JPS59212529A - Oil hydraulic multi-life clutch - Google Patents

Abstract

PURPOSE:To prevent the hopping phenomenon through relief of counter-load using a simple construction by allowing a flywheel installed between a clutch piston and a clutch outer to push open a reed valve installed at the clutch piston when a counter-load is applied, and thereby reducing the pressure in the oil pressure chamber. CONSTITUTION:When a counter-load is transmitted to a clutch, a braking force is applied to a clutch piston 28 together with a clutch center 26 and a clutch outer 22, and the inertia force wants to rotate a flywheel 51 in the regular direction (i) with respect to the abovementioned clutch piston 28. This inertia force draws the ends 52a, 52b of a coupling member 52 to cause reduction of the tilt angle theta of a tilt part 52c, whereby the flywheel 51 approaches the clutch piston 28 to push a push pin 50, which will open a reed valve 49 to release the working oil contained in a pressure chamber 29. Then the leak of this working oil will sink the pressure in the oil pressure chamber 29 to reduce the torque capacity of the clutch.

Description

[Detailed description of the invention]

The present invention relates to a hydraulic multi-plate clutch used in vehicles such as motorcycles. In a vehicle such as a motorcycle, when a vehicle such as a motorcycle suddenly decelerates by downshifting or the like while driving, torque is applied from the rear wheels to the engine in the opposite direction to the normal power transmission direction. If this reverse torque, or reverse load, becomes excessive,
The spring system that serves as the fulcrum of the rear fork suspension is excited, and a vibration called the so-called hopping phenomenon occurs. In order to prevent such vibration 2 from occurring, is there an excessive reverse load? Relaxation is desirable. Conventionally, as a means for alleviating the impact of reverse loads, it has been proposed to provide a mechanism for alleviating the impact of reverse loads, as shown in Fig. 1, in the drive train between the positive movement latch and the engine, which are activated by the operation of the clutch lever. It was done. This reverse load @ shock mitigation clutch is a one-way clutch CI
The one-way clutch C1 includes a clutch inner 2 spline-fitted to the intermediate shaft 1, and an input gear 3 surrounding the clutch inner 2.
A clutch outer 3b using the inner peripheral part 2 of the boss part 3a, and these clutch inner 2 and clutch outer 3b.
When this impact mitigation clutch receives a positive load, the clutch outer 3b and the clutch inner 2 are connected by the locking action of the sprag 40, and when a reverse load is applied, the clutch outer 3b and the clutch inner 2 are connected. The connection between both 3b and 2 is released. Further, the friction clutch 02 is slidably attached to a clutch inner 3C that utilizes the outer circumference of the boss portion 3a of the #J Kidai input gear 3, a clutch outer 5 that surrounds this, and a clutch inner 3c and clutch outer 5, respectively. A plurality of friction plates 6, 7 that are spline-fitted and arranged alternately, and disk blades 8 and 7a1' that urge the clutch outer 5 toward the input gear 3 side and press both M friction plates 6, 7 together. As a prepared item, plate splash 8
The dynamic chip is transmitted according to the zero pressure. Accordingly, at the time of positive load, the 30 revolutions of the input gear driven by the gear 9 on the engine side is the one-way clutch CJ? The power is transmitted to the intermediate shaft l through two systems: one system is transmitted to the intermediate shaft l through the friction clutch CtY, and the other system is transmitted to the intermediate shaft l through the friction clutch CtY, and is then transmitted to the gear 10 on the rear wheel side. Then, due to the reverse load of gear 1071' on the rear wheel side, the intermediate shaft l
is driven, the reverse load is applied to the friction clutch C2
The signal is transmitted to the input gear 3 only through the system that passes through the circuit, and is not transmitted through the system that uses the one-way clutch CI. Therefore, the transmission of excessive reverse load is cut off depending on the strength of the disc spring 8, and is reduced to the extent that it does not cause an impact. But 7. As mentioned above, if we measure the relaxation of the reverse load using the reverse load shock mitigation clutch, the reverse load shock relaxation will be 7f.
Since the O-clutch itself has a complicated structure and is arranged in the drive train separately from the manual clutch, the entire power transmission device has a complicated structure, is large in size, and is expensive. This invention was made in consideration of the above-mentioned circumstances. When a vehicle decelerates, if an excessive reverse load, that is, a driving torque from the rear wheels, is applied, the torque capacity is reduced and the reverse load is reduced. A dedicated clutch is installed separately to alleviate the reverse load when the load is measured and determined (this also eliminates inconveniences such as vibration, making the power transmission system in the vehicle more compact and simplified. , a hydraulic multi-disc clutch that can reduce costs?It is a hydraulic multi-disc clutch that is not available in the past. Between,
A flywheel is provided that approaches the clutch piston when a reverse load is applied, and the flywheel pushes open a reed valve provided on the clutch piston when a reverse load is applied to reduce the pressure in the hydraulic chamber. The present invention 2 will be explained according to the diagram shown in Figs. 2 to 5. In Fig. 2, reference numeral 20 is a transmission shaft. Then, the driving force is applied by two valves of an uninvented hydraulic multi-disc clutch 21' from the engine blade #U (not shown).The clutch 21 has an end wall 22a through which the transmission shaft 20 is inserted.
A peripheral wall portion 22b protruding concentrically from the outer periphery of the transmission shaft 20.
The clutch outer 22 is rotatably supported by the transmission shaft 20 and the clutch outer 2 is rotatably supported by the friction plate 23 and the transmission shaft 20.
a driven gear 24 that supports two gears; and a clutch center that faces inside the clutch outer 22 and is fixed to the transmission shaft 20, and that supports friction plates 25 that are alternately arranged with the friction plates 23 and movable in the axial direction of the transmission shaft. 26 and both friction plates 23 and 257al - disposed between the clutch outer 22 and the clutch center 26 so as to be movable in the axial direction of the transmission shaft, and facing the end wall 22a of the clutch outer 22. a clutch pressure plate 27 having an annular recess 27aY at 1111;
It has an outer peripheral part 28aY that fits into the recess 27a, and is formed in a constant donut plate shape, and is disposed between the clutch pressure plate 27 and the clutch outer 22, and has four parts 27a'a? A hydraulic chamber 29 is formed as part of the chamber wall, and a clutch piston 28 is formed (this clutch piston 28
does not move, and when the clutch pressure plate 27 is activated by hydraulic pressure, the oil supply means 30 which takes out the diameter of the transmission shaft 20 and supplies hydraulic oil to the hydraulic chamber 29 is turned on.
The clutch pressure plate 27 is biased in the direction of the R1 friction plates 23 and 25 by the hydraulic pressure in the hydraulic chamber 29, thereby transmitting power. The driven gear 24 is for transmitting the transmission to the output clutch outer 22 on the engine side, and a protrusion 22C protrudes from the end wall of the clutch outer 22 to the driven gear 24111, and a web of the driven gear 24 perpendicular to the transmission shaft axis. Long hole 2 in the circumferential direction drilled in part 24a
4b, the damper spring 31 is inserted into the driven gear 24 so as to be rotated OT north by a slight angle relative to the driven gear 24, and is elastically connected to the driven gear 24 through a damper spring 31. Due to such a coupling structure between the two, fluctuations in temperature and torque on the engine side are alleviated. The oil feeding means 30 supplies one foot pressure of hydraulic oil into a feed pipe 32 inserted into the hollow transmission 1III 20,
The hydraulic oil is drilled in the transmission shaft 20 and sent into the hydraulic chamber 29 from the communication passage 33.The base end of the feed pipe 320 is connected to the mouthpiece 36 of the crankcase 35 through an orifice 34 valve. The mouthpiece 36 connects to the oil feed pipe (as shown) and connects to the hydraulic pump at the inner bottom of the crankcase 35 (as shown).
It is connected to the. The pressure in the hydraulic chamber 29 is adjusted by leaking constant hydraulic oil supplied by the oil supply means 30, and the transmission torque of the clutch is adjusted by reducing the pressure by 7JO. Hydraulic oil leaks are usually caused by the clutch lever.
This is performed by a hydraulic release device 437 operated by a pressure release device 437 (as shown in the figure), but according to the invention, it is also performed by a pressure reduction device 38.The hydraulic release device 37 is operated by a clutch An operation hole 39 and a leak hole 40 are passed through the four parts 27a of the pressure plate 27, and these holes 39 and 40 are closed off from the hydraulic chamber 291) by the reed valve 41, and furthermore, the clutch center 26 is closed. The operation hole 3 is elastically supported by the clutch lifter plate 42.
A control bin 43 into which the 9 is inserted is provided. The clutch lift plate 42 is connected to the lifter piece 4
4. Camshaft 45. Arm 46. The clutch wire (as shown) is configured to operate in conjunction with the clutch lever by opening two valves, and when the clutch lever is squeezed, the clutch lifter plate 42, that is, the control pin 43, moves to the left in Figure 2. As the reed valve 41 is pushed open and hydraulic oil leaks from the leak hole 40 to the clutch center 26 side, the transmitted torque decreases and the clutch is disconnected. The pressure reducing device 38! L': C1 As shown in FIG.
, an operating section B for opening and closing the pulp section AY, and a force 1. The pulp portion A includes a leak hole 47 and an operation hole 48 that penetrate the clutch piston 28 in the direction of the transmission axis axis and communicate with and exit the hydraulic chamber 29 to the clutch outer 22 side, and these leak hole 47 and operation hole 48 χ hydraulic pressure. It slides freely between the reed valve 49 that is closed from the chamber 29 side and the operation hole 48, and its tip (the right end in FIG. 3) abuts the reed valve 49, and the other end protrudes toward the clutch outer 22 side. The operation part B is arranged between the clutch piston 28 and the clutch outer 22 in order to push the M'+J push bottle 5on and open the reed valve 49. The flywheel 51'lf: a connecting member (hanger spring) 52 which is positioned at an appropriate distance from the clutch piston 28, and which restricts the movement of the flywheel 51 in the direction away from the clutch piston 28. and a stopper circlip 55.The O connecting members 52 are made by bending both ends of the *ta plate in opposite directions, so that they can be bent in half a line from each other, as shown in FIGS. 4 and 5. Both ends 52a spaced apart
, 52b. In this embodiment, it is arranged along the rotational direction between the clutch piston 28 and the flywheel 51, and is arranged along the rotational direction of the clutch outer 22 and the clutch piston 28 (in the normal rotational direction of the engine). An end portion 52a located forward in the direction of rotation by the blade (direction of arrow (a) in FIGS. 4 and 5)
is riveted to the flywheel 5J, and the rear end 52b is riveted to the clutch piston 28, so that the clutch piston 28 and the flywheel 51
When the flywheel 51 tries to rotate in the forward rotation direction relative to the clutch piston 28, the flywheel 51 acts to pull the clutch piston 281ft11 toward the clutch piston 281ft11. In addition, in FIGS. 4 and 5, 53 is a specified relief hole for riveting work, and 54 is a second hole T to avoid interference with the rivet head when the flywheel 51 is aligned with the clutch piston 28 frill. , -6 groove. In the clutch 21, when a load (reverse load) is applied from the road surface to the rear wheel due to sudden deceleration, this reverse negative load is amplified by the intermediate transmission and transmitted to the clutch 21. Ru. Then the clutch piston 28
In addition, due to the reverse load, a braking force acts in the opposite direction to the normal rotation direction together with the clutch center 26, clutch outer 22, etc., and the flywheel 51 rotates in the normal rotation direction against the clutch piston 28 due to inertia.

Attempts to rotate in the direction of arrow (A). Both ends 52a, 52b of the connecting member 52 are pulled by this inertial force, and both ends 52a, 52b are pulled.
When the distance between them becomes a person, the slope part 52 C0) #
45') The angle θ becomes smaller, the flywheel 51 approaches the clutch piston 281i11, the push bottle 50 is pushed, the reed valve 49 is opened, and the hydraulic oil in the pressure chamber 29 leaks. This leak reduces the pressure within the hydraulic chamber 29, reduces the torque capacity of the clutch 21, and alleviates the impact force caused by the reverse load. On the other hand, when the reverse load does not act (and eventually the flywheel 51 and the clutch piston 28 begin to rotate together), the elastic force of the connecting member 520 increases and the reed valve 49
By 0 elastic force, push vinyl 150,7 lie wheel 5
1 returns to its original position, the reed valve 49 closes, and the interior of the °C hydraulic chamber 29 returns to its original closed state. Also, flywheel 5
1 is rotated in the reverse direction, the stopper circlip 55 causes the 72-wheel 51 to rotate in the reverse direction.
7 unnecessary twists on hanger spring 52
Prevention - In addition, in the above-mentioned process, the connecting member 52 is connected to the flywheel 51 and the clutch piston 28
However, it may be connected to the clutch outer 22 as shown in FIG. In this case, the inclination of the connecting member 52 becomes 1 part 52c0)l)J (the oblique angle θ) when a reverse load is applied, and the flywheel 51 approaches the clutch piston 28 accordingly. As usual, the uninvented hydraulic multi-disc clutch (・
When a reverse load is applied, the fixed flywheel disposed between the clutch piston in the hydraulic chamber 29 and the clutch outer moves according to the clutch histone principle, and the movement of the seven flywheels causes the fixed flywheel arranged on the clutch piston to Is it a de-ben? By setting up an EE reducing device that opens the hydraulic chamber by pushing it open, when a reverse load is applied, the hydraulic oil in the hydraulic chamber leaks and the pressure in the hydraulic chamber is reduced, thereby reducing the transmitted torque. Therefore, as a means to reduce the impact force when a reverse load is applied, it is not necessary to provide a clutch for mitigating the reverse load shock as shown in Fig. 1 (which also causes inconveniences such as vibration). In addition, the pressure reducing device of the present invention is incorporated into the hydraulic multi-disc clutch itself, and its constituent parts are simpler than that of the reverse negative impact crest harmonization clutch shown in Fig. 1. Therefore, by applying the present invention, the power transmission device in a vehicle can be made more compact,
Simplification and cost reduction can be achieved.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view of a clutch for mitigating reverse load shocks, Figure 2 is a cross-sectional view of an embodiment of the invention, Figure 3 is an enlarged view of the main parts of Figure 2, Figure 4 is Fig. 3 is a sectional view taken along the line 1v-iv in Fig. 3, Fig. 5 is a cross-sectional view taken along the v-v line in Fig. 4, 20... Transmission shaft, 21... Hydraulic multi-disc clutch, 2
2...Clutch outer, 22a-゛・end μ, 26・
...Clutch center, 27...Clutch clutch plate, 27a...Recess. 38... trick pressure equipment d,
A... Balf section, B... ] squared 1 capital, 47...
Leak, 48°°° operation hole, 49...Lead box, 5
0...4'P L bin, 51...flywheel,
52... Connection member (71 spring), 52a
, 52b-... end, 52c... flj oblique m, s 5
...Stotsunoku-Nakritsubu. Applicant Honde Giken Kogyo Corporation Commissioner of the Patent Office 1. Indication of the case Patent Application No. 84810 of 1984 2 Name of the invention Hydraulic multi-disc clutch 3 Person making the amendment Patent applicant (!; 3) Honda Motor Co., Ltd. 4 Agent drawings

Claims (1)

[Claims] A friction plate formed by a peripheral wall that protrudes concentrically with the transmission shaft from the outer periphery of the end wall through which the transmission shaft passes? Transferred in the direction of the transmission shaft axis # L
a clutch outer supported by the TJNu; a clutch center facing inside the clutch outer and fixed to the transmission shaft and supporting friction plates movably in the axial direction of the transmission shaft, which are alternately arranged with the friction plates; disposed movably in the axial direction of the transmission shaft between the clutch outer and the clutch center to press both friction plates;
A constant clutch pressure plate with an annular recess on the side facing the end wall of the clutch outer, and an outer peripheral portion formed in the recess. a clutch piston formed in a donut plate shape and disposed between the clutch pressure plate and the clutch outer to form a hydraulic pressure with the four parts forming part of the chamber wall; A hydraulic multi-disc clutch is provided with an oil supply means for supplying hydraulic oil to a hydraulic chamber through a valve, and for intermittent transmission of power by the hydraulic pressure in the hydraulic chamber, the clutch piston? A leak hole that penetrates in the direction of the transmission shaft and communicates with the clutch outer of the hydraulic chamber, a reed valve that closes the leak hole from the oil field chamber side, and one end that communicates with the clutch piston. A push pin that abuts the reed valve and projects toward the clutch outer side at the other end, and a flywheel disposed between the clutch piston and the clutch outer to suppress the push pin and push the reed valve open. , is formed by bending both ends of a metal plate in opposite directions, and one end thereof is connected to a flywheel, and the other end is connected to a clutch outer or a clutch piston, so that the flywheel rotates in the normal direction relative to the clutch piston, etc. This hydraulic multi-disc clutch is characterized in that it has a connecting member that moves the flywheel toward the clutch piston side and suppresses the push pin only when a rotational force in the direction is exerted, and a pressure reducing device that is turned on.