JP3346967B2 - Combine traveling hydraulics - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combine hydraulic cylinder provided with a hydraulic cylinder for steering and a friction type hydraulic clutch for switching between forward and backward movement, and having a structure for supplying lubricating oil to the friction type hydraulic clutch. The present invention relates to a traveling hydraulic device.

[0002]

It is conceivable to use return oil from each relief valve as lubricating oil. As one of them, it is conceivable to use return oil from a first relief valve provided in a first pressure oil supply path to a steering hydraulic cylinder. However, during traveling of the combine, the steering hydraulic cylinder is operated relatively frequently,
Where the steering needs to be performed, when the return oil from the first relief valve is used, the supply oil path for the return oil acts as a resistance, and a back pressure acts on the first pressure oil supply path, and the steering hydraulic cylinder is used. The movement of the switching spool of the first switching valve for switching the supply oil to the oil supply becomes poor, which may affect the steering operation. An object of the present invention is to provide a traveling hydraulic device for a combine which can minimize the influence of a back pressure on an operation system when using return oil from a relief valve as lubricating oil for a hydraulic clutch. .

[0003]

According to a first aspect of the present invention, there is provided a fuel cell system having a flow priority valve.
Control flow through the forward / backward switching valve and the forward hydraulic clutch.
Switching to the reverse hydraulic clutch
The excess flow branched by the priority valve is
And the flow priority
Supply the control flow from the tee valve to the forward / reverse switching valve
From the middle of the second pressure oil supply oil passage provided to
Supply lubricating oil to each of the forward and reverse hydraulic clutches
The oil passage to be branched is branched, and the branch hydraulic passage is
2nd secures the working pressure of the
The leaf valve is interposed, and the tank
The forward hydraulic clutch and the reverse hydraulic
Third relief valve to secure the lubrication pressure of each clutch
And the third relief valve in the return oil passage
The upstream side of the branch oil passage to the second
It is connected to a portion downstream of the relief valve , and its operation and effect are as follows.

[Operation] The forward / backward switching operation is performed less frequently than the steering operation. Therefore, even if an oil path is formed between the second relief valve and the hydraulic clutch, even if the movement of the spool is somewhat degraded due to the back pressure acting on the switching valve for forward / reverse switching, the operation system is not affected. The effect is small. In particular, the steering operation is frequently performed and requires a quick switching operation. However, in the forward / reverse switching operation, the demand for the quick operation is not as high as the steering operation, which is advantageous in that respect.

[Effect] Accordingly, return oil from the relief valve can be used as lubricating oil while reducing the influence on the switching operation system.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG. 1, a belt-type continuously variable transmission 1 is provided on the right side of a transmission system transmission case 8, and power transmitted to an input pulley 2 of the continuously variable transmission 1 is provided. Is transmitted from the output shaft 3 to the first transmission shaft 5, the input gear 6 of the hydraulic forward clutch FC and the input gear 9 of the hydraulic reverse clutch RC, and output gear 7 of the forward clutch FC and the reverse clutch RC. , 10 are engaged with the input gear 12 of the second transmission shaft 11.

With the above structure, when the operating oil is supplied to the forward clutch FC and the hydraulic oil is turned on, the power from the first transmission shaft 5 is transmitted through the input gear 6, the forward clutch FC and the output gear 7 to the forward state. At the second transmission shaft 11.
Conversely, when the operating oil is supplied to the reverse clutch RC and the hydraulic oil is turned on, the power from the first transmission shaft 5 is applied to the input gear 6,
9. The power is transmitted to the second transmission shaft 11 via the reverse clutch RC and the output gear 10 in a reverse and reverse traveling state.

A shift gear 13 is externally slidably fitted to the second transmission shaft 11 in a spline structure, and a high speed gear 15, a medium speed gear 16 and a low speed gear 17 are fixed to the third transmission shaft 14 for this. Have been. As a result, the shift gear 13 is slid and engaged with the high-speed gear 18, the medium-speed gear 16 or the low-speed gear 17 meshing with the high-speed gear 15 to shift the power to three stages of high, medium and low. From the transmission gear 28.

Right and left side gears 21 are rotatably fitted on a support shaft 20 supporting a transmission gear 28, and input gears 23 of left and right axles 22 are always engaged with the left and right side gears 21. . A multi-plate side brake 26 is provided between the left and right side gears 21 and the transmission case 8 at both left and right ends of the support shaft 20.
7, the side gear 21 is urged toward the occlusal side with the transmission gear 28.

When the left and right side gears 21 are engaged with the transmission gear 28 by the above structure, the power from the third transmission shaft 14 is transmitted via the transmission gear 28 and the left and right side gears 21 to the left and right crawler type traveling device. The aircraft is transmitted to the vehicle 24 and travels straight. Then, when the right or left side gear 21 is operated to move away from the transmission gear 28 and the side brake 21 is pressed and operated by the side gear 21, one of the traveling devices 24 is braked, and the aircraft body turns around. Thus, a steering device that controls the steering of the traveling device 24 is configured.

A gear pair 25 having a pair of large and small gears is externally fitted to the first transmission shaft 5 so as to be relatively rotatable, and the large gear of the gear pair 25 meshes with the output gear 7 of the forward clutch FC. are doing. A shift gear 43 is externally slidably fitted to an output shaft 42 supporting an output pulley 4 for transmitting power to a reaping section (not shown) at the front of the machine body by a spline structure. Thus, by sliding the shift gear 43 so as to mesh with the large and small gears of the gear pair 25, the power to the reaping unit can be shifted between high and low gears.

Next, a description will be given of a pair of hydraulic cylinders 31 for operating the body by sliding the left and right side gears 21 independently, and hydraulic circuits for forward and backward hydraulic clutches FC and RC. As shown in FIG.
One of the pumps 29 and 45 to be driven
Is supplied to the hydraulic cylinders 31 for the left and right side gears 21 via the flow priority valve 32 (excess flow side) and the first switching valve 30, and the flow priority valve 32, the first switching valve 30 A variable first relief valve 33 is connected between the first and second valves. Then, the flow the hydraulic fluid of the control stream side of the priority valve 32, it is supplied to the forward clutch FC and the reverse clutch RC via the second switching valve 39 as a forward-reverse switching, the second switching valve 39 Forward and reverse clutch F
A second relief valve 48 for securing pressure of C and RC is connected. The return oil from the second relief valve 48 forms a branch oil passage b to be used as lubricating oil for the friction plates of the forward and backward clutches FC and RC. The lubricating oil is applied to the friction plates to prevent the friction plates from rotating together, improve the sharpness of the clutch, and suppress the heat generated by the clutch. Since a pressure of about 0.1 to 0.3 kg / cm2 is required for use as a lubricating oil, a relief valve 54 for securing pressure is provided in the branch oil passage b. Here, only the return oil from the relief valve 48 provided in the supply oil passage to the forward and backward clutches FC and RC is supplied as lubricating oil, and the return oil from the supply oil passage to the side clutch cylinder 31 is lubricating oil. Drain without using. 55 is an accumulator, and 36 is a forward / reverse clutch FC, R
This is an unload valve for returning the pressure oil from C to the oil tank 37 and stopping the traveling of the combine. A pedal operation tool 38 is linked to the unload valve 36,
The configuration is such that the driving stop operation can be easily and quickly switched. Further, a parking brake 40 is also linked to the pedal operating tool 38, so that the operation of one operating tool can stop the traveling and activate the parking brake 40.

As shown in FIG. 6, a variable type valve having the above-described first and second switching valves 30, 39 and a pivot valve 33a is provided .
One relief valve 33 is housed in one second hydraulic block 46, and as shown in FIGS. 3 and 4, the flow priority valve 32, the pair of hydraulic cylinders 31 and the second relief valve 48 are connected to one first hydraulic block 46. 47.

Next, the structure of the first hydraulic block 47 will be described. As shown in FIG. 3, the two hydraulic blocks 46, 47 are sandwiched between the first hydraulic block 47 and the second hydraulic block 46 with respect to the front of the transmission case 8.
They are linked in this order.

Next, the first and second hydraulic blocks 47, 46
Will be described. As shown in FIG. 3, in the first hydraulic block 47, a pump port a is provided on the upper surface of the front end, and a spool 32A of the flow priority valve 32 that receives the pressure oil through the pump port a is provided vertically. It is. A first pressure oil supply path 34 and a second pressure oil supply path 35 are vertically arranged in parallel from the flow priority valve 32 toward the second hydraulic block 46. And a control flow is supplied through the second pressure oil supply path 35. Flow priority valve 32
4 and 5, cylinders 31, 31 for a pair of left and right side brakes 26, 26 are provided, and the drive arm 4 is provided in the cylinders 31, 31, as shown in FIGS.
Pistons 31A, 31A driven by 1, 41 are provided so that their axes are aligned vertically, and are provided in parallel with the spool 32A of the flow priority valve 32. When the first hydraulic block 47 is viewed from the front, the flow priority valve 32
The space is provided between the first and the 31st for effective use of the arrangement space. Further, a relief valve 48 is provided behind the left and right cylinders 31 and 31 and between the two cylinders 31 and 31.
Is also set in a state set in the vertical direction.
As shown in FIGS. 5 and 3, inside the second hydraulic block 46, first and second switching valves 30, 39 and a variable first relief valve 33 are vertically arranged in parallel. In the figure, reference numeral 52 denotes the first and second switching valves 3 for the side brake 26.
0 and 39 are drive rods for driving the spools 30A and 39A, and 53 is a variable first relief valve 33.
Is a drive rod for driving the plunger 33A.

Next, the operation of the continuously variable transmission 1 and the forward and reverse clutches FC and RC by the shift lever 49 will be described. As shown in FIG. 2, a speed change lever 49 and a sector gear 50 are supported by a shift operation portion of the continuously variable transmission 1, and a motor 51 that drives the sector gear 50 to rotate is provided.
The fan-shaped gear 50 is provided with a pressure-sensitive sensor (not shown) for detecting the operation direction of the shift lever 49.

The state shown in FIG. 2 is a state in which the shift lever 49 is operated to the neutral stop position N. If the shift lever 49 is operated to the forward side F and the reverse side R from this state, this operation is performed by the fan. The motor 51 operates so that the sector gear 50 rotates in the operation direction of the transmission lever 49 according to the signal from the pressure sensor detected by the pressure sensor of the mold gear 50, and the continuously variable transmission 1 moves to the high speed side. The shift operation is performed. When the operation of the transmission lever 49 is stopped at a desired operation position, the motor 51 also stops, and the transmission lever 49 and the continuously variable transmission 1 are held at this operation position by the motor 51.

In the claims, reference numerals are provided for convenience of comparison with the drawings, but the present invention is not limited to the configuration shown in the attached drawings.

[Brief description of the drawings]

FIG. 1 is a schematic view showing a transmission structure in a transmission case.

FIG. 2 is a schematic diagram of a hydraulic circuit for hydraulic cylinders for left and right side gears, a first switching valve and a variable relief valve, a second switching valve, a forward and reverse clutch, and the like.

FIG. 3 is a longitudinal sectional side view in a connected state of first and second hydraulic blocks and a flow priority valve.

FIG. 4 is a cross-sectional plan view of first and second hydraulic blocks.

FIG. 5 is a longitudinal sectional front view of a first hydraulic block.

FIG. 6 is a front view of a second hydraulic block.

[Description of Signs] 31 Hydraulic cylinder for steering 32 Flow priority valve 34 First pressure oil supply path 35 Second pressure oil supply path 48 Second relief valve 54 Third relief valve FC, RC forward / reverse hydraulic clutch a Branch oil Road

Continuation of the front page (56) References JP-A 1-161114 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16D 25/12 A01D 69/00-69/10 B60K 17 / 06-17/08 B60R 16/08

Claims (1)

(57) [Claims] (1) a flow priority valve (32);
The branched control flow advances through the forward / backward switching valve (39)
Disconnect to hydraulic clutch (FC) and reverse hydraulic clutch (RC)
And the flow priority valve
The excess flow branched at (32) is passed to the steering hydraulic cylinder (3
1) and the flow priority
From the valve (32) to the forward / reverse switching valve (39).
The second pressure oil supply oil passage (3) provided to supply the control flow
From the middle of 5), the forward hydraulic clutch (FC) and the reverse
Oil passage for supplying lubricating oil to each hydraulic clutch (RC)
(B), and the forward hydraulic pressure is provided in the branch oil passage (b).
Each work of clutch (FC) and reverse hydraulic clutch (RC)
A second relief valve (48) for securing dynamic pressure is interposed,
In the return oil passage from the forward / reverse switching valve (39) to the tank
Is the forward hydraulic clutch (FC) and the reverse hydraulic clutch
3rd relief valve to secure the lubrication pressure of each RC
A third oil passage in the return oil passage.
The upstream side of the leaf valve (54) is
From the second relief valve (48) on the road (b)
Traveling hydraulic device co Nbain which is connected to a site downstream side.