KR940009858B1 - Transmission structure for running of working vehicle - Google Patents

Abstract

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Description

Driving motor structure of work vehicle

The figure shows an embodiment of the drive train structure of the work vehicle according to the present invention,

1 is a hydraulic circuit diagram for slide operation of the side gear.

2 is a longitudinal sectional front view of the transmission case.

3 is a longitudinal sectional front view near the third and fourth transmission shafts.

4 is a partial cutaway rear view of the steering lever arrangement mounting portion.

* Explanation of symbols for main parts of the drawings

1: output shaft 2: transmission case

3: shift gear 4: driving device

5 axle 6 support shaft

7: first output gear 8: medium speed gear

9: 2nd output gear 11: 2nd gear

12: side gear FC: first clutch

RC: Second Clutch

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a traveling transmission structure in a work vehicle provided with a right and left pair of crawler type traveling devices or a multi-wheeled work vehicle such as one four wheel.

In the combine which is an example of the work vehicle provided with a right-and-left pair of crawler-type traveling apparatuses, there exists a thing similar to what is disclosed by Unexamined-Japanese-Patent No. 57-60988, for example. That is, by rotating the side gears (19a, 19b of the publication) to the first output gear (17 of the publication), the forward rotational power can be transmitted and go straight.

Then, reverse rotational power is transmitted to the side gear by switching the switching gear (the publication 11) while the side gear is engaged with the second output gear (18a and 18b of the publication). The side gear can be stopped.

Thereby, three states of a straight state, a mid radius turning when stopping one traveling device, and a small radius turning when one traveling device is driven in reverse rotation are obtained.

In addition, in the above structure, when the side gear is operated in a neutral position which is not engaged with the first output gear or the second output gear, the turning in a state in which power to one traveling device can be stopped and freely rotated, that is, a large radius turning It is also possible to carry out (iii).

However, in order to brake the axle, a locking mechanism for fixing the shift gear to the transmission case, an engagement mechanism for fixing the shift gear to the transmission shaft, etc. is required. It wasn't.

SUMMARY OF THE INVENTION An object of the present invention is to provide an electric mechanism that improves the operability of the above-described various swings and also has a simplified structure.

According to the present invention, the above problems are solved by a traveling electric motor having the following configuration; That is, from the first transmission device receives power from the engine, the second transmission device receives power from the engine, the first output gear (7), the forward power is transmitted from the first transmission device, from the second transmission device A pair of second output gears 9 and 9 to which forward and backward power is transmitted, a pair of side gears 12 and 12 to transfer power to the left and right traveling devices, and the side gears 12 and A first clutch FC installed between the first output gear 7, a multi-plate friction type second clutch RC provided between the side gear 12 and the second output gear 9, and Pressure adjusting means for adjusting the connection operating pressure of the second clutch (RC).

In the traveling electric motor structure configured as described above, the mid-radius line which is realized by rotating the traveling device of the other family forward while rotating one traveling device reversely and the mid-radius line which is realized by rotating the other traveling device forward while stopping one traveling device The structure for sashimi is simplified and its operability is improved.

Small radius turning for left turning according to the present invention is realized by the transmission of power from the engine to the traveling device as follows.

First, the power transmission to the right traveling device will be described. The engine power is transmitted to the first output gear as the forward power through the first transmission device. This power transmitted to the first output gear is transmitted to the right side gear by the operation of the first clutch connecting the first output gear and the right side gear. Power transmitted to the right side gear is transmitted to the right driving unit. Thereby, the right traveling device is operated to advance the vehicle.

Next, the power transmission to the left traveling device will be described. The engine power is transmitted to the second output gear as the reverse power through the second transmission device. This power transmitted to the second output gear is transmitted to the left side gear by the operation of the left second clutch connecting the second output gear to the left side gear. At this time, the pressure adjusting means adjusts the operating pressure to the left second clutch so that no slip occurs with the left second clutch. Power transmitted to the left side gear is transmitted to the left drive. Thereby, the left traveling device acts to reverse the vehicle.

As a result, the small radius turning of the left turning is realized by rotating the traveling device on the right forward while rotating the driving device on the left side in reverse. It is obvious that the small radius turning of the preferred embodiment is realized in the same manner by rotating the traveling device on the left forward while rotating the driving device on the right.

The mid-round turn for the left turn according to the present invention is realized by transmitting power from the engine to the traveling device as follows.

First, the power transmission to the right traveling device will be described. The engine power is transmitted to the first output gear as the forward power through the first transmission device. This power transmitted to the first output gear is transmitted to the right side gear by the operation of the first clutch connecting the first output gear and the right side gear. Power transmitted to the right side gear is transmitted to the right driving unit. In so doing, the right traveling device acts to advance the vehicle.

Next, the power transmission to the left traveling device will be described. The engine power is transmitted to the second output gear as the reverse power through the second transmission device. This power transmitted to the second output gear is transmitted to the left side gear by the operation of the left clutch which connects the second output gear to the left side gear. At this time, if the pressure adjusting means adjusts the operating pressure to the left second clutch so that the left second clutch is slipped, the driving force of the battery action by the right traveling device and the reversal of the left traveling device is balanced and the left traveling device is stopped. Condition occurs.

As a result, by turning the traveling device on the right side forward while stopping the traveling device on the left side, the mid-round turn of the left turn is realized. It is apparent that the mid-round turn of the priority is realized in the same manner by turning the traveling device on the left forward while stopping the traveling device on the right.

In order to realize a normal state of advance, forward rotational power may be transmitted to the traveling devices on both sides by a method apparent from the above description.

As can be understood from the above description, the present invention does not require a complicated structure such as stopping or reversing the side gear when performing a small radius turning or a middle radius turning, as in the prior art. It is only necessary to adjust the operating pressure to the second clutch, and the simplification of the structure and the improvement of the operability can be obtained.

In a preferred embodiment of the present invention, the second electric gear of the second output gear to which the forward power and the reverse power are selectively transmitted to the second output gear and the forward power is transmitted at that time. When the speed is configured to be slower than the speed of the first output gear, in addition to the turning state of stopping or reversing one driving device, one of the driving devices is driven at a low speed to ensure a large anti-rotation. The turning performance of the car can be improved.

That is, the low speed forward rotational power is transferred to the second clutch RC by the electric switching mechanism while the second clutch RC on the left side is connected to the second clutch RC.

As a result, the traveling device on the left side is driven forward at a lower speed than the traveling device on the right side, and the body is reliably turned to the left side by the speed difference between the right and left traveling devices.

Further features according to the present invention will become apparent with the description of the embodiments described below.

EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described based on drawing.

2 shows the structure of the transmission case 2 in the traveling system of the combine, which is one of the working vehicles, and the power from the engine (not shown) is applied to a belt transmission mechanism (not shown) provided with a tension clutch. It is transmitted to the input pulley 16 of the hydrostatic CVT.

The power is transmitted from the first transmission shaft 14 of the power from the output shaft 1 of the hydrostatic stepless speed changer M through the output pulley 15 to a cutting device (not shown).

Power from the output shaft 1 is transmitted to the second transmission shaft 21 via the first gear 10. The first high speed gear 22 is freely interleaved with respect to the second transmission shaft 21, and the shift gear 3 has a spline structure to which the slide operation is freely attached.

The low speed gear 25, the middle speed gear 8, and the second high speed gear 23 are attached to the third transmission shaft 24 in a splined structure, and the first and second high speed gears 22 and 23 are engaged with each other.

Therefore, by shifting the shift gear 3 to the first high speed gear 22, the middle speed gear 8, and the low speed gear 25, the power can be shifted into three stages of high, middle and low speeds. Is transmitted to the first output gear 7 which meshes with the medium speed gear 8.

In the support shaft 6 supporting the first output gear 7, the right and left side gears 12 are freely interleaved, and the input gears 18 of the left and right axles 5 are left and right sides. It is always in mesh with the gear 12.

As a result, an engagement first clutch FC is formed between the right or left side gear 12 and the first output gear 7, and the convex engaging portion 13 of the side gear 12 is formed. By engaging the first output gear 7, the forward rotational power is transmitted to the crawler-type traveling device 4 on the left and right. The spring 19 presses the side gear 12 toward the first output gear 7 side.

A pair of second output gears 9 are fitted to the left and right of the support shaft 6, and a second clutch RC of multi-plate friction type is installed between the second output gear 9 and the support shaft 6. It is. On the other hand, as shown in FIGS. 2 and 3, the second gear 11 is fixed to both ends of the third transmission shaft 24, and the sleeve 38 is fitted to the bearing portion so that the third transmission shaft ( 24) slides left and right.

In this case, since the low speed gear 25 or the middle speed gear 8 is positioned by the sleeve 26, the low speed gear 25 or the medium speed gear 8 may be operated even when the third drive shaft 24 is slid. The position of does not change.

The state shown in FIG. 2 and FIG. 3 is a state which slides the 3rd electric shaft 24 to the left side in drawing, and the 2nd gear 11 of right and left is engaged with the 3rd gear 27 of right and left. It is a state.

In this state, the power of the third transmission shaft 24 is transmitted to the left and right second output gears 9 in the reverse rotation state through the third gear 27, the fourth transmission shaft 39, and the fourth gear 28. Delivered.

Accordingly, as shown in FIG. 2, the left side gear 12 is separated from the first output gear 7, and the second clutch RC is pressed by the pressing portion 17 of the side gear 12. In this case, the reverse rotational power of the second output gear 9 on the left side is transmitted to the traveling device 4 on the left side, and the small radius line change is performed on the left side.

Then, by lowering the pressing force of the left side gear 12 and sliding the second clutch RC, the forward action by the right traveling device (not shown) and the reverse rotation driving force of the left traveling device 4 are reduced. In parallel, the traveling device 4 on the left is apparently stopped. Thereby, a mid-round turn is performed to the left.

Next, when the third transmission shaft 24 is slid to the right in the drawing in the state shown in Figs. 2 and 3, the left and right second gears 11 are directly engaged with the left and right second extraction gears 9. As a result, the forward rotational power which is lower than the forward rotational power transmitted from the third transmission shaft 24 to the first output gear 7 is transmitted from the third transmission shaft 24 to the second output gear 9.

Therefore, as shown in FIG. 2, when the second clutch RC is pressurized and connected to the left side gear 12, the traveling device 4 on the left side is lower than the traveling device (not shown) on the right side. The engine is rotated to the left by rotating forward.

Next, the slide operation structure of the side gear 12 will be described.

As shown in FIG. 1, an operation arm 20 for sliding operation of the side gear 12 and a hydraulic cylinder 29 for oscillating it are provided. In this case, the hydraulic cylinder 29 is movable to the contraction side. A spring 29a is built in. The hydraulic oil from the pump 30 is supplied to the electronically operated swing control valve 31 for the hydraulic cylinder 29.

When the hydraulic cylinder 29 is extended until the side gear 12 is disengaged from the first output gear 7 and the second clutch RC is pressed to move to a position not to be connected, the hydraulic cylinder 29 A drain flow path 32 is provided for pulling hydraulic oil from the hydraulic cylinder 29 and allowing the hydraulic cylinder 29 to remain at that position.

In addition, a variable relief valve 33 (corresponding to a changing means) is provided in the drain flow path 32.

Next, the operation of the swing control means 31 and the variable relief valve 33 will be described. The state shown in FIG. 1 is a state just before the left and right side gears 12 mesh with the first output gear 7.

In this state, for example, when the operating lever 34 is operated to the first swing position L ₁ on the left side, the swing control valve 31 is operated to be switched to supply hydraulic oil to the hydraulic cylinder 29 on the left side, and to the left side gear. (12) slides to the left on the drawing and falls from the first output gear (7). In this case, the drain flow path 32 is opened at the neutral position before the left side gear 12 presses the second clutch RC, and the hydraulic oil flows out from the variable relief valve 33, so that the left side gear 12 Stops at the neutral position. This is a state where the transmission to the driving vehicle 4 on the left side is cut off.

Then, when the operation lever 34 is operated to the second swing position L ₂ on the left side, the variable relief valve 33 is throttled so that the hydraulic cylinder 29 extends from the neutral position to the second clutch RC on the left side. ) Is fully connected.

In this case, as shown in FIG. 3, when the 3rd transmission shaft 24 slides to the left side of the paper surface, the traveling vehicle 4 of the left side will drive reverse rotation.

If the operating lever 34 is positioned between the left first and second swing positions L ₁ and L ₂ , the hydraulic oil is released from the hydraulic cylinder 29 from the above state and the pressing force to the second clutch RC is reduced. Is weakened. As a result, the second clutch RC slides, and the driving vehicle 4 on the left side comes to a stop state.

In addition, when the operation lever 34 is operated between the position (the position where the second clutch RC slides) and the second swing position L ₂ , the pressing force to the second clutch RC is changed to travel on the left side. The reverse rotation speed of the vehicle 4 can be changed.

On the contrary, the operating lever 34 is rotated to the left on the left side by sliding the third electric shaft 24 to the right side in the drawing and engaging the second gear 11 directly with the second output gear 9. By operating to the position L ₂ , the traveling device 4 on the left side is driven in the forward rotation state at a lower speed than the traveling device 4 (not shown) on the right side. In addition, when the operation lever 34 is operated between the first preferred position L ₁ and the second swing position L ₂ on the left side, the pressing force to the second clutch RC is changed, and the traveling device 4 on the left side is changed. The forward rotation speed of) can be changed. Above operation is the same also in the first pivot position of the right (R ₁₎ or the second pivot location (R _2).

Moreover, as shown in FIG. 3, the parking brake 35 is provided in one 4th electric shaft 39. As shown in FIG.

Then, when the parking brake lever 36 is operated, this is detected by the switch 37, and the engine (not shown) is automatically stopped by the automatic stop device 40 and the parking brake 35 thereafter. Is connected.

Next, the linkage mechanism between the operation lever 34 and the variable relief 33 will be described.

As shown in FIG. 4, as the operating lever 34 swings at the straight position N, the lever pivoting member 45 pivotally supports the operating lever 34 so as to be relatively swingable. The operation pin 47 attached to one of the operating levers 34 and 46b is configured to operate under pressure swing, and the outer wire and the inner wire of the operation wire 44 are connected to a pair of swing links 46a and 46b. And a pair of swing links 46a and 46b are connected by a spring 48 so that the swing link interval automatically returns to the set interval when the operation lever 34 is in the straight position N at the same time. And in spite of these connections, when one rocking link 46a or 46b is rocked by the operating lever 51, the stopper pin 49 attached to the lever pivot support member 45 swings on the other side. Supporting base to prevent swinging link 46b or 46a As a result of the locking configuration, the swinging link 46a or 46b of the swing lever 46a or 46b operates the inner wire or the outer wire due to the lever operating force to increase the relief pressure of the swing operating portion 50 of the variable relief valve 33. To the side or restoring operation of the swinging operation part 50 at the pressing force of the spring 38 to the relief pressure reducing side.

In addition, the spring 51 shown in FIG. 4 is tension-elastic deformation operation because of the pressure sliding movement of the spring operating member 52 by the operating lever 34 when the reverse clutch RC is connected. The operation resistance of the lever 34 is made larger than the operation resistance until then, so that the operator can recognize that the reverse clutch RC has been operated.

In the above embodiment, the second clutch RC is pressurized by the hydraulic cylinder 29, but the second clutch RC may be pressurized by an artificial operating force.

Here, a gear transmission mechanism is proposed as the power transmission means, but of course, a transmission structure using other power transmission means, such as a chain transmission mechanism, is also within the scope of the present invention.

The present invention can be applied not only to a crawler type traveling device but also to a multi-wheeled work vehicle such as an eight wheeler or a six wheeler. In addition, although a code | symbol is written in the term of a claim for convenience in contrast with a drawing, this invention is not limited to the structure of an accompanying drawing by this writing.

Claims (4)

In a traveling transmission structure for transmitting engine power to a pair of left and right vehicles (4, 4), the first transmission device receives power from the engine, the second transmission device receives power from the engine, and the first transmission device. Power output to the first and second output gears 9 and 9 of the first and second output gears 7 and 9, from which the forward and backward power is transmitted, from the second transmission device. A pair of side gears 12 and 12 for transmitting a first clutch FC installed between the side gears 12 and the first output gear 7, the side gears 12 and the second second gears; A traveling electric motor structure comprising a multi-plate friction type second clutch RC provided between the output gears 9 and pressure adjusting means for adjusting a connection operation pressure of the second clutch RC. . The method of claim 1, wherein the second transmission device selectively transfers forward power and backward power to the second output gear, wherein the speed of the second output gear from which the forward power is transmitted is increased. A driving motor structure characterized in that it is lower than the speed of the output gear. The drive transmission structure according to claim 1 or 2, wherein the second clutch is a hydraulic multi-plate friction clutch, and the pressure adjusting means is a valve for adjusting the pressure of oil supplied to the hydraulic multi-plate friction clutch. 4. The drive train structure according to claim 3, wherein the pressure adjusting means is a variable relief valve capable of continuously adjusting hydraulic pressure.