KR20020025968A - Industrial power transmission - Google Patents

Abstract

PURPOSE: An industrial power transmission is provided to perform the transmission and conversion of the power effectively and simplify the construction while reducing the size thereof, thereby decreasing the manufacturing cost while increasing the durability. CONSTITUTION: An industrial power transmission includes first and second rotational shafts(31,51) rotated by a power source in directions opposite to each other, a driving shaft(38R) connected to an object to be driven, first and second clutches(31R,51R) for connecting the driving shaft with the rotational shafts respectively, and a lever for controlling the clutches so that the driving shaft is selectively connected with the rotational shafts. The rotation of the driving shaft is braked by a brake(35R). The brake is operated by the lever cooperatively with the clutches so that the driving shaft is braked only when all of the clutches are released. The transmission and the conversion of power is performed effectively by the operation of the lever.

Description

Industrial power transmission {Industrial power transmission}

Industrial machines such as skid steer loaders and tractors frequently perform the operation of interrupting the power transmitted from the power source and switching the power transmission direction. Therefore, the power transmission device used in such an industrial machine not only functions to transmit the power of the engine to the driving object, but also functions as a power switching device to change the rotational direction of the engine and transmit the power to the driving object as necessary.

For example, a machine such as a skid steer loader performs work while repeatedly performing forward, backward, and rotational movements in a narrow place, and thus has a power transmission device that independently transmits engine rotational force to left and right wheels. At this time, the wheels on both sides are rotated in the forward direction when moving forward, the wheels on both sides are rotated in the reverse direction when reversing, and the left and right wheels are rotated in opposite directions when rotating.

As such, the conventional power transmission device capable of controlling and switching power is classified into a belt drive type power transmission device and a hydraulic pump type power transmission device according to the driving method.

However, the belt drive type power transmission device has a disadvantage in that a lot of loss of driving force is not strong. In addition, the belt drive type power transmission device can not perform the power transmission quickly, and the slip occurs frequently between the belt and the pulley and requires frequent maintenance.

The hydraulic pump type power transmission device generates a large force by appropriately decelerating the rotational force of the engine, and generates a high pressure hydraulic pressure by driving the hydraulic pump using this force. This hydraulic force is connected to the hydraulic motor to rotate the hydraulic motor. At this time, by controlling the flow direction of the hydraulic pressure flowing into the hydraulic motor by using a hydraulic valve of a simple structure it is possible to easily switch the rotation direction.

However, the hydraulic pump-type power transmission device as described above requires a high level of airtightness compared to other power transmission devices, and thus has a disadvantage in that a lot of manufacturing and maintenance costs are required. In addition, since the driving force generated in the hydraulic motor is relatively small compared to the high pressure generated by the hydraulic pump, the efficiency of power transmission is low, and additionally, a large number of auxiliary devices are required, so that the volume and weight are heavy. have.

The present invention relates to an industrial power transmission device, and more particularly, to a power transmission device that can be effectively switched in the rotation direction.

1 is a side view of a skid loader to which a power transmission device according to the present invention is applied;

2 is a plan view of FIG.

3 is a perspective view of a power transmission device according to the present invention shown in FIG.

4 is an exploded view of FIG. 3,

5 is a plan sectional view of FIG. 4;

6 is an enlarged cross-sectional view of the clutch shown in FIG. 2;

7 to 9 are enlarged perspective views of the adjusting device shown in FIG. 2;

10 is a schematic side view of FIG. 3;

11 illustrates another embodiment of the present invention. *

Explanation of symbols on the main parts of the drawings

1: power transmission device 2: rotation shaft

10: Bevel gear part 20: Transmission part

30: first driving unit 31: first rotating shaft

31L, 31R: First clutch 32L, 32R: First reduction gear

33L, 33R: Universal joint 37L, 38L: Reduction gear

34L, 34R, 54L, 54R: Drive belt 35L, 35R: Braking device

38L, 38R: drive shaft 40: connection part

50: 2nd drive part 51L, 51R: 2nd clutch

52L, 52R: Second reduction gear 71L, 71R: Shift lever

80L, 80R: Adjustment lever 81L, 81R: Brake rod

82L, 82R: Clutch rod 100: Skid steer loader

102L, 102R, 103L, 103R: wheels 104: engine

The present invention has been made to solve the above problems, and therefore, the object of the present invention, the structure is simple, the production cost is low, and the industrial power transmission that can perform the power interruption and switching operation quickly. To provide a device.

Industrial power transmission device according to the present invention for achieving the above object, the first and second rotary shaft to rotate in opposite directions by a power source; A drive shaft connected to the drive object; First and second clutches for intermittently connecting the first rotary shaft and the drive shaft and the second rotary shaft and the drive shaft; And adjusting means for driving the first and second clutches to control the drive shaft to be selectively connected to the first rotational shaft and the second rotational shaft.

Here, the second rotation shaft is connected to the first rotation shaft by an even number of gears sequentially engaged, and is rotated by the first rotation shaft. In addition, the power source and the first rotary shaft are interconnected by a plurality of gears that are engaged in sequence. Therefore, the rotation speed of the first rotation shaft is reduced compared to the rotation speed of the power source. The ratio between the rotational speed of the power source and the rotational speed of the first rotary shaft is controlled by the transmission means.

Preferably, the drive shaft is connected to the first and second clutches by first and second reduction gears, respectively. In addition, the drive shaft and the drive object are interconnected by a universal joint. Therefore, the rotation of the drive shaft is stably transmitted to the drive object even if the direction of the drive shaft changes.

According to a preferred embodiment of the present invention, the rotation of the drive shaft is braked by a braking device. Here, the braking device is operated in conjunction with the operation of the clutch by the adjusting means to fix the rotation of the drive shaft only when both the first and second clutch is released.

According to another preferred embodiment of the present invention, the first and second clutches and the braking device are surrounded by an oil tank filled with oil. This prevents the inflow of foreign matter into the first and second clutches and the braking device.

According to the present invention, there is provided a power transmission device in which interruption and switching of power are effectively performed. In addition, the structure of the power transmission device is simple and its size is small. Therefore, manufacturing cost of the power transmission device is reduced, and durability is increased.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings. In the description of this embodiment, an example in which the power transmission device according to the present invention is applied to a skid loader is described. First, the structure of the skid steer loader will be described.

1 is a side view of a skid loader to which a power transmission device according to the present invention is applied. The skid steer loader 100 includes a base frame 101, a power generating engine 104, a pair of front wheels 103 driven by the engine 104, a pair of rear wheels 102, and an engine 104. It has a power transmission device 1 for transmitting the rotational force to the front wheel 103 and the rear wheel 102, and a bucket 105 for performing the necessary work.

2 is a view showing the skid steer loader 100 shown in FIG. 1 together with the power transmission device 1 according to the present invention. First, the configuration and operation of the power train 1 according to the present invention will be described with reference to FIG. 2.

The skid steer loader 100 has two left wheels 103L and 102L provided respectively at the front and rear sides of the left side, and two right wheels 103R and 102R respectively installed at the front and rear sides of the right side. These four wheels 102L, 102R, 103L, and 103R become driving objects driven by the power transmission device 1 according to the present invention. When the left wheels 103L and 102L and the right wheels 103R and 102R both drive in the forward direction, the skid steer loader 100 moves forward. When both the left wheels 103L and 102L and the right wheels 103R and 102R drive in the reverse direction, The skid loader 100 is reversed. In addition, when the left wheels 103L and 102L are driven in the forward direction and the right wheels 103R and 102R are driven in the reverse direction, the skid loader 100 rotates in the right direction, that is, the clockwise direction, and the left wheels 103L and 102L are rotated. When the reverse direction and the right wheels 103R and 102R are driven in the forward direction, the skid loader 100 rotates in the left direction, that is, counterclockwise.

The power transmission device 1 advances the bevel gear portion 10 connected to the rotation shaft 2 of the engine 104, the transmission portion 20 for shifting the rotation speed of the engine 104, and the skid loader 100. The first driving unit 30 for driving in the direction, the second driving unit 50 for driving the skid steer loader 100 in the reverse direction, and the first driving unit 30 and the second driving unit 50 in opposite directions to each other. It has a connecting portion 40 for connecting between the first driving portion 30 and the second driving portion 50 to drive the driving object.

On the right side of the skid steer loader 100, a right drive shaft 38R for driving the right wheels 102R, 103R, a first right clutch 31R for intermittently connecting the first drive unit 30 and the right drive shaft 38R, The second right clutch 51R for intermittently connecting the second driving unit 50 and the right driving shaft 38R, the right deceleration unit 37R for decelerating the rotational speed of the right driving shaft 38R, the right driving shaft 38R and the right deceleration For braking the universal joint 33R connecting the sections 37R, the pair of drive belts 34R and 54R connecting the right deceleration section 37R and the right wheels 102R, 103R, and the right driving shaft 38R. The first and second right clutches 31R, 51R and the right brake unit 35R for adjusting the right brake unit 35R, the first and second right clutches 35R, The right clutch rod 82R for controlling the operation of the second right clutch 31R, 51R, the right brake rod 81R for controlling the right brake device 35R in accordance with the operation of the right adjusting lever 80R, and the transmission portion. Right shift lever for controlling shifting operation of 20 71R is provided.

The first and second right clutches 31R and 51R operate according to the operating state of the right adjusting lever 80R, so that the first driving part 30 and the second driving part 50 are selectively connected to the right driving shaft 38R. Thus, the right driving shaft 38R is rotated. The rotational force of the right drive shaft 38R is transmitted to the right wheels 102R and 103R via the universal joint 33R, the right deceleration part 37R, and the drive belts 34R and 54R, whereby the right wheels 102R and 103R are transmitted. Will rotate. At this time, when the right driving shaft 38R is connected to the first driving unit 30, the right wheels 102R and 103R rotate in the forward direction, and when the right driving shaft 38R is connected to the second driving unit 50, the right wheel 102R, 103R) rotates in the reverse direction. The right braking device 35R operates only when both the first and second right clutches 31R and 51R are in a released state. Accordingly, when the right driving shaft 38R is connected to the first driving unit 30 or the second driving unit 50 by the first or second right clutch 31R, 51R, the right driving shaft 38R is rotatable. Braking is released.

On the left side of the skid steer loader 100, the left drive shaft 38L, the first left clutch 31L, the second left clutch 51L, the left reduction gear 37L, the universal joint 33L, The drive belts 34L and 54L, the left braking device 35L, the left adjustment lever 80L, the left clutch rod 82L, the left brake rod 81L, and the left shift lever 71L are provided. Their operation is the same as described above.

Hereinafter, the structure and operation of the power transmission device 1 according to the present invention will be described in more detail with reference to FIGS. 3 to 10. In the following description, the structure of the right part of the power transmission device 1 will mainly be described, and the detailed description of the structure of the left part is omitted. The structure and operation of the left part are the same as the right part.

FIG. 3 is a perspective view illustrating the power transmission device 1 shown in FIG. 2, and FIGS. 4 and 5 are views in which the FIG. 3 is developed in a plan view for convenience of description. FIG. 10 is a schematic side view of FIG. 3 schematically showing a connection state of each component of the power train 1.

The bevel gear portion 10 is composed of bevel gears 3 connected to the rotation shaft 2 of the engine 104. The bevel gear portion 10 functions to switch the rotation axis of the rotation shaft 2 of the engine 104.

The transmission portion 20 includes a pair of transmissions 21 and 22 connecting the first rotation shaft 31 and the bevel gear portion 10. The peripheral gear 21 has a peripheral gear shaft 7 arranged in parallel with the bevel gear shaft 4, and a peripheral gear gear 8 provided in the peripheral gear shaft 7. The sub transmission 22 has a sub transmission shaft 12 arranged in parallel with the peripheral transmission shaft 7 and a sub transmission gear 11 provided on the sub transmission shaft 12. The connecting gear 5 formed on the bevel gear shaft 4 meshes with the peripheral gear 21, and the peripheral gear gear 8 of the peripheral gear 21 meshes with the shift neutral gear 6 of the shift neutral shaft 9. The shift neutral gear 6 is meshed with the sub transmission gear 11 of the sub transmission shaft 12.

The first drive unit 30 is composed of a first rotation shaft 31. The sub transmission 22 is meshed with the first rotation shaft 31. Accordingly, the rotational force of the rotary shaft 2 of the engine 104 is transmitted to the first rotary shaft 31. At this time, the peripheral transmission 21 and the sub-transmission 22 is movable in the axial direction by a shift fork (not shown), the rotational speed ratio by the engagement of the gears varying the number ratio according to the moving position To convert Accordingly, the rotation speed of the rotation shaft 2 is converted and transmitted to the first rotation shaft 31.

The second driving unit 50 is composed of a second rotating shaft 51 disposed in parallel with the first rotating shaft 31.

The connection part 40 is comprised by the two gears 41 and 42 which mutually connect the 1st rotating shaft 31 and the 2nd rotating shaft 51. FIG. Since the connection part 40 is made up of an even number of gears 41 and 42, the first rotation shaft 31 and the second rotation shaft 51 are always rotated in opposite directions. In addition, the number of teeth of the 1st rotation shaft 31 and the 2nd rotation shaft 51 is the same, and therefore the rotation speed is the same.

The first clutch 31R is provided on the first rotary shaft 31, and the second clutch 51R is provided on the second rotary shaft 51. 6 shows the structure of these clutches 31R and 51R. 6, only the structure of the clutch 31R provided on the right side of the first rotary shaft 31 is shown, but all other clutches have the same structure.

The first clutch 31R has a clutch disk 65 fixed to the first rotation shaft 31, a clutch plate 62 rotatably provided on the first rotation shaft 31, and a clutch hub 66. The clutch disc 65 is disposed between the clutch plate 62 and the clutch hub 66. The clutch cam 67 and the clutch cam base 68 are provided outside the clutch hub 66. The clutch cam 67 is operated by the clutch rod 82R.

In a state where the clutch rod 82R is not pulled, the clutch cam 67 is placed at the bottom dead center so that the clutch disc 65 is spaced apart from the clutch plate 62 and the clutch hub 66. Accordingly, only the clutch disc 65 rotates when the first rotation shaft 31 rotates. When the clutch rod 82R is pulled, the clutch cam 67 is placed at the top dead center, and the clutch hub 66 is pressed to the left by the clutch cam 67. Accordingly, the clutch plate 62 and the clutch hub 66 come into contact with the clutch disc 65, and the clutch plate 62, the clutch disc 65, and the clutch hub 66 when the first rotation shaft 31 rotates. ) Will rotate together.

The first reduction gear 32R is connected to the first rotation shaft 31, and the second reduction gear 52R is connected to the second rotation shaft 51. The first and second reduction gears 32R and 52R are connected to the drive shaft 38R. The first reduction gear 32R is not directly connected to the first rotation shaft 31, but is engaged with the clutch plate 62 provided on the first rotation shaft 31 as shown in FIG. 6. Therefore, when the first clutch 31R is operated, the rotation of the first rotation shaft 31 is transmitted to the drive shaft 38R through the first reduction gear 32R. In addition, the second reduction gear 52R is also engaged with the clutch plate 62 provided on the second rotation shaft 51 without being directly connected to the second rotation shaft 51. Therefore, when the second clutch 51R is operated, the rotation of the second rotation shaft 51 is transmitted to the drive shaft 38R through the second reduction gear 52R. When neither of the first and second clutches 31R and 51R operate, the rotation of the first and second rotary shafts 31 and 51 is not transmitted to the drive shaft 38R.

The braking device 35R includes a brake wheel 35R-2, a connecting gear 35R-1 rotating together with the brake wheel 35R-2, and a connecting gear 35R-1 and the first reduction gear 32R. It consists of a brake belt (35R-3) for connecting. The brake wheel 35R-2 is in constant contact with a brake block (not shown). Accordingly, the rotation of the brake wheel 35R-2 is braked by the brake block, and thus the rotation of the first reduction gear 32R is braked. When the brake rod 81R is pulled, the brake block is spaced apart from the brake wheel 35R-2, and thus the first reduction gear 32R is rotatable.

7 to 9 show the adjusting portion of the power train 1. The adjusting part is provided at both ends of the hinge lever 91 and the hinge pin 91 provided at the lower end of the adjustment lever 80R and the adjustment lever 80R, which are rotatably installed on the base frame 101 of the skid steer loader 100. To release the brake release plate 95 and the brake release plate 95 driven by the clutch rod arm 92, the brake operation piece 93, and the brake operation piece 93 respectively installed in the rotational direction. And a brake rod arm 96 connected to the boss 94 and the brake release plate 95. The clutch rod arm 92 is connected to the clutch rod 82R, and the brake rod arm 96 is connected to the brake rod 81R.

As shown in FIG. 8, when the operator rotates the adjustment lever 80R forward, the brake operating piece 93 presses the lower portion of the brake release plate 95, and the brake release plate 95 is formed of the brake rod arm ( 96). As a result, the brake rod 81R is pulled to release the braking of the drive shaft 38R by the braking device 35R. On the other hand, as the adjustment lever 80R is rotated forward, the clutch rod arm 92 drives the first clutch 31R to connect the first rotation shaft 31 with the first reduction gear 32R. Accordingly, the rotational force of the first rotation shaft 31 is transmitted to the drive shaft 38R through the first reduction gear 32R, and the rotational force of the drive shaft 38R is the universal joint 33R, the reduction unit 37R, and the drive belt. It is transmitted to the right wheels 102R and 103R via 34R and 54R. As a result, the right wheels 102R and 103R rotate in the forward direction.

As shown in FIG. 9, when the operator rotates the adjustment lever 80R backward, the brake operating piece 93 presses the upper portion of the brake release plate 95, and the brake release plate 95 is a brake rod arm ( 96). As a result, the brake rod 81R is pulled to release the braking of the drive shaft 38R by the braking device 35R. On the other hand, as the adjustment lever 80R is rotated backward, the clutch rod arm 92 drives the second clutch 51R to connect the second rotation shaft 51 with the second reduction gear 52R. Accordingly, the rotational force of the second rotary shaft 51 is transmitted to the drive shaft 38R through the second reduction gear 52R, and the rotational force of the drive shaft 38R is the universal joint 33R, the reduction unit 37R, and the drive belt. It is transmitted to the right wheels 102R and 103R via 34R and 54R. As a result, the right wheels 102R and 103R rotate in the reverse direction.

As shown in FIG. 7, when the adjustment lever 80R is positioned in the middle, both the first and second clutches 31R and 51R are not driven, and thus, the first rotation shaft 31 and the first deceleration. The connection between the gears 32R and the second rotational shaft 51 and the second reduction gear 52R is broken. In addition, since the brake rod 81R is not pulled, the first reduction gear 32R is fixed by the braking device 35R, thereby driving the drive shaft 38R and the right wheels 102R and 103R.

In this way, the braking device 35R operates in conjunction with the operation of the first and second clutches 31R, 51R in accordance with the operation of the adjustment lever 80R. In addition, the braking device 35R brakes the rotation of the drive shaft 38R only when both the first and second clutches 31R and 51R are released.

On the left side of the power transmission device 1, the first and second clutches 31L and 51L, the first and second reduction gears 32L and 52L, the braking device 35L, and the brake wheel having the above-described structure 35L-2), coupling gear 35L-1, brake belt 35L-3, brake rod 81L, clutch rod 82L, adjustment lever 80L, drive shaft 38L, reduction gear 37L, The universal joint 33L, the drive belts 34L and 54L, and the shift lever 71L are provided. Their configuration and operation are the same as described above.

Hereinafter, the operation of the skid steer loader having a power transmission device 1 according to the present invention as described above.

When the engine 104 operates, the rotational speed of the engine 104 is decelerated by the transmission unit 20, and the first and second rotational shafts 31 and 51 rotate in opposite directions at a reduced speed. . At this time, the rotation direction of the first rotary shaft 31 is a direction for advancing the advance of the skid loader 100, the rotation direction of the second rotary shaft 51 is a direction for moving the skid loader 100 backward. The operator can adjust the shift ratio of the speed change section 20 by adjusting the shift levers 71R and 71L.

When the operator rotates the adjustment lever 80R forward, braking of the first reduction gear 32R by the braking device 35R is released and at the same time, the first rotation shaft 31 and the first rotation shaft are driven by the first clutch 31R. The reduction gear 32R is connected. As a result, the drive shaft 38R rotates in the forward direction, and the right wheels 102R and 103R rotate in the forward direction.

When the operator rotates the adjusting lever 80R backward, the braking of the first reduction gear 32R by the braking device 35R is released and at the same time, the second rotation shaft 51 and the second are rotated by the second clutch 51R. The reduction gear 52R is connected. As a result, the drive shaft 38R rotates in the reverse direction, and the right wheels 102R and 103R rotate in the reverse direction.

As the adjustment lever 80L is operated in the same manner as described above, the left wheels 102L and 103L rotate in the forward direction or the reverse direction. In order to move the skid steer loader 100 forward, the operator rotates both adjusting levers 80R and 80L forward, and in order to reverse, the operator rotates both adjusting levers 80R and 80L backward. . In addition, in order to rotate the skid steer loader 100 to the left, the operator rotates the left adjusting lever 80L to the rear, rotates the right adjusting lever 80R forward, and rotates the skid steer loader 100 to the right. In order to do this, the operator rotates the left adjustment lever 80L forward and rotates the right adjustment lever 80R backward. Accordingly, the skid loader 100 is rotated counterclockwise or clockwise. Therefore, the direction change of the skid steer loader 100 can be easily performed even in a narrow space.

According to the present invention as described above, since the rotational force of the first and second rotary shafts 31 and 51 which are constantly rotating are selectively transmitted to the drive shafts 38R and 38L, the interruption and switching of the power are effectively performed.

In addition, since the power transmission device 1 is composed of an assembly of gears and clutches 31R, 31L, 51R, and 1L, its structure is simple and small in size. Therefore, manufacturing cost is reduced, and durability is increased. In addition, since the driving shafts 38R and 38L are braked by the braking devices 35R and 35L while the rotational force of the first and second rotary shafts 31 and 51 is not transmitted to the driving shafts 38R and 38L, the skid The position of the loader 100 is firmly fixed. Therefore, since the skid loader 100 can perform the work in a fixed state, it is easy to perform the work. In particular, since the drive shafts 38R, 38L and the wheels 102R, 102L, 103R, 103L are connected by the universal joints 33R, 33L, the direction of the drive shafts 38R, 38L is controlled by the load of the skid steer loader 100. Even if this changes, the power of the drive shafts 38R, 38L is stably transmitted to the wheels 102R, 102L, 103R, 103L.

11 illustrates another embodiment of the present invention. In this embodiment, the skid loader 100 and the power transmission device 1 have the same configuration as the above-described embodiment. In this embodiment, the power transmission device 1 is surrounded by the oil tank 1-1. The oil tank 1-1 hermetically surrounds the clutches 31R, 31L, 51R, 51L and the braking devices 35R, 35L in the power train 1, and has frictional force in the oil tank 1-1. This excellent oil is filled. Where the skid steer loader 100 is used has a lot of dust, the wear of the clutch (31R, 31L, 51R, 51L) and the braking device (35R, 35L) can be severe. However, according to the present embodiment, foreign matters are prevented from entering the clutches 31R, 31L, 51R, and 51L and the braking devices 35R and 35L, thereby preventing wear.

According to the present invention, there is provided a power transmission device 1 in which interruption and switching of power are effectively performed. In addition, the structure of the power train 1 is simple and its size is small. Therefore, manufacturing cost of the power transmission device is reduced, and durability is increased.

Therefore, the loss of the driving force is low and robust as compared with the conventional belt drive type power transmission device, the power is transmitted quickly, and there is no need for frequent maintenance. In addition, the manufacturing cost and maintenance cost is lower than the conventional hydraulic pump type power transmission device, the power transmission efficiency is high, and also because it does not require a lot of ancillary auxiliary device is small in volume and light weight.

Although the preferred embodiments of the present invention have been illustrated and described above, the present invention is not limited to the specific preferred embodiments described above, and the present invention is not limited to the specific scope of the present invention as claimed in the claims. Anyone of ordinary skill in the art can make various modifications, as well as such modifications are within the scope of the claims.

Claims (13)

In the industrial power train, First and second rotational shafts which rotate in opposite directions by a power source; A drive shaft connected to the drive object; First and second clutches for intermittently connecting a connection between the first rotary shaft and the drive shaft and a connection between the second rotary shaft and the drive shaft; And And adjusting means for driving the first and second clutches to control the drive shaft to be selectively connected to the first rotational shaft and the second rotational shaft. The method of claim 1, And the second rotation shaft is connected to the first rotation shaft by an even number of gears sequentially engaged and rotated by the first rotation shaft. The method of claim 2, And the first rotational shaft and the second rotational shaft have the same rotational speed. The method of claim 1, And the power source and the first rotation shaft are interconnected by a plurality of gears sequentially engaged, thereby reducing the rotation speed of the first rotation shaft relative to the rotation speed of the power source. The method of claim 1, And a transmission means for adjusting a ratio between the rotational speed of the power source and the rotational speed of the first rotational shaft. The method of claim 1, And a bevel gear that interconnects the power source and the first rotational axis such that the rotational axis is switched. The method of claim 1, And the drive shaft is connected to the first and second clutches respectively by first and second reduction gears. The method of claim 1, The drive shaft and the drive object is an industrial power transmission device, characterized in that interconnected by a universal joint. The method of claim 1, And a braking device for braking the rotation of the drive shaft. The method of claim 9, The braking device is an industrial power transmission device, characterized in that to operate in conjunction with the operation of the first and second clutch by the adjusting means. The method of claim 10, The braking device is an industrial power transmission device characterized in that for fixing the rotation of the drive shaft only when both the first and second clutch is released. The method of claim 11, The adjusting means, An adjustment lever operated by an operator; A brake rod driven by the adjustment lever to drive the braking device; And And a clutch rod driven by the adjustment lever to drive the first and second clutches. The method of claim 9, An oil tank surrounding the first and second clutches and the braking device; And Industrial power transmission device further comprises an oil filled in the oil tank.