JPS6220753Y2 - - Google Patents

Description

[Detailed Description of the Invention] This invention relates to a clutch rotation prevention device that prevents a hydraulic multi-plate clutch that connects and disconnects power from spinning when the power is cut off.

Conventionally, with these hydraulic multi-disc clutches, the driven shaft is dragged and rotated by the rotation of the drive shaft, and it takes a long time for the driven shaft to stop, and when the clutch is disengaged to stop the driven shaft, It has a problem that it does not stop immediately, and for this reason, a brake device is installed that brings the driven shaft side into contact with the fixed machine frame when the clutch is disengaged, and stops the rotation of the driven shaft side immediately. It is now possible that vibrations in this brake device may cause it to operate at unnecessary times, causing resistance to the rotating parts, or in the worst case scenario, the brake device may break and enter the hydraulic path, causing the main unit to malfunction. It had the following drawbacks.

In order to eliminate such defects, the present invention takes the following technical measures. That is, in a hydraulic multi-plate clutch 1 that connects and disconnects power, the clutch housing case 2 on the driven side, which houses the clutch 1 and transmits power through the clutch 1, is provided with a vertical wall 3 on only one side. A piston 4 is inserted into the side having the vertical wall 3 from the open side to provide a hydraulic chamber 5 between the wall surface and the piston 4, and the cylindrical portion has a plurality of notches. 6 is cut into the vicinity of the hydraulic chamber 5, and a donut-shaped brake plate 9 having a cutout part 8 through which the cylindrical wall part 7 excluding the cutout part 6 of the cylindrical part is inserted is attached to the cutout part 6 of the housing case 2. the housing case 2 of the brake plate 9.
In order to provide a coil spring 11 that abuts the outer end surface 10 of the piston 4 on the wall surface side and presses the brake plate 9 toward the piston 4, one end of the coil spring 11 is attached to the housing case along the notch 6 of the housing case 2. A brake wall body 1 is supported on the brake plate 9 side, and the other end is provided in contact with the back of the brake plate 9, and the brake wall body 1 is appropriately fixed on the tension side of the brake plate 9.
Brake lining 13 pressed against the contact surface of 2
The present invention has a configuration of a rotation prevention device for a hydraulic multi-disc clutch, which is characterized by being provided with.

To explain this invention in detail based on an embodiment shown in the drawings, FIG. A cylindrical portion extends toward the left front side in a direction perpendicular to the portion 3 and has an opening 14 at the side end. Reference numeral 6 denotes notches cut into the outer periphery so as to be provided at four equal intervals in parallel with the axial direction of the cylindrical part. It has a protruding structure with four equal parts.

This housing case 2 is arranged so that the vertical wall part 3 is located on the right side as shown in FIG. A hydraulic chamber 5 is formed between the piston 4 and the vertical wall 3.

Next, as shown in FIG. 4, a donut-shaped brake plate 9 having four equally spaced cutouts 8 through which the cylindrical wall 7 is inserted [brake lining 13 on one side of the plate]
] is fitted and inserted from the opening 14 of the housing case 2 so that the brake lining 13 is positioned outside the notch 6 with the brake lining 13 facing the vertical wall 3 side.

The wall surface of the housing case 2 of the brake plate 9 is in contact with the outer end surface 10 of the piston 4, and the center portion thereof is a hole 15 through which shafts pass.

Furthermore, a friction plate 16 which is a clutch body of the multi-plate clutch 1 is in contact with this brake plate 9.
A large number of separator plates 17 are assembled alternately toward the opening 14, and their outermost ends are held down by a stopper plate 18 shown in FIG. 5 and secured by a C-shaped retaining ring 19.

The friction plate 16 has brake linings 20, 20 on both sides, has a circular outer circumference, and has a large number of locking protrusions 21, 21, etc. equally spaced toward the inner circumference. .

The separator plate 17 has outer circumferential protrusions 22 provided at four equal intervals on its outer circumferential portion, and is assembled so as to rotate integrally with the housing case 2 by inserting the protrusions 22 into the notches 6 of the housing case 2.
The inner circumference is simply a circular hole that does not come into contact with other objects.

The outermost stopper plate 18 also has four equally spaced projecting plates 23 projecting outward into the notch 6 of the housing case 2 and fitted therein.

A pin 24 is fixed to the projection plate 23 in a state substantially parallel to the notch 6 so as to protrude long toward the brake plate 9, and the outer periphery of the pin 24 connects the stopper plate 18 and the brake plate 9. A coil spring 11 is inserted between the stopper plate 18 and the brake plate 9 to press the brake plate 9 toward the inner side of the notch 6, that is, toward the piston 4 side.

One end of the pin 24 is fixed to the protruding plate 23 of the stopper plate 18, and the other end faces the brake plate 9 at a constant distance 25.

To explain the side of the vertical wall portion 3 of the housing case 2, a boss portion protrudes inwardly and outwardly from the center of the vertical wall portion 3 with the wall portion in between.
Reference numeral 6 has an outer periphery as a sliding guide for the inner periphery of the piston 4, a power transmitting device such as a spline on the inner periphery of the inwardly protruding boss 26, and an outer periphery of the outwardly protruding boss 27. A bush 28 having an oil passage therein is rotatably fitted into the boss 27, and an oil passage 29 is provided inside the boss 27 to communicate the oil passage in the bush 28 with the hydraulic chamber 5.

Reference numeral 30 denotes a transmission case body, which is separated by a partition wall 31 into a hydraulic clutch chamber 32 and a transmission gear chamber 3.
It is divided into 3.

A driven shaft 34 is supported via a bearing approximately in the middle of the partition wall 31.
connects one end of the shaft to the housing case 2 vertical wall 3
It is fitted into the inner circumferential spline portion of the inwardly protruding boss 26 from the vertical wall portion 3 side to form an integral body, and the other end is pivotally supported by a shaft support wall 35 in the transmission gear chamber 33 via a bearing.

Reference numeral 12 denotes a brake wall body integrally attached to the partition wall 31, in which the hydraulic multi-plate clutch 1 is fitted from the side of the vertical wall portion 3 to the driven shaft 34 protruding from the transmission gear chamber 33 into the hydraulic clutch chamber 32. When inserted together, the brake lining 13 of the brake plate 9 which has protruded outward from the housing case 2 approaches this brake wall 12 in opposition to it, and a contact surface 36 having approximately the same diameter as this brake lining 13 is formed. The brake wall 12 is approximately bowl-shaped, and the housing case 2 is inserted into the bowl-shaped recess 37.
A part of it is inlaid.

38 is a drive shaft, one end of which is attached to the flywheel 40 of the engine 39.
During the 9 rotations, both are constantly rotating. Also, drive shaft 3
A plurality of engagement grooves 38a provided at equal intervals in the axial direction on the outer periphery of the other end of the hydraulic multi-disc clutch 1 have locking protrusions 21, 21, . It fits into the shaft and is integral only in the direction of rotation.

Reference numeral 40 denotes a thrust collar which is inserted between the drive shaft 38 and the driven shaft 34 so as to butt each other, and facilitates rotation while regulating the sliding movement of both shafts in the axial direction.

41 is a retaining ring which is fixed to prevent the driven shaft 34 from coming off the inwardly projecting boss 26 of the clutch body.

The drive shaft 38 is supported by a retaining lid 42 via a bearing and a seal 43 to prevent oil from leaking from the hydraulic clutch chamber 32 to the outside.

Reference numeral 44 denotes a main shaft, whose rotation is interrupted and resumed by a main clutch 45 provided at the flywheel 40 section, and which passes through an opening formed in the center of the drive shaft 38 and driven shaft 34 and enters the transmission gear chamber 33. The rear wheels 4 for driving enter the vehicle through various transmission gears.
Drive 6.

Reference numeral 47 is a sealing body that seals oil leaking into the main clutch 45 portion around the main shaft 44.

Reference numerals 47 and 48 indicate transmission gears provided in the transmission gear chamber 33 portion of the driven shaft 34, and two opposing gears provided at the front end of a PTO shaft 49 provided below and approximately parallel to the driven shaft 34. It rotates while constantly meshing with the shifting driven gears 50 and 51.

52 is a clutch that is always engaged with the PTO shaft 49, and by operating a manual lever (not shown), it engages with either of the driven gears 50, 51 and transmits the gear ratio to the PTO shaft 49, or sets it to a neutral state. , which does not transmit power.

In the partition wall 31 and the brake wall 12, there is an oil hole 5 that communicates the oil passage of the bush 28 with the diversion valve 53.
4,55 are provided.

The diverter valve 53 is fixed externally adjacent to the hydraulic clutch chamber 32.

Next, to explain the operation, a hydraulic pump (not shown) is operated by the driving force of the engine 39 to guide pressure oil to the diverter valve 53, and an opening/closing lever (not shown) provided on the diverter valve 53 is manually operated. When pressure oil flows into the oil hole 54, the pressure oil flows through the oil hole 55, the oil passage provided in the bush 28, the oil passage 29, and the hydraulic chamber 5, moving the piston 4 in the direction of arrow A, and moving the piston 4 outward. The end face 10 similarly presses the brake plate 9 from the side in the direction of arrow A, and simultaneously stops the plurality of friction plates 16 and separator plates 17 held between the brake plate 9 and the stopper plate 18. Press it against the par plate 18 side.

Since brake linings 20, 20 are provided on both sides of the friction plate 16, the friction plate 16 and the separator plate 17 are
are rotated integrally by the pressing force of the piston 4 in the direction of arrow A, and the drive shaft 38 fitted into the inner circumferential protrusions 21, 21, etc. of the friction plate 16, and the outer circumferential protrusion in the notch 6. 22 is plunged in, and the housing case 2 and separator plate 17 rotate integrally. The driven shaft 34, which is integrally fitted to the inwardly protruding boss 26 of the housing case 2, are both in a connected state and rotate, resulting in a so-called clutch ON state.

When pressure oil flows into the hydraulic chamber 5 in this way, the clutch is turned ON and the outer end surface 10 of the piston 4 presses the side of the brake plate 9 in the direction of arrow A, so that the side of the brake plate 9 is pressed. The brake lining 13 in contact with the contact surface 36 of the provided brake wall body 12 is pushed by the piston 4 and moves away from the contact surface 36 against the coil spring 11.

When the brake lining 13 provided on the side surface of the brake plate 9 separates from the contact surface 36 in this way,
The brake plate 9 is no longer in contact with the abutting surface 36, and the contact resistance between the abutting surface 36 and the housing case 2, which is inserted into the brake plate 9 and rotated together through the cylindrical wall 7, is eliminated. can be rotated easily.

As described above, the drive shaft 38 and the driven shaft 34 rotate together, and the gears 47 and 48 for changing speeds provided at the rear end of the driven shaft 34 and the driven gears 50 and 51 for changing speeds provided at the front end of the PTO shaft 49 mesh. Either of the gear ratios is transmitted to the PTO shaft 49 via the clutch 52, and a power take-off shaft 56 protruding rearward from the transmission case 30 is rotated.

Next, when the internal pressure in the oil hole 54 is lowered by manually operating the opening/closing lever provided on the diverter valve 53, the hydraulic chamber 5
The internal pressure also decreases, and the pressing force of the piston 4 disappears, and the piston 4 is pushed back in the opposite direction of arrow A by the pressing force of the coil spring 11 via the brake plate 9.

For this reason, the pressing force that presses the friction plate 16 and the separator plate 17 decreases, and eventually there is a gap between the two members.The friction plate 16 rotates together with the drive shaft 38, and the separator plate 17 is rotating together with the housing case 2 and the driven shaft 34, but since the driving force is cut off between the friction plate 16 and the separator plate 17, the rotation gradually decreases and the driven side finally stops. It is.

At this time, when the brake plate 9 is pushed by the coil spring 11, the brake lining 13 is pushed against the brake wall body 1.
The rotational movement of the brake plate 9 is prevented by being pressed against the abutment surface 36 of the housing case 2, and the rotation of the housing case 2, which is inserted and fitted into the housing case 2 and rotates integrally with the brake plate 9, is also restricted to provide a braking action.

In this way, when the hydraulic clutch 1 is turned OFF and the transmission force between the drive shaft 38 and the driven shaft 34 is cut off, a braking action is simultaneously applied to the housing case 2 to quickly eliminate the rotation on the driven side. It is.

Also, there is a gap 25 between the pin 24 provided on the protrusion plate 23 of the stopper plate 18 and the brake plate 9.
Since this is provided, the brake plate 9 does not come into contact with the pin 24 when the piston 4 moves under the pressure of pressure oil, and the pin 24 acts as a guide when the coil spring 11 expands and contracts, eliminating the possibility of it coming off unexpectedly.

As mentioned above, since the rotation prevention device with a clutch of this invention has the above-mentioned structure, when the clutch is ON, the movement of the piston reliably presses the brake plate and removes the brake lining from the brake wall to avoid unnecessary contact. At the same time, when the clutch is OFF, the action of the coil spring reliably presses the brake lining of the brake plate against the contact surface of the brake wall, quickly stopping the rotation of the housing case, and the brake plate is always pressed against the piston. Alternatively, since the brake plate is pressed by a coil spring, there is no wobbling of the brake plate during rotation, and there is less wear on the brake plate due to unnecessary contact, making it possible to provide a device that can be used for a long period of time.

[Brief explanation of the drawing]

The figures show one embodiment of this invention, in which Fig. 1 is a partially sectional side view showing the overall configuration, Fig. 2 is a side sectional view of the main part, Fig. 3 is a perspective view of the main part, Fourth
5 is a front view of main parts, and FIG. 6 is a sectional view taken along the line A-A in FIG. 2. In the figure, symbol 1 is a hydraulic multi-plate clutch, 2 is a housing case, 3 is a vertical wall, 4 is a piston, and 5
1 is a hydraulic chamber, 6 is a notch, 7 is a cylindrical wall, 8 is a cutout, 9 is a brake plate, 10 is an outer end surface, 11 is a coil spring, 12 is a brake wall, and 13 is a brake lining.

Claims (1)

[Scope of utility model registration request] In the hydraulic multi-plate clutch 1 that connects and disconnects power,
A clutch housing case 2 on the driven side in which the clutch 1 is housed and to which power is transmitted via the clutch 1 is formed into a horizontally cylindrical shape having a vertical wall 3 on only one side, and a piston on the side having the vertical wall 3. 4 is inserted from the open side to provide a hydraulic chamber 5 between the wall portion and the piston 4, and a plurality of notches 6 are cut into the cylindrical portion to the vicinity of the hydraulic chamber 5. A donut-shaped brake plate 9 having a cutout 8 through which the cylindrical wall 7 excluding the cutout 6 is inserted is inserted into the cutout 6 of the housing case 2, and the brake plate 9 is inserted into the cutout 6 of the housing case 2. The outer end surface 1 of the piston 4 is placed on the wall side of the housing case 2.
In order to provide a coil spring 11 that presses the brake plate 9 toward the piston 4 with the coil spring 11 in the abutting state, the coil spring 11 is inserted along the notch 6 of the housing case 2.
One end is supported on the housing case 2 side, and the other end is provided in contact with the back of the brake plate 9, and pressed against the tension surface of the brake plate 9 and the contact surface of the brake wall 12, which is appropriately fixed. This anti-slip device for a hydraulic multi-disc clutch is characterized in that it is provided with a brake lining 13 that prevents the clutch from spinning.