control oil path Lp that branches from the discharge oil path Lj (arrow B2).

The remaining hydraulic oil that has not been sent to the control oil path Lp is first transferred to the third port 120a as the spool 122 moves upward in the figure due to the hydraulic pressure acting on the spool 122 from the first port 120a.
Excess hydraulic oil is sent from the port 120c to the first charge oil path Lk (arrow B3), and excess hydraulic oil is sent from the fourth port 120d to the drain oil path Lm (arrow C).

The oil sent to the first charge oil passage Lk is transmitted through an oil passage 111 formed in the pump housing 10a and the second case 5b.
As shown by arrow B4 in FIG. 3, the input shaft 1 is fed into a space 112 surrounded by the second case 5b and the gear 9a at the distal end of the input shaft 1. And this space 112
From gear 9a and hub member 53 of centrifugal filter 50
The filter 50 is sent to the rotating container interior space 56 of the filter 50 through a groove 113 formed in the filter 50 .

This filter 50 includes a first side plate 51 of a disc bar coupled to the flywheel 1a, a second side plate 51 of the disc bar joined to the first side plate 51 at the outer peripheral end, and both side plates 51.
．． 52 and a hub member 53 spline-coupled to the tip of the input shaft 1, and a rotating container inner space 56 is formed surrounded by these three members 51, 52, and 53. There is. The groove 113 is formed on the inner periphery of the hub member 53, and an inlet hole 114 communicating with the inner space 56 of the rotary container is formed from the groove 113. Furthermore, when this filter 50 is assembled as shown in FIG.
6 is formed, and this space 116 and the rotating container inner space 5
An outlet hole 115 communicating with the hub member 53 is formed in the hub member 53.

Therefore, as described above, the first charge oil path Lk (oil path 1
11, a space 112, and a groove 113), the hydraulic oil is sent from the inlet hole 114 to the rotating container interior space 56. The hydraulic oil that fills this space 56 is rotated together with the input shaft 1 and receives its centrifugal force. are collected in. The hydraulic oil in the rotating container inner space 56 is sequentially sent into the space 116 from the outlet hole 115, but at this time, the dust collected on the outer periphery is left as is, thereby purifying the hydraulic oil. Note that when the engine E is stopped, the centrifugal force is not clouded, so the dust on the upper part of the outer periphery falls to the inner periphery, so the blocking plate 54 is installed in the space 56 to stop the dust from falling to the inner periphery.
It is connected to the second side plate 52 inside.

Furthermore, a radiation fin 55 is bonded to the outer surface of the first side plate of the filter 50. The radiation fins 55 have a shape that forms an air flow flowing from the inner periphery to the outer periphery in accordance with the rotation thereof, and the heat of the hydraulic oil in the space 56 is transferred to the Heat is effectively dissipated and cooled by air flow.

As described above, the hydraulic oil purified and cooled by the centrifugal oil filter 50 is sent out from the outlet hole 115 into the space 116 as described above, and then formed in the input shaft 1 and opened into the space 116. It enters into the second charge oil passage Lh formed by the through hole 1b. Then, by the action of the check valves 3, 3, the first and second oil passages La
*The above-mentioned hydraulic oil is supplied into the oil passage on the low pressure side of Lb.

A first communication hole 117 communicating with the communication hole 1b and containing the check valve 18 is formed in the third portion 70c of the motor cylinder 70;
and the right space 89 inside the motor cylinder 70.
A second communication hole opening at the second portion 70b is formed in the second portion 70b. Therefore, a portion of the hydraulic oil in the second charge oil passage Lh is supplied into the right side space 89a via the first passage hole 117, check valve 18, and second passage hole 118.

Note that the space inside the motor cylinder 70 is
4 and a spring holding member 67 that contacts the inner periphery of the shoe 64 and transmits the biasing force of the spring 66 to the shoe 64, the space is divided into a right side space 69a and a left side space 69b. Therefore, the hydraulic oil supplied to the right side space 69a lubricates the pump plunger 62, gear 68a, Et8b, etc., and is sent from the through hole 87a formed in the spring holding member 67 to the left side space 69b.

In this left side space Etea, the pump swash plate ring 6
3. Lubricate the pump shoe 64, etc., and then lubricate the groove 119 formed in the first portion 70a of the motor cylinder 70.
The bearings 79a and 79C are then returned to the sump in the case 5 while being lubricated. A check valve 19 is provided in the second through hole 118, and when the motor cylinder 70 is not rotating, this valve 19 is opened to allow oil in the spaces 89a and 89b to escape. This makes it possible to reduce the resistance when starting the engine (particularly when starting at a low temperature).

In the above example, a hydraulic system including a swash plate plunger type pump and motor has been described, but the present invention is not limited to this, and may be used in other types of equipment.

As described in detail, according to the present invention, the drive shaft is supported by the bearings disposed between the drive gear, the oil pump, and the governor valve. The shaft is firmly supported for rotation, preventing the shaft from wobbling, twisting, etc., and furthermore, preventing excessively uneven loads from being applied to each bearing. Additionally, each bearing is reliably lubricated by the leaked oil from the oil pump and the leaked oil from the port leading to the governor valve, improving the durability of the bearing.

[Brief explanation of the drawing]

Fig. 1 is a hydraulic circuit diagram of a continuously variable transmission having an oil pump drive structure according to the present invention, Fig. 2 is a sectional view of the above-mentioned continuously variable transmission, and Fig. 3 is a diagram of the replenishment pump in the above-mentioned continuously variable transmission. FIG. 4 is a cross-sectional view showing the regulator valve in the continuously variable transmission. 1... Input shaft 1a... Flywheel 8... Governor valve 9a+9b... Drive gear 10... Supply pump 11... Drive gear 50.
...Centrifugal oil filter 120...Regulator valve

Claims (1)

[Claims] 1) A drive shaft, a drive gear attached to one end of the drive shaft and transmitting rotational driving force to the drive shaft, and a drive gear attached to the other end of the drive shaft that transmits rotational driving force to the drive shaft; It consists of a governor valve that generates governor hydraulic pressure, and an oil pump attached to the drive shaft between the drive gear and the governor valve, and supplies oil to the governor valve and supplies oil with governor hydraulic pressure from the governor valve. The oil is removed from a port formed between the oil pump and the governor valve through an oil passage formed in the drive shaft, and between the drive gear and the oil pump, and between the oil pump and the governor valve. A drive structure for an oil pump, characterized in that the drive shaft is rotatably supported by three bearings disposed between the drive shaft and a port and between the port and the governor valve.