JP2002276745A - Transmission device of industrial vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission device to make shifting between the first speed range and second speed range in which a hydraulic path of a clutch is formed as one system and spring members are arranged in one set. SOLUTION: The transmission device is furnished with a first speed range clutch device 22 of hydraulically operated multi-disc type to connect and disconnect a first speed range clutching gear 16 to/from a clutch shaft 10, a second speed range clutch device 23 of hydraulically operated multi-disc type to connect and disconnect a second speed range clutching gear 17 to/from the clutch shaft 10, and a changeover device 38 to change over these clutch devices 22 and 23 between connection and disconnection, wherein the changeover device 38 is composed of a pressing member 39 reciprocating along the axis E of the clutch shaft 10, the hydraulic path 41 to move the pressing member 39 in the direction A of an end plate 25 for the first speed range by supplying the oil pressure to the pressing member 39, and a spring member to move the pressing member 39 toward another end plate 32 for second speed range.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission device provided in an industrial vehicle such as a wheel type hydraulic excavator vehicle.

[0002]

2. Description of the Related Art Conventionally, as this type of transmission device, for example, as shown in FIGS.
There is a transmission device 101 that can change speed. That is, in the transmission case 102,
Input shaft 104 rotated and driven by hydraulic motor 103
An output shaft 105 that outputs rotation to the wheel side; and a clutch shaft 1 that transmits rotation of the input shaft 104 to the output shaft 105.
06 is provided.

[0003] The input shaft 104 is provided with an input gear 107. The clutch shaft 106 is provided with a clutch gear 108 meshing with the input gear 107, a first-speed clutch gear 109, and a second-speed clutch gear 110. Of these, the clutch shaft 106 and the clutch gear 108 rotate integrally, while the clutch shaft 106 and the first-speed and second-speed clutch gears 109 and 110 are configured to be rotatable individually. I have.

In the transmission case 102, a hydraulic multi-plate type first speed clutch device 111 for connecting and disconnecting the clutch gear 108 and the first speed clutch gear 109, and the clutch gear 108 2
A hydraulic multi-plate type second speed clutch device 112 for connecting and disconnecting the speed clutch gear 110 is provided.

The first-speed clutch device 111 includes a first-speed end plate 113 that rotates integrally with the clutch gear 108, a reciprocating member that rotates integrally with the clutch gear 108 and moves in the direction of the axis e of the clutch shaft 106. A free first-speed piston 114 and a plurality of 1-speed pistons provided between the end plate 113 and the piston 114 so as to intersect each other.
Outer disk 115 and inner disk 11 for speed
6.

Similarly, the second-speed clutch device 112 also has a second-speed end plate 117 that rotates integrally with the clutch gear 108, and an axial center e of the clutch shaft 106 that rotates integrally with the clutch gear 108. And a plurality of second-speed outer discs 119 and inner discs 120 provided between the end plate 117 and the piston 118 so as to intersect each other. I have.

In the clutch shaft 106, a first-speed hydraulic path 1 for moving the first-speed piston 114 in the direction a of the first-speed end plate 113 by pressing the first-speed piston 114 with hydraulic pressure.
22 and a second-speed hydraulic path 123 for pushing the second-speed piston 118 in the direction b of the second-speed end plate 117 by hydraulic pressure, and further pressing the first-speed piston 114 A first-speed return spring 124 for moving in the direction c opposite to the direction a,
A second-speed return spring 125 that pushes the second-speed piston 118 and moves it in the direction d opposite to the direction b.
And are fitted outside.

The output shaft 105 has a first-speed output gear 12 meshed with the first-speed clutch gear 109.
7 and a second-speed output gear 128 meshing with the second-speed clutch gear 110 are provided.

The above-described transmission device 101 is provided in a wheel-type hydraulic shovel vehicle or the like. According to this, when switching to the first speed, the operator switches the speed change lever (not shown) to the first speed side, whereby the hydraulic oil is supplied to the first speed clutch device 111 from the first speed hydraulic path 122. , The hydraulic path 12
The first-speed piston 114 moves in the direction a
And the first-speed outer disk 115 and the first-speed inner disk 116 are sandwiched between the first-speed end plate 113 and the first-speed piston 114 and pressed against each other.
The clutch gear 108 and the first-speed clutch gear 109
Are connected.

At this time, the hydraulic pressure acting on the second speed piston 118 from the second speed hydraulic passage 123 has been released.
The piston 118 for the second speed is pushed in the direction d by the urging force of the return spring 125 for the second speed, and the clutch gear 1
It has been returned to the 08 side. As a result, the connection between the outer disk 119 for the second speed and the inner disk 120 is released, and thus the connection between the clutch gear 108 and the clutch gear 110 for the second speed is released.

As a result, the rotation of the input shaft 104 is transmitted to the clutch gear 108, the clutch shaft 106 is rotated integrally with the clutch gear 108, and the first-speed clutch gear 109 is transmitted via the first-speed clutch device 111. As a result, the rotation of the clutch gear 109 for the first speed is transmitted to the output gear 127 for the first speed, and the output shaft 105 rotates at the speed ratio of the first speed.

In the case of switching to the second speed, the operator switches a speed change lever (not shown) to the second speed side, so that hydraulic oil is supplied from the second speed hydraulic path 123 to the second speed clutch device 112. And the hydraulic path 123
The second-speed piston 118 moves in the direction b due to the hydraulic pressure from the second gear, and the second-speed outer disk 119 and the inner disk 120 are sandwiched between the second-speed end plate 117 and the second-speed piston 118 and pressed against each other. Therefore, the clutch gear 108 and the second-speed clutch gear 110 are connected.

At this time, the hydraulic pressure acting on the first-speed piston 114 from the first-speed hydraulic path 122 has been released.
The first-speed piston 114 is pushed in the direction c by the urging force of the first-speed return spring 124 and the clutch gear 1
It is returned to the 08 side. As a result, the connection between the first-speed outer disk 115 and the inner disk 116 is released,
Thus, the clutch gear 108 and the first-speed clutch gear 109 are disconnected.

As a result, the rotation of the input shaft 104 is transmitted to the clutch gear 108, the clutch shaft 106 rotates integrally with the clutch gear 108, and the second-speed clutch gear 110 is connected via the second-speed clutch device 112. As a result, the rotation of the clutch gear 110 for the second speed is transmitted to the output gear 128 for the second speed, and the output shaft 105 rotates at the speed ratio of the second speed.

[0015]

However, in the above-mentioned conventional type, since two clutch hydraulic paths, that is, the first-speed hydraulic path 122 and the second-speed hydraulic path 123, are required, the structure and hydraulic control are not sufficient. There is a problem that it becomes complicated.
Also, return springs 124 and 125 (elastic members)
However, since two sets, one for the first speed and the other for the second speed, are required, there is a problem that the number of parts increases and the cost increases.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a transmission device for an industrial vehicle, which has a single hydraulic pressure path for the clutch and can further reduce the number of elastic members (such as return springs).

[0017]

SUMMARY OF THE INVENTION In order to achieve the above object, a first aspect of the present invention provides an industrial system capable of shifting between one speed having a specific speed ratio and the other speed having a different speed ratio from one speed. A transmission device for a vehicle, in a transmission case, an input shaft that is rotationally driven by a driving device, an output shaft that outputs rotation to a wheel side, and a clutch shaft that transmits rotation of the input shaft to the output shaft. The input shaft is provided with an input gear for one speed and an input gear for the other speed, and a clutch gear for one speed and an input for the other speed meshed with the input gear for one speed. The other-speed clutch gear meshing with the gear is fitted around the clutch shaft in a rotatable state, and the one-speed clutch gear connects and disconnects the one-speed clutch gear and the clutch shaft. Clutch equipment A clutch device for connecting and disconnecting the clutch gear for the other speed and the clutch shaft, and a switching device for switching the clutch device for one speed and the other speed to connect and disconnect. The one-speed clutch device includes a plurality of one-speed inner disks and one-speed end plates that rotate integrally with the clutch shaft, and one-speed clutch gear that rotates integrally with the one-speed clutch gear. The clutch device for the other speed has a plurality of inner disks for one speed and a plurality of outer disks for one speed alternately arranged, and the plurality of inner disks for the other speed rotate integrally with the clutch shaft. And an end plate for the other speed, and a plurality of end plates that rotate integrally with the clutch gear for the other speed and that are alternately arranged with the inner disk for the other speed. The switching device includes a pressing member that is reciprocally movable in the axial direction of the clutch shaft, and a fluid member that supplies the pressing member to the pressing member for the one-speed operation. A fluid pressure path for moving the pressing member in the direction of the end plate, and an elastic member for moving the pressing member in the direction of the other speed end plate. The inner disk and the outer disk for one speed are located, the inner disk and the outer disk for the other speed are located between the pressing member and the end plate for the other speed, and the fluid pressure path is formed on the clutch shaft. The transmission gear provided on the clutch shaft and the output gear provided on the output shaft mesh with each other.

According to this, the switching device switches the one-speed clutch device to the connected state and the other-speed clutch device to the disconnected state, whereby the one-speed clutch gear and the clutch shaft are connected and the other one is connected. The speed clutch gear and the clutch shaft are disconnected. This allows
The rotation of the input shaft is transmitted to the output shaft via the clutch shaft,
At this time, the output shaft rotates at a one-speed speed ratio. Further, the switching device switches the clutch device for one speed to disconnect and the clutch device for the other speed to connection,
The one-speed clutch gear and the clutch shaft are disconnected, and the other-speed clutch gear and the clutch shaft are connected. Thus, the rotation of the input shaft is transmitted to the output shaft via the clutch shaft, and at this time, the output shaft rotates at the other speed ratio.

The switching device switches to one speed by the following operation. That is, by supplying fluid pressure to the pressing member from the fluid pressure path, the pressing member is pressed by the fluid pressure and moves in the direction of the one-speed end plate, and the one-speed inner disk and the outer disk are pressed by the pressing member. And the first-speed end plate are pressed against each other, so that the one-speed clutch gear and the clutch shaft are connected via a one-speed clutch device.

At this time, since the pressing member moves in the direction of the one-speed end plate as described above, the pressing member moves away from the other-speed end plate.
The distance between the pressing member and the end plate for the other speed is increased, whereby the connection (pressure contact) between the inner disk and the outer disk for the other speed is released, and thus the clutch gear and the clutch for the other speed are released. The shaft and the shaft are disconnected via the clutch device for the other speed.

When switching to the other speed, the following operation is performed. That is, by releasing (lowering) the fluid pressure acting on the pressing member from the fluid pressure path, the pressing member is pushed by the elastic force of the elastic member, moves in the direction of the other speed end plate, and moves in the direction of the other speed. Since the inner disk and the outer disk are sandwiched between the pressing member and the end plate for the other speed and pressed against each other, the clutch gear for the other speed and the clutch shaft are connected via the clutch device for the other speed.

At this time, since the pressing member moves in the direction of the end plate for the other speed as described above, the pressing member moves away from the end plate for the one speed.
The distance between the pressing member and the one-speed end plate is increased, whereby the connection (pressure contact) between the one-speed inner disk and the outer disk is released, and thus the one-speed clutch gear and the clutch are released. The shaft and the shaft are disconnected via the one-speed clutch device.

As described above, the shift can be performed with the hydraulic path of the clutch as one system, so that the structure and the hydraulic control are simplified. Further, since the number of elastic members can be reduced from two to one in the related art, the number of parts is reduced, leading to cost reduction.

According to the second aspect of the present invention, there is provided a release clutch device for connecting and disconnecting the output shaft and the output gear. According to this, one of the one-speed clutch device and the other-speed clutch device is always in a connected state, so if the vehicle is towed due to a failure or the like, the output clutch device is used by the release clutch device. And the output gear are disconnected. Thus, when the vehicle is towed, the output shaft also rotates according to the rotation of the wheels, but the rotation of the output shaft is not transmitted to the output gear, and therefore,
The rotation of the output shaft does not rotate the clutch shaft. Thereby, even if one of the clutch device for the one speed and the clutch device for the other speed is in the connected state,
The vehicle can be towed.

[0025]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS. As shown in FIG.
Reference numeral 1 denotes a wheel-type hydraulic excavator vehicle (an example of an industrial vehicle). A turnable base 40 is provided on a vehicle body 2, and a driver's cab 3 that turns together with the base 40 is provided on the base 40.
And an excavator 4 for excavation. The vehicle body 2 has a plurality of wheels 5 for traveling, a hydraulic motor 6 (hydrostatic motor) for rotating each wheel 5 as shown in FIG.
Transmission device 7 for shifting to a high speed (an example of the other speed), a hydraulic pump (hydrostatic pump: not shown) for supplying hydraulic oil to the hydraulic motor 6, and an engine (not shown) for operating the hydraulic pump Are provided.

The transmission device 7 is configured as follows. That is, as shown in FIGS. 1 to 3, an input shaft 9 rotated by the hydraulic motor 6 (an example of a driving device) is provided in a transmission case 8.
An output shaft 11 for outputting rotation to the respective wheels 5, and a clutch shaft 1 for transmitting rotation of the input shaft 9 to the output shaft 11.
0, and are arranged such that the axes of the shafts 9, 10, 11 are parallel to each other.

The hydraulic motor 6 is mounted outside the transmission case 8, and a drive shaft 12 of the hydraulic motor 6 is connected to the input shaft 9. The input shaft 9 is integrally provided with an input gear 14 for first speed (one speed) and an input gear 15 for second speed (other speed).

The clutch shaft 10 has a first speed (one speed) clutch gear 16 meshed with the first speed input gear 14 and a second speed (the other) meshed with the second speed input gear 15. And a transmission gear 18 for transmitting the rotation of the clutch shaft 10 to the output shaft 11. Both clutch gear 1
Since the clutch gears 6 and 17 are fitted to the clutch shaft 10 via bearings 19 and 20, respectively, the clutch gears 16 and 17 and the clutch shaft 10 are configured to be rotatable individually. The transmission gear 18 is fixed so as to rotate integrally with the clutch shaft 10.

The clutch gear 16 for the first speed and the clutch shaft 10 are connected and disconnected by a clutch device 22 for the first speed (one speed), and the clutch gear 17 for the second speed and the clutch shaft 10 are connected to each other by two. The connection and disconnection are performed by the clutch device 23 for the high speed (the other speed).

That is, the first-speed clutch device 22
Is a hydraulic (wet) multi-plate clutch, which is formed on a cylindrical first-speed outer spline portion 24 provided on the first-speed clutch gear 16 and an inner peripheral surface of the outer spline portion 24. A spline tooth 24a, a disc-shaped first-speed (one-speed) end plate 25 externally fitted and fixed to the clutch shaft 10, and a cylindrical first-speed end plate provided on the first-speed end plate 25. Inner spline portion 26, and spline teeth 26a formed on the outer peripheral surface of the inner spline portion 26
A plurality of disc-shaped outer disks 27 for one speed (one speed) spline-fitted to the spline teeth 24a of the outer spline portion 24; And a plurality of disc-shaped inner disks 28 for one speed (one speed).

Note that the inner peripheral surface of the outer spline portion 24 and the outer peripheral surface of the inner spline portion 26 are radially opposed, and the center axis of the outer spline portion 24 and the inner spline portion 26 is It coincides with the axis E. Also,
The spline teeth 24a and 26a are formed in the direction of the axis E of the clutch shaft 10. In addition, each outer disk 2
Numerals 7 are inserted into the gaps between the inner disks 28 and are alternately arranged with the inner disks 28. As a result, each outer disk 27 is connected to the clutch gear 16 for the first speed.
And the inner disk 28 can be slid in the direction of the axis E of the clutch shaft 10.
Can be slid in the direction of the axis E.

Similarly, the second-speed clutch device 23 is a hydraulic (wet) multi-plate clutch, and is a cylindrical second-speed outer spline portion 31 provided on the second-speed clutch gear 17. A spline tooth 31a formed on the inner peripheral surface of the outer spline portion 31, a disk-shaped second speed (the other speed) end plate 32 externally fitted and fixed to the clutch shaft 10; A second-speed internal spline portion 33 provided on a speed end plate 32 and spline teeth 33 formed on the outer peripheral surface of the inner spline portion 33.
and a plurality of disc-shaped second speeds (the other speed) spline-fitted to the spline teeth 31a of the outer spline portion 31
And a plurality of disc-shaped inner discs for the second speed (the other speed) which are spline-fitted to the spline teeth 33a of the inner spline portion 33.

The inner peripheral surface of the outer spline portion 31 and the outer peripheral surface of the inner spline portion 33 are radially opposed, and the center axis of the outer spline portion 31 and the inner spline portion 33 is It coincides with the axis E. Also,
The spline teeth 31a and 33a are formed in the direction of the axis E of the clutch shaft 10. In addition, each outer disk 3
4 are inserted into the gaps between the inner disks 35 and are alternately arranged with the inner disks 35. Thereby, each outer disk 34 is provided with the clutch gear 17 for the second speed.
And the inner disk 35 is slidable in the direction of the axis E of the clutch shaft 10.
Can be slid in the direction of the axis E.

Between the clutch device 22 for the first speed and the clutch device 23 for the second speed, the clutch devices 2
Switching device 3 for switching connection and disconnection between 2, 23
8 are provided. The switching device 38 includes a pressing member 39 that can reciprocate in the direction of the axis E of the clutch shaft 10, and a pressing member 39 that moves the pressing member 39 in the direction A of the end plate 25 for the first speed.
(See FIG. 2) A hydraulic path 41 (an example of a fluid pressure path) for moving the pressing member 39 in the direction B of the end plate 32 for the second speed (that is, a direction opposite to the direction A: see FIG. 3). And a spring member 42 (an example of an elastic member). The spring member 42 includes a plurality of disc springs 42a.
Are combined in series.

The pressing member 39 is formed in an annular shape and is externally fitted to the clutch shaft 10. The pressing member 39 has a pressing surface 43 for the first speed facing the inner disk 28 at the end of the clutch device 22 for the first speed. And a second-speed pressing surface 44 facing the inner disk 35 at the end of the second-speed clutch device 23. The pressing member 39 and the end plate 2 for the first speed are used.
5, the first-speed outer disk 27 and the inner disk 28 are positioned, and the second-speed outer disk 34 and the inner disk 35 are positioned between the pressing member 39 and the second-speed end plate 32. are doing.

In the inside of the pressing member 39, a working oil space 45 into which working oil (an example of working fluid) can enter and exit is provided.
And a storage space 46 for storing the spring member 42,
The partition plate 47 is formed by partitioning. Incidentally, the partition plate 47 is formed in a disk shape and is fitted to the clutch shaft 10 outside. The spring member 42 is configured to be able to expand and contract in the direction of the axis E of the clutch shaft 10.

The clutch shaft 10 is provided with the hydraulic path 4
1, a hydraulic passage 48 is formed.
Has one end opened to one end of the clutch shaft 10 and the other end opened to the working oil space 45. One end of the hydraulic passage 48 is connected to a hydraulic circuit (not shown) that supplies and discharges hydraulic oil, and this hydraulic circuit is configured to operate by operating a shift lever (not shown) in the cab 3. Have been. Further, a lubricating oil supply path (not shown) for supplying lubricating oil to the bearings 19 and 20 and the inner spline portions 26 and 33 is formed in the clutch shaft 10.

The transmission gear 1 is connected to the output shaft 11.
An output gear 50 meshing with the outer gear 8 is externally fitted with a certain gap. Thus, the output shaft 11 and the output gear 50 are individually rotatable.

The transmission device 7 is provided with a release clutch device 51 for connecting and disconnecting the output shaft 11 and the output gear 50. As shown in FIGS. 4 to 6, the release clutch device 51 moves the output shaft 1 between the connection position C and the disconnection position D.
The shift sleeve 52 includes an annular shift sleeve 52 that can reciprocate in one axial direction F and a moving unit 53 that moves the shift sleeve 52 to a connection position C and a disconnection position D.

A groove 54 is formed on the outer peripheral surface of the shift sleeve 52 over the entire circumference.
The sleeve-side spline teeth 55 in the axial direction F of the output shaft 11 are formed on the inner peripheral surface of the second shaft 2. Further, the outer peripheral projection 11a of the output shaft 11 and the hub 50 of the output gear 50 are provided.
The output shaft side spline teeth 56 and the gear side spline teeth 57 meshing with the sleeve side spline teeth 55 are formed on the outer peripheral surface of the line a. As shown in FIG. 4, when the shift sleeve 52 is located at the connection position C, the sleeve-side spline teeth 55 mesh with both the output shaft-side spline teeth 56 and the gear-side spline teeth 57, As shown in FIG. 5, when the shift sleeve 52 is located at the disconnection position D, the sleeve-side spline teeth 55 separate from the gear-side spline teeth 57 and mesh only with the output shaft-side spline teeth 56. .

The moving means 53 is supported in the transmission case 8 and is reciprocally movable in the axial direction F of the output shaft 11, and is provided orthogonal to the moving shaft 58. Shift yoke 59
And a coil spring 60 for returning the moving shaft 58 from the disconnection position D to the connection position C.
The moving shaft 58 is moved from the connection position C to the connection release position D against the urging force (extension force) of the spring 60.
And an operation bolt 61 to be pushed in the direction of.

The moving shaft 58 is connected to a cylindrical support member 62 provided in the transmission case 8.
63 and is supported. Further, the shift yoke 59 is attached to a boss portion 64 which is externally fitted to the moving shaft 58 and fixed integrally therewith. The distal end of the shift yoke 59 has U-shaped forked portions 59a and 59b, and the distal ends of the forked portions 59a and 59b are formed with engaging portions 65 that engage with the grooves 54 of the shift sleeve 52. Have been. The spring 60 is fitted around the moving shaft 58 and is provided between the support member 63 and the boss 64. The operation bolt 61 is screwed into a mounting member 66 provided on the outside of the transmission case 8, and as shown in FIG. 61
And is pushed in the direction from the connection position C to the connection release position D.

As shown in FIG. 1, the transmission device 7 is operated by operating a parking brake lever (not shown) in the cab 3 to operate the clutch shaft 1.
A parking brake device 67 for braking 0 is provided. The parking brake device 67 is operated by the urging force (extension force) of the brake spring 68,
In addition, the operation is released by hydraulic pressure against the urging force. The supply of the hydraulic pressure for releasing the operation to the parking brake device 67 and the supply of the clutch hydraulic pressure to the hydraulic passage 48 are performed by the hydraulic pump (not shown).

The wheels 5 are connected to both ends of the output shaft 11 via a differential (not shown), a propeller shaft, and the like. Less than,
The operation of the above configuration will be described.

When the vehicle 1 is driven at the first speed, the operator in the cab 3 switches the gear shift lever to the first speed side, and as shown in FIG. The pressure member 39 is supplied to the space 45, and the pressing member 39 is pushed by the hydraulic pressure in the working oil space 45 to move in the direction A of the first-speed end plate 25, and the first-speed outer disk 27 and the inner-disk 28 are pressed by the pressing member. The first-speed clutch gear 16 and the clutch shaft 10 are connected via the first-speed clutch device 22 because the first-speed clutch gear 16 and the first-speed clutch gear 22 are connected to each other by being pressed between the first-speed end plate 39 and the first-speed end plate 25.

At this time, when the pressing member 39 moves in the direction A as described above, the pressing member 39 moves away from the end plate 32 for the second speed, so that the spring member 42 is compressed, and the pressing member 39 and the second speed The distance from the end plate 32 for the second speed is increased, so that the outer disc 3 for the second speed is provided.
The connection (pressure welding) between the inner disk 35 and the inner disk 35 is released,
Thus, the clutch gear 17 for the second speed and the clutch shaft 10 are disconnected via the clutch device 23 for the second speed.

As a result, the input shaft 9 is rotated by the hydraulic motor 6, and the input gear 1 for the first speed and the second speed is integrally formed with the input shaft 9.
4 and 15 rotate, and the first speed clutch gear 16 meshed with the first speed input gear 14 and the second speed clutch gear 17 meshed with the second speed input gear 15 rotate. At this time, as described above, the first-speed clutch gear 16 and the clutch shaft 10 are connected via the first-speed clutch device 22, and the second-speed clutch gear 17 and the clutch shaft 10 are connected to each other. Is disconnected via the second-speed clutch device 23, so that the clutch shaft 10 rotates integrally with the first-speed clutch gear 16. 1st speed clutch gear 1
The rotation of No. 6 is transmitted to the output shaft 11 via the transmission gear 18 and the output gear 50, and the output shaft 11 rotates at the first speed gear ratio.

When the vehicle 1 is driven at the second speed By switching the gear shift lever to the second speed side, the hydraulic pressure acting on the pressing member 39 from the hydraulic passage 48 is released (lowered), and as shown in FIG. The spring member 42 is extended, and the pressing member 39 is pushed by the extension force (biasing force) of the spring member 42 to move in the direction B of the second-speed end plate 32, and the second-speed outer disk 34 and the inner-disk 35 is sandwiched between the pressing member 39 and the second-speed end plate 32 and pressed against each other.
7 and the clutch shaft 10 are connected via a clutch device 23 for the second speed.

At this time, the pressing member 39 moves in the direction B of the end plate 32 for the second speed as described above, so that the pressing member 39 moves away from the end plate 25 for the first speed. The distance between the first-speed end plate 25 and the first-speed end plate 25 is increased, whereby the connection (pressure contact) between the first-speed outer disk 27 and the inner disk 28 is released. The connection with the clutch shaft 10 is released via the clutch device 22 for the first speed.

As a result, the clutch gear 17 for the second speed and the clutch shaft 10 are connected via the clutch device 23 for the second speed, and the clutch gear 16 for the first speed and the clutch shaft 10 are connected to each other. Since the connection is released via the speed clutch device 22, the clutch shaft 10 rotates integrally with the second speed clutch gear 17. The rotation of the clutch gear 17 for the second speed is performed by the transmission gear 18 and the output gear 50.
To the output shaft 11, and the output shaft 11 rotates at the second gear ratio.

As described above, the hydraulic path 41 of the clutch is
Since the transmission can be performed in a system, the structure and the hydraulic control are simplified. Further, since the number of elastic members such as the spring member 42 can be reduced from two to one, the number of parts is reduced, which leads to cost reduction.

In the event that the engine or the hydraulic pump fails and stops, the hydraulic pump 6, the hydraulic passage 48, and the parking brake device 67
Supply of hydraulic oil to the pump has stopped,
The hydraulic motor 6 stops, and the hydraulic pressure in the working oil space 45 decreases, and as shown in FIG. 3, the spring member 42 expands, and the clutch gear 17 for the second speed and the clutch shaft 10
The connection is established via the speed clutch device 23, and the parking brake device 67 is operated by the urging force of the brake spring 68 (see FIG. 1).
The operation cannot be canceled because the hydraulic pressure for canceling the operation is interrupted.

In the case of such a failure, the vehicle 1 is towed. Before towing, as shown in FIG. By tightening, the moving shaft 58 is pushed by the tip of the operating bolt 61 and is pushed in the direction from the connection position C to the connection release position D.
0 is compressed, the shift sleeve 52 moves from the connection position C to the disconnection position D via the shift yoke 59, and the sleeve side spline teeth 55
7, the connection between the output shaft 11 and the output gear 50 is released.

In this state, when the vehicle 1 is towed, the output shaft 11 also rotates according to the rotation of the wheels 5, but the rotation of the output shaft 11 is not transmitted to the output gear 50. Accordingly, even if the clutch gear 17 for the second speed and the clutch shaft 10 are connected via the clutch device 23 for the second speed, or the operation release of the parking brake device 67 is disabled, Since the vehicle 1 can be towed, a failure can be dealt with quickly and easily.

During normal running, as shown in FIG. 4, when the operator turns the operation bolt 61 in the reverse direction to loosen it, the moving shaft 58 causes the urging force (extension force) of the spring 60 to move. ) To return to the connection position C from the disconnection position D, the shift sleeve 52 moves from the disconnection position D to the connection position C via the shift yoke 59, and the sleeve side spline teeth 55 are changed to the output shaft side spline teeth. The output shaft 11 and the output gear 50 are connected so as to mesh with both the gear 56 and the gear-side spline teeth 57. Thus, during normal running, the rotation of the output gear 50 is reliably transmitted via the release clutch device 51 to the output shaft 11.
Is transmitted to

In the above embodiment, the wheel-type hydraulic shovel vehicle 1 has been described as an example of the industrial vehicle, but may be another type of industrial vehicle such as a wheel loader. In the above embodiment, the hydraulic motor 6 is used as an example of the driving device.
However, an electric motor, an engine, or the like may be used.

In the above embodiment, a hydraulic pressure is used as the fluid pressure. However, a liquid other than hydraulic oil or a gas such as air may be used. In the above-described embodiment, one example of one speed is 1
Although the second speed was mentioned as an example of the other speed,
The speed is not limited to the second speed, but may be the third speed and the fourth speed, for example.

In the above embodiment, the spring member 42 is used as an example of the elastic member. However, the present invention is not limited to the spring member 42. Further, the spring member 42 is formed by a plurality of disc springs 42.
a, but a single disc spring 42a
May be configured. Further, as the spring member 42, a type other than the disc spring 42a, for example, a coil spring or the like may be used.

In the above embodiment, the pressing member 39 is moved in the direction A (see FIG. 2) by hydraulic pressure and in the direction B (see FIG. 3) by the spring member 42.
It may be moved in the direction A by the spring member 42 and moved in the direction B by the hydraulic pressure.

[0060]

As described above, according to the first aspect of the present invention, the shift can be performed with one hydraulic path of the clutch, so that the structure and the hydraulic control are simplified. In addition, since the number of elastic members can be reduced from the conventional two sets to one set,
The number of parts is reduced, leading to cost reduction.

According to the second aspect of the invention, when the vehicle is towed due to a failure or the like, the output shaft and the output gear are disconnected by the release clutch device, so that the vehicle can respond to the rotation of the wheels. The output shaft also rotates, but the rotation of the output shaft is not transmitted to the output gear. Thus, even if one of the one-speed clutch device and the other-speed clutch device is in the connected state, the vehicle can be towed.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a transmission device for a hydraulic shovel vehicle according to an embodiment of the present invention.

FIG. 2 is a diagram of a clutch shaft portion of the transmission device of the hydraulic excavator vehicle, in which a first-speed clutch gear and a clutch shaft are connected, and a second-speed clutch gear and a clutch shaft are disconnected. It shows the state that it was turned on.

FIG. 3 is a view of a clutch shaft portion of the transmission device of the hydraulic excavator vehicle, in which a first-speed clutch gear and a clutch shaft are disconnected, and a second-speed clutch gear and a clutch shaft are connected. It shows the state that it was turned on.

FIG. 4 is a diagram of the release clutch device of the transmission device of the hydraulic shovel vehicle, showing a state where an output shaft and an output gear are connected.

FIG. 5 is a diagram of the release clutch device of the transmission device of the hydraulic shovel vehicle, showing a state where an output shaft and an output gear are disconnected.

6 is a view as viewed in the direction of arrows XX in FIG. 4;

FIG. 7 is a diagram of the hydraulic excavator vehicle.

FIG. 8 is a cross-sectional view of a conventional transmission device.

FIG. 9 is a view of a clutch shaft part of a conventional transmission device.

[Explanation of symbols]

 Reference Signs List 1 hydraulic excavator vehicle (industrial vehicle) 5 wheels 6 hydraulic motor (drive device) 7 transmission device 8 transmission case 9 input shaft 10 clutch shaft 11 output shaft 14 input gear for first speed 15 input gear for second speed 16 first speed Clutch gear 17 for 2nd speed 18 clutch gear for 2nd transmission 22 clutch device for 1st speed 23 clutch device for 2nd speed 25 end plate for 1st speed 27 outer disk for 1st speed 28 inner for 1st speed Disk 32 End plate for 2nd speed 34 Outer disk for 2nd speed 35 Inner disk for 2nd speed 38 Switching device 39 Pressing member 41 Hydraulic circuit (fluid pressure path) 42 Spring member (elastic member) 50 Output gear 51 Open Clutch device E shaft center

 ──────────────────────────────────────────────────続 き Continuation of front page (72) Inventor Noriaki Nishimura 1-15-10, Kyomachibori, Nishi-ku, Osaka-shi, Osaka F-term in TCM Corporation (reference) FC64 GA15 HA13 HA32

Claims (2)

[Claims] 1. A transmission device for an industrial vehicle capable of shifting between one speed having a specific speed ratio and another speed having a different speed ratio from the one speed, wherein the transmission device includes a driving device in a transmission case. An input shaft that is driven to rotate, an output shaft that outputs rotation to the wheel side, and a clutch shaft that transmits the rotation of the input shaft to the output shaft are provided, and the input shaft has an input gear for one speed and the other speed. An input gear is provided, and the one-speed clutch gear meshing with the one-speed input gear and the other-speed clutch gear meshing with the other-speed input gear are individually rotated. A one-speed clutch device that is fitted around the clutch shaft in a possible state and connects and disconnects the one-speed clutch gear and clutch shaft, and connects and disconnects the other-speed clutch gear and clutch shaft. A clutch device for the other speed to be disengaged and a switching device for switching the clutch device for the one speed and the other speed to the connection and disconnection are provided, and the clutch device for the one speed is integrated with the clutch shaft. A plurality of one-speed inner disks and one-speed end plates, and a plurality of one-wheels which rotate integrally with the one-speed clutch gear and are alternately arranged with the one-speed inner disk. The clutch device for the other speed includes a plurality of inner disks for the other speed and an end plate for the other speed that rotate integrally with the clutch shaft, and the clutch for the other speed. A plurality of outer disks for the other speed, which rotate integrally with the gears and are alternately arranged with the inner disks for the other speed, the switching device includes: A pressing member capable of reciprocating in the axial direction of the clutch shaft, a fluid pressure path for moving the pressing member in the direction of the one-speed end plate by supplying fluid pressure to the pressing member, and the pressing member. An elastic member that moves in the direction of the other end plate for speed, the inner disk and outer disk for one speed are located between the pressing member and the end plate for one speed, and the pressing member and The inner disk and the outer disk for the other speed are located between the other end plate for the other speed, and the fluid pressure path is formed on the clutch shaft,
A transmission device for an industrial vehicle, wherein a transmission gear provided on the clutch shaft and an output gear provided on the output shaft mesh with each other. 2. The transmission device for an industrial vehicle according to claim 1, further comprising a release clutch device for connecting and disconnecting the output shaft and the output gear.