JPS60205062A - Buffer for hydraulic transmission - Google Patents

Abstract

PURPOSE:To absorb a torque variation lying between an engine and a transmission, by installing a torque buffer member interposingly between a rotary vessel to be connected to an input shaft and a driving plate to be fitted in the periphery of this vessel free of rotation, while connecting this driving plate to a flywheel. CONSTITUTION:Output torque of an engine crankshaft E is transmitted to an input shaft 2 of a transmission T via each transmission route of a flywheel 6, both driving plates 104, a buffer member 108 and a rotary vessel 65. In this case, when a torque variation is produced in an interval between the flywheel 6 and the input shaft 2, the buffer member 108 is elastically deformed, causing relative rotation between the driving plate 104 and the rotary vessel 65, whereby the torque variation is absorbed.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a shock absorber for a hydraulic transmission, particularly an input shaft connected to a crankshaft of an engine through a rotating container of a centrifugal filter, and a hydraulic oil replenishment device driven by the input shaft. In a hydraulic transmission, the inside of the rotary container is connected to the discharge port of the replenishment pump on one side and to the transmission hydraulic circuit on the other side, the torque fluctuation between the flywheel and the input shaft is controlled. The present invention relates to a shock absorbing device that prevents mutual transmission of signals.

A hydraulic transmission in which an input shaft is connected to a flywheel of an engine via a rotary container of a centrifugal filter has already been disclosed in Japanese Utility Model Application Publication No. 152952/1983, based on a proposal by the present applicant. By the way, in the existing proposal, the input shaft is integrally connected to the engine flywheel, so when torque fluctuation occurs between the engine and transmission, it is directly transmitted to each other, causing vibration. It was found that

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a simple and effective shock absorber η that uses a rotating container of a centrifugal filter as a component to absorb torque fluctuations between an engine and a transmission.

In order to achieve this object, the present invention provides a structure in which a rotary container connected to the input shaft and a drive plate rotatably fitted around the outer circumference of the container are provided. The driving plate is connected to the flywheel by interposing a torque buffering member that deforms in accordance with the motion.

Hereinafter, one embodiment of the present invention will be described with reference to page 11. The automobile transmission shown in FIG. 1 includes a hydraulic transmission 'F driven by a crankshaft E of an engine, It is composed of a differential gear unit G, which connects the differential gear, and a reverse gear unit G, which are connected to the transmission case 1.
be accommodated in.

First, let me explain about the hydraulic transmission 51T, which is a constant displacement ■
Type swash plate type hydraulic pump P and variable displacement type swash plate type hydraulic motor M
It consists of

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 mission case l and protrude outside, where they are connected to a flywheel 6 attached to the crankshaft of the engine.

The pump cylinder 4 has many through stages (J cylinder hole 7
, 7 are bored in an annular arrangement surrounding the center of rotation of the cylinder 4, and in the illustrated example, each stepped cylinder hole 7 has a large diameter hole 71 in the left half and a small diameter hole 7 in the right half, and the difference in level between them is A large and small pump plunger 91 is formed in each stepped cylinder hole 7 to face each other. , 9r slide together to define a pump oil chamber 7A therebetween. Both plungers 9β.

9r each has a bottomed cylindrical shape with the bottom facing the outer end,
Both plungers 9 are provided in the hollow part of the large diameter pump plunger 91.
A coil spring 11 that springs the springs 1 and 9r away from each other is housed, and a base of a spring guide rod 10 that is inserted into the spring 11 and prevents it from buckling is fitted into the hollow part of the small-diameter pump plunger 9r. be done. The spring guide rod 10 is made of a material having a lighter specific gravity than the pump plungers 94', 9r.

On the other hand, the hydraulic motor M surrounds the pump cylinder 4,
It has a motor cylinder 12 concentric therewith, in which a number of through cylinder holes 13, 13... are bored in an annular arrangement surrounding the center of rotation of the cylinder 2,
Further, a distribution end wall 12a is integrally formed at the right end thereof.

Each hole 13 has a pair of motor plungers 147 with the same diameter facing each other! , 14r slide together to define a motor oil chamber 1.3A therebetween. 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 by bolts 15, respectively, and the output shaft 16 is supported on the outer peripheral surface by the transmission case 1 via a bearing 18, and the inner peripheral surface is supported by a bearing link 19. The input shaft 2 is supported through the angle 20°. Further, the outer peripheral surface of the support shaft I7 is supported by the transmission case 1 via a hair ring 2I. The motor cylinder 12 supports the support shaft 3 of the pump cylinder 4 through a hair ring 22 inside thereof, and brings the end surface of the support shaft 3 into close contact with the distribution end wall 12a. A seal ring 23 is fitted onto the outer periphery of the end of the support shaft 3 and is in contact with the inner circumferential surface of the motor cylinder 12 .

Further, inside the motor cylinder 12, there is a pair of left and right pump swash plates arranged symmetrically and in contact with the outer ends of the left pump plunger 91Y and the right pump plunger group 9r, respectively, at a constant angle with respect to their axes. 24j! , 24
r is thrust and radial hair ring 251.261
! ;25r, supported via 2Gr. Thus, when each pump swash plate 241° 24r rotates relative to the moke sill ring 12, it cooperates with the coil spring 11 to give reciprocating motion to each pump plunger group 9R and 9r, thereby repeating the suction and discharge strokes. I can do it.

In addition, in the hydraulic motor M, the left motor plunger 14j! A pair of left and right motor swash plates 211.27r are arranged symmetrically at each outer end of the group and the right motor plunger 14r group with respect to their axes, respectively. These motor swash plates 27β.

27r to thrust and radial bearings 28e, 2
97! ; Swash plate frame 311 supported via 28r and 29r! , 31r are trunnion shafts (not shown) each having an axis perpendicular to the rotational axis of the motor cylinder 12.
These trunnion shafts are rotatably supported by the mission case 1 and are movably connected to the transmission case 11 and the other through an interlocking device (not shown). Both motor swash plates 27L27r can be symmetrically tilted from the straight η position perpendicular to each motor slanted 141.14r group to the maximum tilted position shown in the figure by operating the interlocking device, and the motors can be tilted at these tilted positions. When the cylinder 12 rotates, each motor plunger 14p.

The 14r group is sequentially given reciprocating motion to repeat the expansion and contraction strokes, and the plungers ]1! , 14
The sliding stroke of r is determined by the inclination angle of the motor swash plates 27e and '17r.

A hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M as follows. That is, an oil chamber 38 facing the distribution end wall 12 is formed on the support shaft 17 of the motor cylinder 12, and a large number of communication boats 39, 39, . . . The two discharge boats 111 and the suction boat 42 are opened, and the discharge boat 41 is opened.
II O: si is on the rotation center line of the motor cylinder 12, and the open end of the communication boat 39, 39... is on the discharge boat 41
On the same circle surrounding the suction boat 42 and the communication boat 3
They are located outside of the 9 groups. A fixed shaft 4 is positioned and fixed to the mission case 1 via a positioning pin 43.
4 is a support shaft I7 (which protrudes into the oil chamber 38 from the end, and a distribution ring 45 is installed at the protruding end with a certain amount of eccentricity with respect to the center of rotation of the motor cylinder 12. The oil chamber 38 is connected to the inner high pressure oil chamber 38 in contact with the end wall 12a.
11 and an outer low-pressure oil chamber 38e, and the discharge bow 1-41 communicates with three communication boats connected to the motor oil chamber 138 of the expansion stroke through the high-pressure oil chamber 38h, and the low-pressure oil chamber 38β The suction boat 42 communicates with a communication boat 39 connected to the motor oil chamber 13A for the contraction stroke. On the other hand, the support shaft 3 of the pump cylinder 4 that comes into contact with the distribution end wall 12a
On the end face, there are many communication balls 1 connected to each pump oil chamber 7Δ.
-47.47... are opened, and the one connected to the pump oil chamber 7A in the discharge stroke is the discharge boat 4.
1 and the pump oil chamber 78 on the suction line 1'1° communicate with the suction boat 42, respectively.

Therefore, due to the rotation of the engine crankshaft E, the human power shaft 2
When the pump cylinder 4 is rotated through the pump cylinder 4, the high pressure oil generated in the pump oil chamber 7A due to the discharge stroke of the pump plungers 9r and 9r flows from the discharge bow I.41 to the high pressure oil chamber 38h.
Then, the opposing plunger 14j flows into the expansion stroke motor oil chamber 138 through the communication boat 39 that is in communication with it, and faces the oil chamber! , 14r, while the motor plunger 141 . The hydraulic oil discharged by I4r is connected to a communication boat 39 that communicates with a low pressure oil chamber 38Il.
and the pump oil chamber 7 for the suction stroke via the suction boat 42
Reflux to A. During this period, the pump syringe 9 in the discharge stroke
The reaction torque Il, 9r gives to the motor cylinder 12 via the pump swash plate 24j2゜24r, and the expansion stroke motor plunger 141゜14r gives the motor slant 4N, 277+
, 21r and the reaction torque, the motor cylinder 12 is rotated and an output is output from its output shaft 16.

In this case, motor cylinder 1 relative to pump cylinder 4
The gear ratio of 2 is increased by +7 using the following equation.

As is clear from the above equation, by changing the capacity of the hydraulic motor M): Ll from zero to the maximum value, the gear ratio can be changed to the required value consisting of 1, and the capacity of the hydraulic motor M is Since it is determined by the stroke of the motor plungers I4ρ, 14'', the above-mentioned speed change action can be obtained steplessly by tilting both motor swash plates 27m!, 27r from the upright position to the maximum inclination angle as described above.

In addition, during gear shifting, the strokes of the opposing motor plungers 14L and 14r are simultaneously controlled by the pair of motor swash plates 27/, 27r that are interlocked so as to tilt symmetrically with each other, so that the tilt angle of the motor swash plates 271°27r is reduced. For example, compared to a conventional hydraulic motor that has only one motor swash plate, the capacity of the motor swash plate can be adjusted to a large extent. The angle is actually only one-half that of the conventional one. the result,
Motor cylinder 1 of each motor plunger 141.14r
■ Overhang from 2, therefore motor swash plate 21
The bending moment received from 1.27r is reduced, and the sliding speed thereof is also reduced, which is effective in improving smoothness of operation and durability.

Further, a similar effect can be obtained in the hydraulic pump P having the opposed pump plunger 9L9r.

Further, in the pump cylinder 4, each opposed pump plunger 9j! , 9r, the hydraulic pressure generated in the pump oil chamber 7A between them acts on the pressure receiving surface 8 formed at the step of the stepped cylinder hole 7 and presses the pump cylinder 4 to the right. A large pressing force is applied to the surface in close contact with the distribution end wall 12a, that is, the hydraulic oil delivery surface, thereby preventing oil leakage from the hydraulic oil delivery surface.

Axial movement of the pump cylinder 4 for pressing the hydraulic oil delivery surface L is allowed by sliding between the proximal half of the man-powered shaft 2 and the spline connecting cylinder 5. In order to further ensure the close contact of the hydraulic oil delivery surface, there is a slot I at the inner end of the output shaft 16.
- The elastic force of the coil spring 49 supported via the 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 boat 51 that can communicate between the high and low pressure oil chambers 38h and 38/ is bored in its side wall, and a cylindrical clutch valve 5 opens and closes the boat.
2 is rotatably fitted into the hollow portion of the fixed shaft 44.

The clutch valve 52 has a control (h53) on the side wall of the distal end, and a rotating plate 54 connected to a clutch control device (not shown) on the base end.
By rotating the rotating plate 54, the control groove 53 is aligned with the shorting boat 1-51, and the shorting boat 51 is connected to the shorting boat 51.
When fully opened, the clutch is off, the control groove 53 is short-circuited boat 51; 11: Shifted/U shorted boat 5
When 1 is fully closed, the clutch is on (as shown),
A half-clutch state is obtained when the shorting boat 51 is half-opened.

1! II 1), when the clutch is off, the discharge boat 4
Hydraulic oil discharged from 1 to 11jI pressure oil chamber 38h passes through the short-circuit boat 51 and is directly short-circuited to the low-pressure oil chamber 381 and therefore to the suction boat 42, rendering the hydraulic motor M inoperable. Such a short circuit of the hydraulic oil is prevented, and the hydraulic oil is circulated from the hydraulic pump P to the motor M, and normal transmission occurs.

The clutch valve 52 has a built-in hydraulic servo motor 57 operated by the pilot valve 55, and the tip of the piston 58 is formed into a valve rod 58a having a smaller diameter than the inner diameter of the clutch valve 52, and is connected to the high pressure oil chamber 381+. A closing valve 59 for the discharge boat 41 is swingably attached to the tip of the plunger.

By moving the servo piston 58 to the left, the discharge boat 41 can be closed by bringing the closing valve 59 into close contact with the distribution end wall 12a. This closure is the motor swash plate 27j! , 27r are in the upright position and the gear ratio is controlled to 1:1. This causes the pump plungers 9β and 9r to be hydraulically locked and the pump plunger 97 to be moved from the pump cylinder 4.
! . The load on each part of the hair ring is removed.

Motor swash plate 27j! . to the high pressure oil chamber 38h, and the oil supply path 61 to the hydraulic servo motor 57.
pass through the valve rod 58a and the closing valve 59, and similarly open into the high pressure oil chamber 38h.

As clearly shown in FIG. 2, on the left end wall of the mission case 1 is a replenishment pump 62 for replenishing the hydraulic closed circuit between the hydraulic pump P and the motor M.
A centrifugal oil filter 63 is provided between the flywheel 6 and the human power shaft 2 to purify the discharged oil.

1-The oil distribution filter 3 is a flat rotary container [; 5
The interior of the rotating container 65 is divided into an inlet chamber 65d and an outlet chamber 65.
It is composed of a partition plate 68 having a through hole 67 that communicates between the two chambers 65; i and (i5b) on the outer periphery.

A boss 100 is provided at the center of each of the rotating container 65 and the partition plate 68.
is fixed, and this boss 100 is connected to a spline 101.
When connected to input shaft 2 via! 1, hair ring 1
It is supported by the mission case l via 02.

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 driving plates 1
04 and 104 are tied together at the outer periphery and connected to the flywheel 6 with bolts 105.

The flange 103 has a plurality of windows 106 spaced at equal intervals on the circumference.
(only one shown in the figure) are drilled and these windows 10
A plurality of windows 10 are also provided on both driving plates 104, 104 corresponding to
7,107 is drilled. A set of these three windows 106,
A shock absorbing member 108 such as a spring or rubber is attached to the drive plates 104 and 104.
Elastic deformation occurs in response to the relative rotation of the rotating container 65.

In order to regulate the amount of elastic deformation of the buffer member 108, both driving plates 104 are provided in a notch 109 provided in the flange 103.
．． The stopper member 110 connected between the drive plate 10
4, 104, etc., are inserted at predetermined intervals in the rotational direction.

The replenishment pump 62 has a drive gear 113 in which a boss 111 is connected to the input shaft 2 via a spline 112, and a driven gear 114 that meshes with the driven gear 114 and is driven. 111 is the rotating container 6
These bosses 100 are arranged adjacent to the bosses 100 of
, 111, an annular oil passage 115 is formed between them. Further, an oil chamber 116 is formed adjacent to the boss 111 of the drive gear 113 and connected to the discharge 1'' 71 of the replenishment pump 62.

As shown in FIGS. 1 and 3, a plurality of oil passages 117 are provided 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.
is formed, and this oil passage 117 communicates between the oil chamber 116 and the annular oil passage 115. In the illustration, when forming the oil passage 117, both the teeth of the boss Ill 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. 1 and 4, a plurality of oil ports 118 are bored in the boss 100 of the rotating container 65, and these oil holes 118 are connected to the annular oil passage 115 and the inlet chamber 6 of the rotating container 65.
5a are connected.

The outlet chamber 65b of the rotating container 65 communicates with an oil passage 74 bored in the center of the input shaft 2, and this oil passage 74 also communicates with the discharge port 41 via a check valve 75 on one side. On the other hand, there is communication between the pump cylinder 4 and the motor cylinder 12 (through an oil chamber 77 and a check valve 76 to the low pressure oil chamber 38I!).

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

A subshaft 78 parallel to the output shaft 16 is rotatably supported by the transmission case 1 between the output shaft 16 of the hydraulic motor M and a well-known differential device connected to a drive wheel (not shown). The output shaft 16 has first and second drive gears 79. ．． 79
□ is fixed in the axial direction with Jr<, and its first drive gear 7
9. The first driven gear 801 that meshes with the second driving gear 79! A second driven gear 8 meshes with the intermediate gear 81 via an intermediate gear 81.
0° is rotatably provided on the sub-shaft 78. Both of the driven gears 801.80□ have a drive clutch gear 82 on each opposing part
．． , 82□, and a driven clutch gear 83 fixed to the subshaft 78 is disposed between them, and this clutch gear 83 is connected to the driven clutch gear 83 through an annular clutch portion 84 that is always engaged with the driven clutch gear 83. Drive clutch gear 82. Alternatively, it can be selectively linked to 82□. Reference numeral 85 denotes a shift fork that operates a clutch unit (As2), which is operated by a hydraulic cylinder (not shown).Furthermore, the subshaft 78 has an actuating device 1 at its left end.
) A gear 87 meshes with a large gear 88, and a parking gear 89 is fixed to the right end.

When the hydraulic motor M rotates, if the clutch member 84 is moved to the left as shown by the solid line and the driven clutch gear 8 is connected to the drive clutch gear 82, the rotational torque of the output shaft 16 becomes The first drive gear 791, the first wave peak i1t, 80., the clutch gear 83, the subshaft 78, the float 87, and the large gear 88 are sequentially transmitted to drive the differential gear in the forward direction within the city. If the clutch member 84 is moved to the right as shown by the chain line to connect the driven clutch member 83 to the drive clutch gear 82□, the rotational torque of the output shaft 16 will be the same as that of the second drive gear 792,
The intermediate gear 81, the second driven gear 80□, the Clara Y gear 83, the subshaft 78, the gear 87, and the large gear 88 are sequentially transmitted to drive the differential in the backward 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 3 is transmitted to the input shaft 2 of the transmission 'F through the transmission path of the flywheel 6, both driving plates 104, 104, the buffer member 108, and the rotating container 65. Also, during engine braking, a reverse load travels in the opposite direction along the transmission path and is transmitted to the crankshaft E.

In either case, when a torque fluctuation occurs between the flywheel 6 and the input shaft 2, the buffer member 108 is elastically deformed to cause relative rotation between the drive plate 104, 104 and the rotating container 65, and this The above torque fluctuation is absorbed by.

The input shaft 2 continues to drive the replenishment pump 62 while it rotates, and the replenishment pump 62 discharges oil drawn from an oil reservoir (not shown) from the discharge lower 1 to the oil chamber 116 at a constant pressure. The oil discharged into the oil chamber 116 flows into the rotating container 65 through the oil passage 117, the ring rod oil passage 115, and the oil hole 11B, and flows from the inlet chamber 65a to the outlet chamber 65b while bypassing the partition plate 68. During the transfer, foreign matter such as cutting chips and abrasion powder in the oil is centrifugally separated, and the foreign matter accumulates on the inner circumferential surface of the rotating container 65.

The oil passed through the rotating container 65 and purified fills the oil passage 74 and the oil chamber 77, and the hair ring 25j of the pump swash plate 241°24r! ,26j! ; Lubricate 25r, 26r, etc. In addition, if hydraulic oil leaks from the hydraulic closed circuit between the hydraulic pump P and the motor, a check valve 75 is installed to compensate for the leakage.
Alternatively, the oil 76 is pushed open to flow into the discharge boat 41 or the low pressure oil chamber 38Il.

As described above, according to the present invention, a rotating container connected to an input shaft and a drive plate rotatably fitted to the outer periphery of the container are deformed according to relative rotation thereof. Since the drive plate is connected to the flywheel with a torque buffer member interposed, the elastic deformation of the buffer member and the accompanying relative rotation between the drive plate and rotating container absorbs torque fluctuations occurring between the engine and transmission. Therefore, generation of vibration due to torque fluctuation can be prevented, and power transmission between the engine and the transmission can be made smooth. Moreover,
Since the rotating container with a relatively large diameter performs the holding function for the buffer member, the buffer member can be held at a sufficient distance in the radial direction from the input shaft without using a special holding member, and therefore the °ζ structure is simple. At the same time, the load on the buffer member can be reduced and its durability can be increased.

[Brief explanation of the drawing]

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 III-III WA and rV-IVi cross sections of Fig. 2. It is a diagram. T...Transmission, P...Hydraulic pump, M...Hydraulic motor, E...Koninjin crank f+llI%1.
...Mission case, 2...Input shaft, 6...Flywheel, 62...Replenishment pump, 65...Rotating container, 65a...Inlet chamber, 65b...Output 1'' chamber, 74
... Supply oil path to the hydraulic closed circuit, 104... Drive plate,
108 ... Cushioning member patent applicant Honda Motor Co., Ltd. Agent Patent attorney Ochiai 4 Figure 4 Figure 3//7 Procedural amendment (self-restraint August 16, 1980, Mr. Commissioner of the Japan Patent Office) , 1. Indication of the case Japanese Patent Application No. 61870 filed in 1982 2 Name of the invention Hydraulic transmission shock absorber 3 Person making the amendment Relationship to the case Patent applicant name (532) Honda Motor Co., Ltd. 4 , representative
Person 〒105 Subject to 5 amendments

Claims (1)

[Claims] The centrifugal filter has an input shaft connected to the flywheel of the crankshaft of the engine through a rotating container, and a hydraulic oil replenishment pump driven by the input shaft, and the inside of the rotating container is connected to the replenishment pump on the one hand. In the hydraulic transmission, the rotary container is connected to the input shaft, and the drive plate is rotatably fitted to the outer periphery of the container. A shock absorbing device for a hydraulic transmission, comprising: interposing a torque buffering member that deforms according to relative rotation between the two, and connecting the drive plate to the flywheel.