JPH0155826B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention comprises spline-coupling the boss of a rotating container of a centrifugal oil filter driven by an engine to an input shaft of a transmission, and spline-coupling a drive gear of an oil pump to this input shaft. The present invention relates to a centrifugal filtration oil supply device in which a discharge port of the oil pump is communicated with an inlet chamber of the rotary container via an inflow path, and an outlet chamber of the rotary container is communicated with an oil supply portion via an outflow path.

In the conventional centrifugal filtration oil supply device,
− As disclosed in Publication No. 152952, inflow,
Since both of the outlet passages are bored in the input shaft, if it becomes necessary to increase the flow rate of oil, there is a limit to increasing the cross-sectional area of the inlet and outlet passages, considering the strength of the input shaft.

The present invention has been made in view of the above points, and
It is an object of the present invention to provide a simple and effective centrifugal filtration oil supply device that can cope with an increase in the flow rate of oil while ensuring the strength of the input shaft.

To achieve this object, the present invention includes an oil chamber formed adjacent to one side of the drive gear and connected to a discharge port of the oil pump, and an oil chamber formed adjacent to one side of the drive gear and connected to the other side of the drive gear. The annular oil passage formed between the boss of the rotating container and the oil chamber and the annular oil passage are formed by removing some teeth of the spline joint between the drive gear and the input shaft. and an oil hole bored in the boss of the rotary container to communicate between the annular oil passage and the inlet chamber, and the outflow passage is configured such that one end opens into the outlet chamber. It is characterized in that the input shaft is bored.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings. The automobile transmission device shown in FIG. It is comprised of a front gear unit G and a reverse gear unit G, which are housed in a transmission case 1.

First, the hydraulic transmission T is composed of a constant displacement swash plate hydraulic pump P and a variable displacement swash plate hydraulic motor M.

The hydraulic pump P has a pump cylinder 4 with an input shaft 2 protruding from the left end and a support shaft 3 from the right end. They are connected to each other so as to be movable only in the axial direction, and their distal ends penetrate the left side wall of the transmission case 1 and protrude to the outside, where they are connected to a flywheel 6 attached to the crankshaft E of the engine.

The pump cylinder 4 is provided with a large number of through stepped cylinder holes 7, 7 in an annular arrangement surrounding the center of rotation of the cylinder 4, and in the illustrated example, each stepped cylinder hole 7
The left half is a large-diameter hole 7l, the right half is a small-diameter hole 7r, and a stepped portion thereof is formed on the pressure receiving surface 8.
A pair of large and small pump plungers 9l and 9r that face each other slides into each stepped cylinder hole 7 to define a pump oil chamber 7A therebetween. Both plungers 9l and 9r each have a bottomed cylindrical shape with the bottom facing the outer end, and a coil spring 11 is housed in the hollow part of the large diameter pump plunger 9l, which causes both plungers 9l and 9r to move away from each other. A base portion of a spring guide rod 10 that is inserted into the spring 11 to prevent buckling thereof is fitted into the hollow portion of the small diameter pump plunger 9r. The spring guide rod 10 is made of a material having a lighter specific gravity than the pump plungers 9l, 9r.

On the other hand, the hydraulic motor M has a motor cylinder 12 that surrounds and is concentric with the pump cylinder 4, and the motor cylinder 12 has a large number of through cylinder holes 13, 13, . A distribution end wall 12a is integrally formed at the right end thereof. Each hole 13 above
A pair of motor plungers 14 of the same diameter are opposed to each other.
l and 14r slide together and the motor oil chamber 1 is formed between them.
Define 3A. Furthermore, the left side of the motor cylinder 12,
A hollow output shaft 16 and a support shaft 17 are fixed to both right end faces with bolts 15, respectively, and the output shaft 1
6 is supported by the transmission case 1 on its outer circumferential surface via a bearing 18, and supports the input shaft 2 on its inner circumferential surface via bear links 19, 20. Further, the outer peripheral surface of the support shaft 17 is supported by the mission case 1 via a bearing 21. The motor cylinder 12 supports the support shaft 3 of the pump cylinder 4 via a bearing 22 inside thereof, and the support shaft 3
The end face and the distribution end wall 12a are brought into close contact. A seal ring 23 is fitted onto the outer periphery of the end of the support shaft 3 so as to be in contact with the inner peripheral surface of the motor cylinder 12 .

Further, inside the motor cylinder 12, there are a pair of left and right pump ramps arranged symmetrically and in contact with the outer ends of the left pump plunger group 9l and the right pump plunger group 9r at a fixed angle with respect to their respective axes. Plates 24l, 24r are thrust and radial bearings 25l, 26l, 26r, 26
Supported via r. Therefore, each pump swash plate 24
When rotating relative to the motor cylinder 12, the pump plungers 9l and 24r can cooperate with the coil spring 11 to give reciprocating motion to each group of pump plungers 9l and 9r, thereby repeating suction and discharge strokes.

In the hydraulic motor M, a pair of left and right motor swash plates 27l and 27r are arranged symmetrically at the outer ends of the left motor plunger 14l group and the right motor plunger 14r group, respectively, and abut against their respective axes. Ru. These motor swash plates 27l,
Thrust 27r and radial bearing 28
The swash plate frames 31l and 31r supported through the motor cylinders 1, 29l, 28r and 29r respectively have integrally trunnion shafts (not shown) having axes perpendicular to the rotational axis of the motor cylinder 12, and these trunnion shafts , are rotatably supported by the mission case 1, and are interlocked and connected to each other via an interlocking device (not shown). Both motor swash plates 27l, 2
7r can be tilted symmetrically from an upright position perpendicular to each motor plunger group 14l, 14r to the maximum tilted position shown in the figure by operating the interlocking device, and in these tilted positions, the motor cylinder 1
2 rotates, each motor plunger 14l,
14r group can be sequentially reciprocated to repeat the expansion and contraction strokes, and the plungers 1
The sliding stroke of 4l and 14r is the motor swash plate 27.
It is determined by the inclination angle of l and 27r.

A hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M as follows. That is, an oil chamber 38 is formed in the support shaft 17 of the motor cylinder 12, and the distribution end wall 12a faces the oil chamber 38.
A large number of communication ports 39, 3 each drilled in a.
9... and one discharge port 41 and one suction port 42 are opened, and the open end of the discharge port 41 is on the rotation center line of the motor cylinder 12, and the communication port 3
The opening ends of 9, 39, . . . are located on the same circle surrounding the discharge port 41, and the suction port 42 is located outside the group of communication ports 39, respectively. Mission case 1
The fixed shaft 44 , which is positioned and fixed through the positioning pin 43 , projects into the oil chamber 38 from the outer end of the support shaft 17 , and the distribution ring 45 is eccentrically located at the projecting end by a certain amount with respect to the center of rotation of the motor cylinder 12 . Installed. This distribution ring 45 is in contact with the distribution end wall 12a and divides the oil chamber 38 into an inner high-pressure oil chamber 38h and an outer low-pressure oil chamber 38l, and connects the discharge port 41 and the expansion stroke via the high-pressure oil chamber 38h. Motor oil chamber 13
A communicates with the communication port 39 connected to A, and the suction port 42 communicates with the communication port 39 connected to the motor oil chamber 13A in the contraction stroke via the low pressure oil chamber 38l. On the other hand, a large number of communication ports 47, 47, . 7A is connected to the discharge port 41, and that connected to the pump oil chamber 7A of the suction stroke is connected to the suction port 42.

When the pump cylinder 4 is rotated via the input shaft 2 due to the rotation of the engine crankshaft E, the high pressure oil generated in the pump oil chamber 7A due to the discharge stroke of the pump plungers 9l and 9r is transferred to the discharge port 41. The oil flows from the high-pressure oil chamber 38h to the motor oil chamber 13A in the expansion stroke through the communication port 39 in communication with the high-pressure oil chamber 38h, giving thrust to the opposed plungers 14l and 14r facing the oil chamber, while the motor plunger in the contraction stroke The hydraulic oil discharged by the pumps 14l and 14r is returned to the pump oil chamber 7A in the suction stroke via the communication port 39 communicating with the low pressure oil chamber 38l and the suction port 42. During this period, the pump plungers 9l and 9r in the discharge stroke are moved to the pump swash plate 24.
1, 24r to the motor cylinder 12 and the motor plunger 14 during the expansion stroke.
The motor cylinder 12 is rotated by the sum of the reaction torques received from the motor swash plates 27l and 27r, and an output is output from the output shaft 16.

In this case, the gear ratio of the motor cylinder 12 to the pump cylinder 4 is given by the following equation.

Gear ratio = rotation speed of pump cylinder 4/
Number of revolutions of motor cylinder 12 = 1 + capacity of hydraulic motor M/
Capacity of Hydraulic Pump P As is clear from the above equation, if the capacity of hydraulic motor M is changed from zero to the maximum value, the gear ratio can be changed from 1 to a certain required value, and the capacity of hydraulic motor M is Opposed motor plunger 14l, 1
Since the stroke is determined by the stroke of 4r, the above-mentioned speed change action can be obtained steplessly by tilting both motor swash plates 27l and 27r from the upright position to the maximum inclination angle as described above.

Furthermore, during gear shifting, the strokes of the opposed motor plungers 14l, 14r are simultaneously controlled by the pair of motor swash plates 27l, 27r which are interlocked so as to tilt symmetrically with respect to each other.
The capacity of the hydraulic motor M can be greatly adjusted with a small tilt angle of 27r. For example, compared to a conventional hydraulic motor that has only one motor swash plate, it is possible to adjust the capacity of the motor swash plate to give a certain rate of change to the capacity. The tilting angle according to the invention is only one-half of the conventional one. the result,
The amount of overhang from the motor cylinder 12 of each motor plunger 14l, 14r, and therefore the bending moment received from the motor swash plate 27l, 27r, is reduced, and their sliding speed is also reduced, resulting in smooth operation and durability. It is effective in improving the performance.
Further, a similar effect can be obtained in a hydraulic pump P having opposed pump plungers 9l and 9r.

Furthermore, during the discharge stroke of each opposing pump plunger 9l, 9r in the pump cylinder 4, the hydraulic pressure generated in the pump oil chamber 7A between them acts on the pressure receiving surface 8 formed in the stepped portion of the stepped cylinder hole 7, and the pump cylinder 4 In order to press the hydraulic oil to the right, a large pressing force is applied to the close contact surface between the support shaft 3 and the distribution end wall 12a, that is, the hydraulic oil transfer surface, thereby preventing oil leakage from the hydraulic oil transfer surface. Can be done. Axial movement of the pump cylinder 4 for pressing the hydraulic oil delivery surface is allowed by sliding between the proximal half of the input shaft 2 and the spline connecting cylinder 5. In order to further ensure the close contact of the hydraulic oil delivery surface, a resilient force of a coil spring 49 supported on the inner end of the output shaft 16 via a thrust bearing 48 is applied to the left end surface of the pump cylinder 4.

The fixed shaft 44 is formed hollow, and a short-circuit port 51 that can communicate between the high and low pressure oil chambers 38h and 38l is bored in its side wall, and a cylindrical clutch valve 52 that opens and closes the port is connected to the fixed shaft 44. It is rotatably fitted into the hollow part of.

The clutch valve 52 has a control groove 53 on the side wall of the tip end.
Further, each of the base ends is provided with a rotating plate 54 connected to a clutch control device (not shown), and by rotating the rotating plate 54, the control groove 53 is aligned with the short-circuiting port 51, and when the short-circuiting port 51 is fully opened, the clutch is closed. - Off state, when the control groove 53 is moved from the position of the short circuit port 51 and the short circuit port 51 is fully closed, the clutch is on state (state shown), the short circuit port 5
When 1 is left half-open, a half-clutch state is obtained.
That is, in the clutch-off state, the hydraulic oil discharged from the discharge port 41 to the high-pressure oil chamber 38h passes through the short-circuit port 51 to the low-pressure oil chamber 38l, and therefore immediately short-circuits to the suction port 42, rendering the hydraulic motor M inoperable. Further, in the clutch-on state, the short circuit of the hydraulic oil as described above is prevented, and the hydraulic oil is circulated from the hydraulic pump P to the motor M, and normal transmission is performed.

A hydraulic servo motor 57 operated by a pilot valve 55 is built into the clutch valve 52, and the tip of the servo piston 58 is connected to the clutch valve 52.
The valve stem 58a is formed into a valve stem 58a having a smaller diameter than the inner diameter of the valve stem 58a, and protrudes into the high pressure oil chamber 38h.A closing valve 59 for the discharge port 41 is swingably attached to the tip of the valve stem 58a. The discharge port 41 can be closed by moving the servo piston 58 to the left to bring the closing valve 59 into close contact with the distribution end wall 12a. This closing is performed when the motor swash plates 27l and 27r are placed in an upright position and the gear ratio is controlled to 1:1. This causes the pump plungers 9l and 9r to be hydraulically locked and the pump plungers 9l and 9r to be moved from the pump cylinder 4 to the pump plunger 9l, 9
The motor cylinder 12 can be mechanically driven via the r group and the pump swash plates 24l, 24r, so that the motor plungers 14l, 14r
The thrust applied to the motor swash plates 27l and 27r disappears, and the load on the bearings of each part due to the thrust is removed.

The high-pressure oil chamber 38h is used as a hydraulic pressure source for the hydraulic servo motors 37, 57 for operating the motor swash plates 27l, 27r and the blockage valve 59, and therefore the oil supply path 60 to the hydraulic servo motor 37 is connected to the fixed shaft 44. An oil supply path 61 to the hydraulic servo motor 57 passes through the valve rod 58a and the closing valve 59 and opens into the high pressure oil chamber 38h.

As clearly shown in Figure 2, the mission case 1
A replenishment pump 62 for replenishing the hydraulic closed circuit between the hydraulic pump P and the motor M with hydraulic oil is installed on the left end wall of the
However, a centrifugal oil filter 63 for purifying the oil discharged from the pump 62 is provided between the flywheel 6 and the input shaft 2.

The oil filter 63 includes a flat rotary container 65 accommodated in a recess 64 formed on one side of the flywheel 6 and an inlet chamber 65 inside the rotary container 65.
5a and an exit chamber 65b, with both chambers 65 on the outer periphery.
It is composed of a partition plate 68 having a through hole 67 that communicates between a and 65b.

A boss 100 is fixed to the center of each of the rotating container 65 and the partition plate 68, and this boss 100 is coupled to the input shaft 2 via a spline 101 and is supported by the mission case 1 via a bearing 102. be done.

The rotating container 65 is integrally provided with a flange 103 that projects radially from the center of its outer circumferential surface, and a pair of drive plates 104 are rotatably fitted to the outer circumferential surface of the rotating container 65 so as to sandwich the flange 103 therebetween. Ru. These drive plates 104, 104 are connected to the flywheel 6 with bolts 105 with their outer peripheral portions facing each other.

A plurality of windows 106 (only one is shown in the figure) are bored in the flange 103 at equal intervals on the circumference.
Both drive plates 104 and 10 correspond to these windows 106.
4 is also provided with a plurality of windows 107, 107. A buffer member 108 made of a spring, rubber, etc. is installed over each set of three windows 106, 107, 107, and this buffer member 108 is elastically deformed in accordance with the relative rotation of the drive plates 104, 104 and the rotating container 65. It's like it's happening.

In order to regulate the amount of elastic deformation of the buffer member 108, a stopper member 110 connected between both drive plates 104, 104 is inserted into a notch 109 provided in the flange 103 so that the stopper member 110 is inserted in a predetermined direction in the rotational direction of the drive plates 104, 104, etc. It is inserted at intervals.

The replenishment pump 62 has a boss 111 connected to the input shaft 2.
A drive gear 113 is connected to the drive gear 113 via a spline 112, and a driven gear 1 is driven by meshing with the drive gear 113.
The boss 111 of the drive gear 113 is arranged adjacent to the boss 100 of the rotating container 65, and an annular oil passage 115 is formed between these bosses 100 and 111. In addition, drive gear 1
An oil chamber 116 that is connected to the discharge port 71 of the replenishment pump 62 is formed adjacent to the thirteenth boss 111 .

As shown in FIGS. 2 and 3, a plurality of oil passages 117 are formed between the input shaft 2 and the boss 111 of the drive gear 113 by removing some teeth of the spline 112 that connects them. This oil passage 117
communicates between the oil chamber 116 and the annular oil passage 115. In the illustrated example, when forming the oil passage 117, the teeth of both the boss 111 and the input shaft 2 of the spline 112 are removed, but only one of the teeth may be removed.

Further, as shown in FIGS. 2 and 4, a plurality of oil holes 118 are bored in the boss 100 of the rotating container 65, and the oil holes 118 are connected to the annular oil passage 115 and the inlet chamber 65a of the rotating container 65. communicate between.

The oil chamber 116, oil passage 117, annular oil passage 115, and oil hole 118 constitute an inflow passage that communicates the discharge port 71 of the replenishment pump 62 with the inlet chamber 65a of the rotary container 65.

The outlet chamber 65b of the rotary container 65 communicates with an outlet passage 74 formed in the center of the input shaft 2, and this outlet passage 74 communicates with the discharge port 41 via a check valve 75 on one side. On the other hand, it communicates with the low pressure oil chamber 38l via an oil chamber 77 sandwiched between the pump cylinder 4 and the motor cylinder 12 and a check valve 76.

Next, the forward and reverse gear device G will be explained.

A subshaft 78 parallel to the output shaft 16 is connected to the transmission case 1 between the output shaft 16 of the hydraulic motor M and a well-known differential device D connected to a drive gear (not shown).
is rotatably supported. First and second drive gears 79 ₁ and 79 ₂ are fixedly arranged in the axial direction on the output shaft 16, and a first drive gear 79 1 and a second drive gear 79 2 mesh with the first drive gear 79 ₁ .
A second driven gear 80 ₂ that meshes with the driven gear 80 1 and the second driving gear 79 ₂ via the intermediate gear 81 is _rotatably provided on the subshaft 78 . Both driven gears 80 ₁ , 80 ₂ have a drive clutch gear 82 on each opposing part.
₁ and 82 ₂ , and a driven clutch gear 83 fixed to the subshaft 78 is disposed between them, and this clutch gear 83 is engaged with the driven clutch gear 83 through an annular clutch member 84 that is constantly engaged with the driven clutch gear 83. Drive clutch gear 82 ₁
or 82 ₂ can be selectively linked.
A shift fork 85 operates the clutch member 84 and is operated by a hydraulic cylinder (not shown).
Further, on the counter shaft 78, a gear 87 that meshes with a large gear 88 of the actuating device D is fixed at the left end, and a parking gear 89 is fixed at the right end.

Therefore, when the hydraulic motor M rotates, the clutch member 84 is moved to the left as shown by the solid line, and the driven clutch gear 8 is rotated.
3 is connected to the drive clutch gear 82 ₁ , the rotational torque of the output shaft 16 is transferred to the first drive gear 79 ₁ , the first
Driven gear 80 ₁ , clutch gear 83, subshaft 78,
The gear 87 and the large gear 88 are sequentially transmitted to the differential device D.
is driven in the forward direction of the vehicle. Conversely, if the clutch member 84 is moved to the right as shown by the chain line to connect the driven clutch gear 83 to the drive clutch gear 82 ₂ , the rotational torque of the output shaft 16 is changed to the second drive gear 79 .
₂ , the intermediate gear 81, the second driven gear 80 ₂ , the clutch gear 83, the subshaft 78, the gear 87, and the large gear 88 are sequentially transmitted to drive the differential device D in the reverse direction of the vehicle.

Next, the operation of this embodiment will be explained.

During normal operation of the engine, the output torque of the crankshaft E is applied to the flywheel 6 and both drive plates 10.
4, 104, it is transmitted to the input shaft 2 of the transmission T via the transmission path of the buffer member 108 and the rotating container 65, and during engine braking, the reverse load travels in the opposite direction along the transmission path and is transmitted to the crankshaft E.

And in any case, the flywheel 6
When a torque fluctuation occurs between the input shaft 2, the buffer member 108 is elastically deformed to cause relative rotation between the drive plates 104, 104 and the rotating container 65, thereby absorbing the torque fluctuation.

The input shaft 2 continues to drive the replenishment pump 62 during its rotation, and the replenishment pump 62 discharges oil sucked from an oil reservoir (not shown) into the oil chamber 116 from the discharge port 71 at a constant pressure. The oil discharged into the oil chamber 116 flows into the rotary container 65 through the oil passage 117, the annular oil passage 115, and the oil hole 118, and then passes through the partition plate 68.
from the inlet chamber 65a to the outlet chamber 6
5b, foreign substances such as cutting chips and abrasion particles in the oil are centrifuged and accumulate on the inner circumferential surface of the rotating container 65.

The oil passed through the rotating container 65 and purified passes through the outflow path 74 and fills the oil chamber 77, and the pump swash plate 24
l, 24r bearings 25l, 26l, 25
Lubricate r, 26r, etc. In addition, if hydraulic oil leaks from the hydraulic closed circuit between the hydraulic pump P and the motor, the check valve 75 or 7 is installed to compensate for the leakage.
6 and open the discharge port 41 or low pressure oil chamber 3.
8l.

As described above, according to the present invention, the inflow path is
an oil chamber formed adjacent to one side of the drive gear and connected to the discharge port of the oil pump; an annular oil passage formed between the other side of the drive gear and the boss of the rotating container; An oil passage formed by cutting out some teeth of a spline joint between the driving gear and the input shaft to communicate between the annular oil passage and the inlet chamber to communicate between the oil chamber and the annular oil passage. The oil hole is formed in the boss of the rotary container, and the outflow passage is formed in the input shaft such that one end thereof opens into the outlet chamber. An inlet passage can be formed in the input shaft, and an outlet passage can be formed in the input shaft. Therefore, it is possible to increase the flow rate of oil by expanding the cross-sectional area of the inlet and outlet passages without significantly reducing the strength of the input shaft. .

In particular, even if some of the teeth are removed from the spline joint between the drive gear and input shaft of the oil pump to form the inflow path, the load on the oil pump is relatively small, so it will be sufficient to withstand the load. Moreover, since there is no need to form a hole in the drive gear to form an inflow path, there is no need to form the boss with a particularly large diameter.

On the other hand, an oil hole is drilled in the boss of the rotating container to form an inflow path, but this is to prevent the inflow path from reducing the strength of the spline connection between the rotating container and the input shaft. The rotating container can reliably transmit the engine power to the input shaft.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional side view of an automobile transmission device embodying the present invention, FIG. 2 is an enlarged view of its main parts, and FIGS. 3 and 4 are sectional views taken along lines - and - in FIG. 2. . T...Transmission, P...Hydraulic pump, M...Hydraulic motor, E...Engine crankshaft, 2...Input shaft, 62...Replenishment pump as oil pump, 6
3... Centrifugal oil filter, 65... Rotating container, 6
5a... Inlet chamber, 65b... Outlet chamber, 71... Discharge port, 74... Outflow path, 100... Boss of rotating container, 101... Spline, 112... Spline, 113... Drive gear, 115... …Circular oil road,
116...Oil chamber, 117...Oil passage, 118...Oil hole.

Claims (1)

[Claims] 1. Centrifugal oil filter 6 driven by an engine.
The boss 100 of the rotary container 65 of No. 3 is spline-coupled to the input shaft 2 of the transmission T, and the drive gear 113 of the oil pump 62 is spline-coupled to the input shaft 2, and the discharge port 71 of the oil pump 62 is connected to the inflow path. The outlet chamber 65b of the rotary container 65 is connected to the inlet chamber 65a of the rotary container 65 through the outlet passage 7.
4, the inflow passage is formed adjacent to one side of the drive gear 113 and connects to the discharge port 7 of the oil pump 62.
1, an annular oil passage 115 formed between the other side of the drive gear 113 and the boss 100 of the rotary container 65, and these oil chambers 116.
and an oil passage 117 formed by removing some teeth of the spline joint between the driving gear 113 and the input shaft 2 to communicate between the annular oil passage 115 and the inlet chamber 65a. and an oil hole 118 bored in the boss 100 of the rotary container 65 for communication between the two, and the outflow passage 74 is bored in the input shaft 2 so that one end thereof opens into the outlet chamber 65b. A centrifugal filtration oil supply device characterized by: