JPS60155014A - Power transmission device - Google Patents

Abstract

PURPOSE:To rotate a Bellerville spring and a pressure-plate indentically together, to prevent both from being worn, by providing a rotation-check between both Bellerville spring and pressure plate. CONSTITUTION:More then one pawl-like projections 52 projected from the inner periphery 51 of a bearing race are fitted into a fitting groove 43 formed in a pressure plate 4 which abuts against a Bellerville spring 2. Further, an outer spline 54 formed in the outer periphery 53 is fitted into an inner spline 18a in a stop ring 198 which is secured to a rear cover 110 so that the Bellerville spring 2 and the pressure plate 4 are rotated, identialy together.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field 1] The present invention relates to a power transmission device having a power cutoff device (clutch) using a disc spring.

``Conventional technology 1'' It has a built-in power coupling clutch using a disc spring, and has a thrust bearing between the spring 1 and Clara f to smooth the relative rotation of both, and also between the bearing and the Tsukuda spring. 1 for
J5 is a fluid coupling with a brake V-plate and a bearing race that uniformly transmits the 1+1 spring load to the clutch.When the engine's rotation fluctuates rapidly, the disc spring and bearing race They are in the same rotation system and follow the rotation fluctuations (Chunkan is Pressure Play 1)
~ is also due to the frictional force of the bearing race (J, same rotation),
Frictional force alone is not enough4.
] If the plate is not in the same rotational system as the engine, the breath plate's own inertial mass will cause a delay in rotational fluctuations (l
I'll leave it alone. When friction occurs between the C spring and the Bnossi I7 play 1, wear occurs at the contact area between the two parts, and the cork changes and the clutch In some cases, the suppressing load on the clutch may decrease, resulting in a 1-lux decrease in the clutch capacity, causing the clutch to slip and causing burnout of the friction material.

[Object 1 of the invention] The object of the present invention is to
Since the clutch rotates at the same time, it prevents wear on both clutches, and since the stroke of the spring does not change, it prevents the pushing cart to the power connection clamp from slipping at a low IZ. Prevent low 1! 1 (゛Kirume Fl+
l Prevents the sliding of the powerful gangway and prevents the friction material from burning out J-
The purpose of the present invention is to provide a power transmission device that can prevent such problems.

``Structure of the Invention'' The power transmission device of the present invention includes a fluid coupling such as a fricoid coupling or a torque converter, and a fluid phase installed in parallel in the case of the fluid coupling, and the outer periphery of a leaf spring. (to the thrust bearing that smoothes the relative rotation between the power cutoff device having a frictional engagement portion to be engaged and the power cutoff device and the book pone, and the thrust I-) In a power cutoff device including a pressure play 1 which is disposed between the bearing races and the springs and which transmits the curved spring load to the power cutoff device (111), the pressure play 1 and the bearing race are rotated at the same time. i) A rotation stopper is provided.

[Configuration 1 of the Invention In addition to the above configuration, the power transmission device of the present invention has the following effects.

b) ■Since the spring and the pressure plate rotate at the same time, it prevents wear on the yamajaku and improves the durability of the book spring and pressure plate 1.

口) Since the stroke length of the book spring does not change, the force applied to the power cutoff clutch Φ is prevented from decreasing.
First, since it prevents the torque capacity of the power cutoff clutch from decreasing, it is possible to prevent the power cutoff clutch from slipping.

C) It is possible to prevent the friction material of the power coupling clutch from burning out.

[Example 1 Based on the embodiment shown in the drawings of the power transmission device of the present invention, 5- Explanation J-ru.

FIG. 1 shows a flow-through J (using a free-hand coupling) according to an embodiment of the present invention.
~ Drive Vehicle Transmission FIG. 2 shows the main parts of the vehicle transmission.

This vehicle transmission has a power output of 1 m (fiff 1) and a forward speed of 4.
It consists of a gear width transmission 200 for one reverse speed, a seven-range differential mechanism (not shown), and a transmission housing 300 housing these.

The power transmission device 1 includes a free coupling (hereinafter referred to as a coupling) 11 and a power cutoff clutch (hereinafter referred to as a clutch) 1 of a power cutoff device provided inside the free coupling.
3 and the outer periphery of the coupling 11.In this embodiment, the direct coupling clutch 15 is installed in the engine hole (the illustrated hole, hereinafter referred to as the right hole), and the input and output portions of the coupling 11. (4 between NQ 1.j oil pump 1
1. Glue 1 for releasing and engaging the clutch 13.
It consists of a bow mechanism 19.

The coupling 11 is attached to the crankshaft of the engine.
6 = Dry Zosoles 1 to 102 are welded to the human power shaft 101 of the connected power transmission device 1 at the outer periphery of fc (, (connected) [-1 to cover 111, applicable) The pump blade 11 is installed around the inner peripheral wall surface of the inner plate-shaped Ritz cover 110 and the i-rear cover 110.
3. Turbine grade 114, OJ, and turbine blade 11 arranged opposite to pump blade 113;
4 and a turbine seal 111).

At the center of the front cover 1 to the cover 111, a large diameter part of the engine side is provided as a piezo 1 to a boss 105, which fits into the bay lower 1 to the hole 104 provided at the center of the end face of the input shaft 101. The tip of the outer glass (not shown, hereinafter referred to as the outer glass) in which the south-central transmission 200 is located serves as the drive shaft 106 of the oil pump 17, and the middle portion serves as the oil pump cover 177 fixed to the oil pump 17 in both directions of the rotating shaft. A center @ 108, which serves as a holding shaft 107, is protruded from the sliding shaft 1 and supported by the sliding shaft 1. A cylindrical portion 111B having a frictional engagement surface 111Δ parallel to the axis formed thereon is connected to the outer periphery of the inner wall of the cover 111 of the cover 1-1.

The clutch 13 has an inner line 133 formed on its inner periphery, a hub-shaped portion 116 of a turbine shell 115 is welded to the outer periphery at the left end in the figure, and damper drive plates 1 to 158B, which are output members of the direct coupling clutch 15, are welded to the outer periphery. , a clutch drum 134 to which a slidably centered kite sleeve 144 is press-fitted, an inner part of the clutch drum 134 is fixed to an oil pump body 170, and a damper spring 157 is provided on the outer circumferential side to hold it. Doing F1
1 head damper plate 1 to 1 8C and a frictional engager on the outer periphery (iIJ coupling hoe clutch 15 force member, said tamper drive plate 158B is attached (pushed, center part shown)). 7 Supports the pressing force of the flamm spring 2, and 6 side faces are rotatably supported with the fan 1 to the cover 111 while transmitting the pressing force of the fluoram spring 2. Nitori 1 = J
The thrust bearing is in contact with the L link race 161, and the clutch drum 134
The damper driven plate 158A is fixed so that the two are perpendicular to each other, and the output 4Ill11 of the transmission device 1 is
A hub part 135 is spline-fitted to the clutch hub part 13, and an outer peripheral spline 136 is formed at a position corresponding to the inner 1 line 133 of the clutch drum 134.
7, and a clap disc wheel 139 consisting of a disc part 138 that connects the hub part 135 and the clutch hub part 131; A clutch disk 1 is spline-fitted to the clutch hub portion 137 of the clutch disk wheel 139 and overlapped with the clutch plate 1 in an intersecting U manner.
It consists of 43.

The direct coupling clutch 15 includes a friction engagement surface 111A formed on the inner peripheral surface of the front 1 to J bar 111 and a friction engagement element 150 supported by the damper drive plates 1 to 158B.

The oil pump 17 uses an internal gear bong 1 in this embodiment, and Hl ti is located between the cover 177 of the oil pump and the disc part 138 of the clutch disc wheel 139 inside the clutch disc wheel 139.
It is being This oil pump 17 is fixed to the cover 177 of the oil pump at its outer circumference, and its inner circumference is loosely attached to the tip small diameter portion 103B of the output 1)Ill 103 of the power transmission H@1 through an A oil seal 175, and the thrust An oil pump body 170 is brought into contact with a disc portion 138 of a clutch disc wheel 139 via a bearing 176, and internal teeth of the oil pump body 170 are rotatably fitted into a rear chamber in which an engine is located. A gear 172, an external gear 171 spline-fitted to the tip of the central shaft 108, and an output @
It is connected to an oil passage 103A formed at the center of the oil pump 103 and connected between the cover 111 of the oil pump and the front cover 111, and includes an inlet 174.

The servo machine I419 of the clutch 13 is connected to a clutch pedal installed in the driver's seat, or a connecting rod 101 connected to a servo mechanism 10 that operates in response to an automatic feed such as intake pipe negative pressure or oil pressure. , supported by the connecting rod 191
? ;< A pressing rod 192 rotated around 193, a bearing 195 attached to a clutch 194 that is in contact with the tip 192Δ of the pressing rod 192, and a sliding sleeve 1 fitted inside the bearing 195.
96, as shown in FIG. 2, there is a reinforcing plate C for the oil seal 197△ between the rear cover 110 and the sliding sleeve 196, which is secured to the sliding sleeve 196 together with the 6 sabots 1-197B in the annular part. A diaphragm spring 2 with an annular plate shape and a diaphragm spring 2 with a spring 11 inserted through the output shaft 103, and a protrusion pressed against the outer periphery 22 of the die (7) shown in FIG. The pressure plate 1 has an abutting part 41 of the strip, an inset vortex part 43 on the inner periphery 42, and a 1-shape protruding in the axial direction at one or more places on the inner periphery 51 corresponding to the inset vortex part 43. It has a claw-like protrusion 52, an outer spline 54 on the outer periphery 53 that fits with an inner spline 198a of a stop ring 198 fixed to the rear cover 110 at one or more places, and a die (7 flam spring 2 and clutch 13). The bearing race 5 of the thrust bearing 3 for smoothing the relative rotation between the bearing race 5 and the suppression ring 199 for suppressing the clutch 13, and the release and sliding (half-clutch) of the clutch 13 being performed manually or automatically, Fit the pawl-like protrusion 52 of the bearing race into the fitting vortex part 43 of the pressure play 1-4, and connect the rotation stopper 6 to the pressure play 1 through the rotation stopper 6. Rotate.

The gear transmission 200 undergoes a known disaster, and the output lI! of the power transmission device 1! Inject l1103 [-shirt 1~
and a dog clutch 202 for switching between the first speed and the second speed, a dog clutch 202 for switching between the first speed and the second speed, and a dog clutch 202 for switching between the first speed and the second speed, and a dog clutch 202 for switching between the first speed and the second speed, and a dog clutch 202 for switching between the first speed and the second speed. It has a switching dog clutch 203 and a reverse gear (not shown).

This power transmission device 1 operates as usual.

The servo mechanism 19 of the clutch 13 operates such that when the connecting rod 191 is operated manually or automatically to the left in the drawing, the pressing rod 192 rotates to the left around the point 193 and displaces the sliding sleeve 196 toward the engine via the bearing 195. Shout out. As a result, the sliding sleeve 196 causes the center of the diaphragm spring 2 to bulge out toward the engine, and the outer periphery 22 of the diaphragm spring 2 is displaced to the left in the figure. This action eliminates the pressing force acting on the clutch 13, and the clamp 13 is released. In this state, the power from the clutch 13 is cut off, so that the gear transmission 200 can perform a gear change operation.

When the pressing force in the left direction in the drawing is released on the connecting rod 191 manually or automatically, the sliding sleeve 196 is displaced to the left in the drawing by the restoring force of the diaphragm spring 2, and the pressing ring 199 is pressed against the engine. clutch 1
3 is engaged, and the input shaft 101 of the power transmission device 1 and the output shaft 1
03 are connected via a coupling 11. At this time, the direct coupling clutch 15 is a centrifugal clutch, and when the rotation speed exceeds a certain level, the clutch starts to engage and starts transmitting power. 13- In the low rotation range, the power is transmitted by the coupling 11 (), and when the rotation of the turbine blade exceeds a certain level, the power is divided and transmitted by both the direct coupling clutch 15 and the coupling 11, and the rotation becomes rough. When the rotation increases and the relative rotation of the coupling 11 ceases, power is transmitted only by the direct coupling clutch 15.

Figure 4.5 shows a second embodiment of the power transmission device of the invention.

In this embodiment, the first outer spline 7 is formed on the first outer spline 54 formed on the outer periphery 53 of the bearing race 5, and on the outer periphery 44 of the pressure plate 4 in correspondence with the first outer spline 54. and a second outer spline 45, and by spline fitting both splines 45 and 54, the repair race 5 and the pressure play 1 are rotated in the same direction.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a vehicle transmission incorporating the power transmission device of the present invention, and FIG. 2 is a sectional view of the main parts of a transmission for light rain incorporating the power transmission device 14 of the present invention. FIG. 3 shows a prefix 1 according to a first embodiment of the power transmission device of the present invention.
? - A front view of the plays 1 to 7 and the ring race; FIG. 4 is a front view of the pressure plays 1 to 7 and the bearing race according to the second embodiment of the power transmission device of the present invention;
FIG. 5 is a sectional view taken along line AA in FIG. 4. In the diagram 1...Power transmission device 2...Die A? Fram spring 3...Thrust bearing 4...Pressure play 1~1]...Bearing race 6
．． 7... Detent portion 15... Direct coupling clutch 10
1... Input shaft 103... Output shaft 11... Noluid Cutting Agent Kenji Ishiguro 15--0 Ku

Claims (1)

[Scope of Claims] 1) A fluid coupling, and a frictional engagement that is installed in the case of the fluid coupling in a -IQ row with the coupling and is pressed and engaged by the outer periphery of a curved spring. A power cut-off device that rotates the thrust bearing to the right, a thrust bearing that smoothes relative rotation between the power cut-off device and the leaf spring, and a fringe disposed between the bearing race of the thrust bearing and the leaf spring, In the power cut-off device which is a replica of the plate spring load applied to the power cut-off device (i), a first toe is provided to prevent the plate spring 11-play 1 and the bearing race from rotating at the same time. Characterized by
Power transmission device. 2) The rotation stopper includes at least one pawl-like protrusion protruding in the axial direction on the inner periphery of the bearing race, and a vortex installed on the inner circumferential side of the pressure play 1 to correspond to the pawl-like protrusion. By fitting the pawl-shaped projection into the groove, a bearing race and a pressure play i~ are formed.
The power transmission device according to claim 1, characterized in that the same rotation is avoided. 3) The rotation stopper is formed from a first outer spline formed on the outer periphery of the bearing race, and a second outer spline formed on the outer periphery of the pressure play 1 to correspond to the first outer spline. The dynamic horn transmission device according to claim 1]+1, wherein the bearing race and the brake plate are rotated in the same manner by spline-fitting both splines.