JPS6113399Y2 - - Google Patents

Description

[Detailed description of the invention] This invention is designed for use by agricultural workers using combine harvesters, tractors, etc., or civil construction workers using wheel loaders, etc., to reduce the amount of travel transmitted to the left and right crawlers or wheels, which are the final travel drive means. This invention relates to a side brake device that brakes left and right crawlers or wheels after power is cut off by a side clutch.

This type of handbrake device can be used instead of the commonly used cone type, for example.
As disclosed in Publication No. 138221 and Publication No. 144533 of 1982, a self-servo type is constructed of a multi-plate type and the braking force is automatically increased once the initial operation of the brake is obtained. When the brake is constructed in a similar manner, it has the advantage of having a large braking capacity and being easy to operate.

The purpose of this invention is to provide the above-mentioned handbrake device, which has a particularly simple and compact structure, and which is designed to provide reliable braking release with a reasonable structure. To provide a new handbrake device for workers.

The side brake device of the present invention that solves this problem of the invention consists of a movable clutch metal fitting 5 of a side clutch 7, which is provided on the side clutch shaft 2 and constantly connected to the final traveling drive means, and a movable clutch metal fitting 5 of the side clutch 7, which is connected to the final traveling drive means at all times and which is provided on the side clutch shaft 2. 1 and a brake housing 14 which is supported so as to be slidable along the axial direction of the side clutch shaft 2 and rotatable only within a regulated range, and friction plates 15 and mating plates 16 arranged alternately are connected to the side clutch shaft. The friction plates 15 and the other surfaces of the friction plates 15 and the mating plates 16 are slidably moved along the two axial directions, and the friction plates 15 and The movable clutch hardware 5 is pressed against the mating plates 16.
The friction plate 15 and the pressure receiving part 19 provided on the inner surface of the transmission case 6 face each other and are supported by the pressing part 18 provided on the inner surface of the transmission case 6, and the friction plate 15 and In addition to providing other pressing portions 20, 20' facing the mating plate 16 group, a ball 23 is placed between the transmission case 1 and the brake housing 14, and the ball 23 lifts up the other pressing portions 20, 20'.
cam grooves 22, 21' having cam slopes 22a, 22b, 21a, 21b that are inclined so that the brake housing 14 is slidably displaced via the balls 23 in a direction that presses the friction plate 15 and the mating plate 16; The brake housing 14 is housed in the other pressing parts 20, 2, and
The ball 23 is moved and energized from the side opposite to 0'.
A compression spring 30 for returning the cam grooves 22, 21' from the shallow parts to the deep parts is provided in the transmission case 1, and the compression spring 30 is inserted into the brake housing 4 on the opposite side of the other pressing parts 20, 20'. It is characterized in that it is configured to act on the brake housing 14 through a press plate 25 that is provided with protrusions 25a intermittently in the circumferential direction that come into contact with the end surface of the brake housing 14.

According to the present invention having the above-mentioned configuration, the side clutch shaft 2
When the movable clutch hardware 5 is slid in the direction of cutting the side clutch 7 at the top, the side clutch 7 is cut.
Since the pressing part 18 provided on the movable clutch hardware 5 pushes the friction plate 15 and the group of mating plates 16 toward the pressure receiving part 19 on the inner surface of the transmission case 1, the friction plate 15
and the mating plate 16 are engaged with each other. Due to this engagement, the rotation of the movable clutch hardware 5, which is constantly interlocked and connected to the final traveling drive means, is caused to rotate through the friction plate 15 and the mating plate 16 to the brake housing 1.
This rotational displacement of the brake housing 14 causes the balls 23 in the cam grooves 22, 21' to move toward the cam slopes 22a, 22b. , 21a, 21b. As the balls 23 ride up, the brake housing 14 is forced to slide against the force of the compression spring 30 in a direction in which the other pressing parts 20 and 20' press the friction plate 15 and the group of mating plates 16. As a result, the friction plate 15 and the group of mating plates 16 are more firmly pressed toward the pressure receiving part 19 on the inner surface of the transmission case 1, and the friction plate 1
5 and the mating plate 16 are firmly engaged, and the movable clutch hardware 5 and the final traveling drive means which are constantly interlocked therewith are braked as required.

When the movable clutch metal fitting 5 is slid on the side clutch shaft 2 in the direction of engaging the side clutch 7 in order to release the brake from the state in which the handbrake is braking, the compression is caused by the brake housing 14 during the brake operation. The compression spring 30 received by the brake housing 14 slides and displaces the brake housing 14 via the pressure plate 25 in a direction opposite to that when the handbrake starts operating. Therefore, the ball 23 moves from the shallow part to the deep part of the cam grooves 22, 21', and the other pressing part 2 of the brake housing 14
0 and 20' separate from the friction plate 15 and the group of mating plates 16, the engagement between the friction plate 15 and the mating plate 16 is released, and the braking by the handbrake is released.

To explain embodiments, the configuration of the handbrake device according to this invention will be described as follows.
In one embodiment shown in the figure, 1 shown in FIG.
Mission case (transmission case) for combine harvesters, etc.
A side clutch shaft 2 is provided in the transmission case 1, and an input transmission is carried on the side clutch shaft 2 from a vehicle speed change section 3, only a portion of which is shown in FIG. A large-diameter gear 4, which is rotated by receiving a large-diameter gear, and small-diameter left and right sliding gears 5, which are meshed with internal teeth 4a formed on the large-diameter gear 4 from the left and right directions, are loosely fitted. As shown in FIG. 1 for the left sliding gear 5, the sliding gear 5, which is a movable clutch metal part, is moved by the shifter 6.
The left and right side clutches 7 are configured to be disengaged by slidingly displacing the inner teeth 4a in the opposite direction on the side clutch shaft 2 to release the engagement with the inner teeth 4a. The left and right sliding gears 5 are constantly meshed with large-diameter gears 9 fitted to the inner ends of left and right transmission output shafts 8 that transmit power to crawlers or wheels (not shown) as the final traveling drive means. It is formed of a wide width that maintains the same, and is permanently operatively connected to the final drive means.

The left and right side brakes 10, which are activated by disengaging the left and right side clutches 7, are constructed of the following multi-plate type. That is, an opening 11 is formed in the transmission case 1 at both ends of the side clutch shaft 2, and the opening 11 is covered with two inner and outer covers 1a and 1b. These covers 1a and 1b cover the second and third covers.
As shown in the figure, the protrusions 1'a, 1'b protruding from the outer circumferential surface of each cover 1a, 1b are positioned by knob pins 12, and each cover 1a, 1b is positioned by a knob pin 12.
It is fixed to the mission case 1 by fastening with threaded bolts 13 at protrusions 1''a and 1''b protruding from the inner peripheral surface of 1b. The boss portion of each sliding gear 5 is located on the cover 1 on the side clutch shaft 2.
a, 1b direction, and in particular, a cylindrical brake housing 14 is disposed on the outer periphery of the extension portion 5a of the boss portion and is separate from the transmission case 1 and the covers 1a, 1b. It is provided in
The brake housing 14 described above has an opening 11
The side clutch shaft 2 is supported on the transmission case 1 so as to be slidable and rotationally displaceable along the axial direction of the side clutch shaft 2, and a protrusion 14a that faces between the protrusions 1''a in the cover 1a is provided at the base end of the side clutch shaft 2 in a circular manner. Friction plates 15 are formed intermittently in the circumferential direction to restrict the rotational displacement range.Friction plates 15 are alternately arranged on the extension portion 5a of the boss portion of the sliding gear 5 and the brake housing 14. and a mating plate 16 are supported so as to be slidable only along the axial direction of the side clutch shaft 2.Furthermore, the boss portion of the sliding gear 5 is provided with a support plate for the friction plate 15 and the mating plate 16 group described above. An annular pressure plate 1 slidably provided in the brake housing 14 from the opposite side of the cover 1a.
When the sliding gear 5 is displaced in the direction in which the side clutch 7 is disengaged, the press section 18 is disposed facing the side clutch 7.
The friction plate 15 and the mating plate 16 are pressed together via the pressure plate 17. Furthermore, a friction plate 15 and a mating plate 1 are attached to the cover 1a from the side opposite to the above-mentioned pressing part 18.
A pressure receiving section 19 facing the sixth group is provided. In particular, the brake housing 14 includes a sliding gear 5.
A ring 20 constituting another pressing portion facing the friction plate 15 and the group of mating plates 16 via the pressure plate 17 from the same direction as the pressing portion 18 is attached.

In the projection 14a described above, a ball accommodation groove 21 is formed in the brake housing 14 on the inner surface side of the projection 14a, and a cam groove 2 facing the ball accommodation groove 21 is formed on the surface of the transmission case 1.
2 is formed between the transmission case 1 and the brake housing 14, as shown in FIG.
2, a plurality of balls 23 facing each other are inserted intermittently in the circumferential direction. Cam groove 2
2 is a cam slope 22 that slopes in one direction in the circumferential direction;
a and a cam slope 22b that slopes in the other direction.

A cylindrical protrusion 2 is provided on the inner surface of the outer cover 1b.
A pressure plate 25 is provided in the cover 1b on the protrusion 24 so as to be movable along the axial direction of the side clutch shaft 2 and rotatably displaceable. This pressing plate 25
There are protrusions 2 intermittently in the circumferential direction on the inner surface of the
5a is fixed, and each protrusion 25a protrudes into the inner cover 1a through a through hole 26 having a constant width in the circumferential direction, which is formed by penetrating the inner cover 1a. The tip of the protrusion 25a faces into the slot 27 formed in the shape of a notch from the outer peripheral end on the back surface of the protrusion 14a of the brake housing 14.
4, that is, the end surface of the brake housing 14 on the opposite side of the ring (pressing portion) 20. Inside the outer cover 1b, on the protrusion 24, a spring bearing ring 2 is placed in contact with the inner surface of the cover 1b and the back surface of the pressing plate 25, respectively.
8 and 29 are provided with a disc spring 30 having both ends received therein. Therefore, the disc spring 30
5, the brake housing 14 is energized to move in the direction of the transmission case 1.

In FIG. 1, reference numeral 31 denotes a return spring that urges the sliding gear 5 to move in the direction of meshing with the internal teeth 4a. As shown in FIG. 1, the transmission case portion 1c, which is located on the outer periphery of the brake housing 19 and in which the cam groove 22 is formed, is formed separately from the main body of the case 1 from the viewpoint of workability.

The handbrake 10 shown in FIGS. 1-4 is constructed as described above, so after removing the sliding gear 5 from the internal teeth 4a by operating the shifter 6 and disengaging the side clutch 7, When the sliding gear 5 is further displaced in the clutch 7 disengaging direction by operating the shifter 6, the pressing portion 18 of the sliding gear 5 presses the friction plate 14 and the mating plate 15 group to the pressure receiving portion 19 via the pressure plate 17. Push the friction plate 1 in the direction
5 and a group of mating plates 16 are pressed against the pressure receiving part 19, and the friction plates 15 and mating plates 16 are engaged with each other. As a result, once the initial operation of the handbrake 10 is obtained, the rotational force of the sliding gear 5 is in a state where it can be transmitted to the brake housing 14 via the friction plate 15 and the mating plate 16. The rotational force transmitted to the moving gear 5 is transmitted to the brake housing 14.
4 is rotationally displaced. At this time, depending on the direction of rotation, the ball 23 climbs up onto one cam slope 22a as shown in FIG. 4b or the other cam slope 22b as shown in FIG. Since the ring 20 is slidably displaced in the direction away from the cam groove 22, the ring 20 moves the friction plate 15 and the mating plate 16 group to the pressure receiving portion 1.
9 direction, thereby increasing the engagement force between the friction plate 15 and the mating plate 16, and the braking action of the handbrake 10 is obtained by such self-servo action. In this case, the greater the rotational torque acting on the brake housing 14, the greater the braking force on the balls 23.
The amount of climbing or biting into the cam slope 22a or 32b becomes large, and the friction plate 15 and the mating plate 16
This is further enhanced because the spaces between the two are more firmly engaged.

When the shifter 6 is operated in the opposite direction to turn off the handbrake 10, the sliding gear 5 is moved toward the internal teeth 4a by the force of the return spring 31. Also, the brake housing 14 is connected to the cam groove 22.
The disc spring 30, whose spring force has been increased by being displaced in the opposite direction, moves and urges the brake housing 14 inward to the transmission case 1 via the press plate 25 and the protrusion 25a thereon. Therefore, the biasing force acts to press the ball 23 against the cam slope 22a or 22b, thereby pushing the ball 23 away from the shallow part of the cam groove 22 between the ball 23 and the cam slope 22a or 22b. A force component in the direction of moving the ball 23 to the deep part is obtained, and the ball 23 is returned to the deep part of the cam groove 22.
The brake housing 14 is also moved to the neutral position, and the handbrake 10 is released. This brake 10 is released by the disc spring 30.
(or a coil spring provided in place of this). That is, brake 10
Return spring 31 for sliding gear 5 during cutting
The brake housing 14 is biased to move slightly in the same direction as the disc spring 30, but this biasing force acts on the brake housing 14 via the friction plate 15 and the mating plate 16, which are released from pressure contact. Depending on the braking torque, it may be difficult to return the brake 10 to neutral if only the return spring 31 is used. The brake is reliably returned to the neutral position, and the brake is reliably released.

Next, let me explain with some modified examples.
First, in the modified example shown in FIG. 5, the groove on the surface of the brake housing 14 corresponding to the ball accommodation groove 21 described above is also a cam groove 21' similar to the cam groove 22, that is, a cam inclined in one direction in the circumferential direction. slope 21a
and a cam groove 21' having a cam slope 20b inclined in the other direction. Its action is the fifth
As is clear from Figure b.

Further, in the modification shown in FIG. 6, another pressing portion 2 corresponding to the ring 20 of the brake housing 14 is
0' is constituted by an inward flange formed at the inner end of the brake housing 14, and the cover 1
Cam grooves 21' and 22 similar to those shown in FIG. 5 are provided in the inward flange 40 at the inner end of the cylindrical separate case part 1c fixed to the transmission case 1 together with a and 1b, and in the brake housing 14, respectively. , balls 23 similar to those described above are accommodated in the cam grooves 21' and 22.
has been established. The other parts are almost the same as those shown in FIG. The effect of the modification shown in FIG. 6 will be obvious without further explanation.

As is clear from the above description, the handbrake device for traveling operators of this invention is provided with a pressing part 18 on the movable clutch metal fitting 5 of the side clutch 7 for disengaging the multi-plate handbrake 10, and a multi-plate side brake device. The brake housing 14 supporting the mating plate 16 of the brake 10 is particularly movable so that the self-servo action of the brake 10 is obtained by rotational and sliding displacement of the brake housing 14 after the initial actuation of the brake 10. It has a particularly simplified structure by omitting a special operating mechanism for the handbrake device, and is compact in that the handbrake mechanism is all housed inside the transmission case. It's summery. In addition to the return spring 31 for the movable clutch hardware 5 described above, the handbrake device of this invention also includes a spring 30 that urges the movably provided brake housing 14 to move in the direction of returning the ball 23 as described above. , so that when the brake 10 is turned off, the ball 23 and the brake housing 14 are reliably returned to the neutral position, thereby achieving reliable brake release. The spring 30 described above is attached to the brake housing 1.
4, the spring 30 is actuated via the pressing plate 25, which is provided with protrusions 25a intermittently in the circumferential direction, which contact the end surface of the brake housing 14. This has the effect that the fastener 13 can be easily placed in a position avoiding interference with the case convex portion for forming the insertion hole shown in the example.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional front view of the essential parts of a traveling work vehicle equipped with an embodiment of this invention, and Figs. 2 and 3 are partially omitted longitudinal sectional side views taken along lines - and - in Fig. 1, respectively. , FIGS. 4a, b, and c are sectional views of essential parts of the same embodiment, and FIGS. 5 and 6 are sectional views showing modified examples, respectively. 1...Mission case (transmission case), 1
a, 1b...Cover, 2...Side clutch shaft,
4...Large diameter gear, 4a...Internal gear, 5...Sliding gear (movable clutch hardware), 7...Side clutch, 8
...Mission output shaft, 9...Large diameter gear, 10...
...Handbrake, 14...Brake housing, 14a...Protrusion, 15...Friction plate, 16...
...Opponent plate, 17...Pressure plate, 18...
... Pressing part, 19... Pressure receiving part, 20... Ring (other pressing part), 20'... Other pressing part, 21... Ball accommodation groove, 21'... Cam groove, 21a, 21b...
...Cam slope, 22...Cam groove, 22a, 22b...
...Cam slope, 23...Ball, 25...Press plate, 25a...Protrusion, 26...Through hole, 27...
...Groove hole, 30... Belleville spring, 40... Flange.

Claims (1)

[Scope of utility model registration request] A movable clutch metal part of the side clutch is provided on the side clutch shaft and is constantly interlocked with the final travel drive means, and a movable clutch metal part of the side clutch is provided on the side clutch shaft within the transmission case and can slide within the transmission case along the axial direction of the side clutch shaft within a restricted range. The brake housing is rotatably supported by the brake housing, and the friction plates and the mating plates arranged alternately are slidable along the side clutch axis direction, and one side of the friction plates and the mating plate group. and a pressure receiving portion provided on the inner surface of the transmission case and a pressing portion provided on the movable clutch hardware so as to press the friction plate and the mating plate group by sliding displacement of the movable clutch hardware in the side clutch cutting direction. The brake housing is provided with another pressing part facing the friction plate and the mating plate group on the pressing part side of the movable clutch hardware, and between the transmission case and the brake housing. A cam groove having a cam slope inclined so that when the ball rides up, the other pressing part presses the friction plate and the mating plate by slidingly displacing the brake housing through the ball. The transmission case further includes a compression spring for moving and energizing the brake housing from the side opposite to the other pressing part to return the ball from the shallow part to the deep part of the cam groove. The compression spring is configured to act on the brake housing through a pressing plate that is provided intermittently in the circumferential direction with protrusions that contact an end surface of the brake housing opposite to the other pressing portion. Become characterized by what you have done,
Handbrake device for mobile workers.