KR102606152B1 - Power transmission apparatus and valve unit - Google Patents

Abstract

A power transmission device and valve unit capable of always cooling the friction plate group of a soft clutch mechanism or the friction plate group of a spin clutch mechanism are provided.
A soft clutch mechanism 70 capable of slowing down the power output from the power input shaft 14 and transmitting it to the side clutch shaft 30, and a spin capable of reversing the power output from the power input shaft 14 and transmitting it to the side clutch shaft 30. A swing clutch shaft 60 on which the clutch mechanism 80 is arranged, a valve unit 90 capable of supplying and discharging hydraulic oil discharged from the hydraulic pump to the soft clutch mechanism 70 and the spin clutch mechanism 80, and a swing clutch. It has a cooling passage 66 formed on the shaft 60, and coolant is supplied to the friction plate group 73 of the soft clutch mechanism 70 and the friction plate group 83 of the spin clutch mechanism 80 through the cooling passage 66. Cooling equipment is available for supply.

Description

Power transmission and valve unit {POWER TRANSMISSION APPARATUS AND VALVE UNIT}

The present invention is a power transmission device configured to transmit power output from a power source to the left and right traveling devices, and capable of turning the aircraft by the speed difference between the left and right traveling devices, and a power transmitting power to the left and right traveling devices. It relates to a valve unit used in a power transmission device that is provided with left and right side clutches and a plurality of swing clutches for switching between a transmission state and a blocking state that does not transmit power, enabling turning by multiple types of turning patterns.

A work machine that requires work on uneven ground, such as a combine, is equipped with a pair of left and right crawler-type traveling devices, and is configured to transmit power output from an engine as a power source to the left and right traveling devices through a power transmission device.

As disclosed in Patent Document 1, the power transmission device includes a power input shaft through which engine power is input, a left side clutch mechanism capable of transmitting the power output from the power input shaft to the left traveling device among the left and right traveling devices, and the left and right Among the traveling devices, there is a side clutch shaft equipped with a right side clutch mechanism that can be transmitted to the right traveling device, a wet multi-plate soft clutch mechanism that can reduce the power output from the power input shaft and transmit it to the side clutch shaft, and a side clutch shaft that can transmit the power output from the power input shaft. It is equipped with a swing clutch shaft equipped with a wet multi-disc spin clutch mechanism capable of reversing power and transmitting it to the side clutch shaft, and a valve unit capable of supplying and distributing hydraulic fluid to the soft clutch mechanism and the spin clutch mechanism.

Japanese Patent Publication No. 2009-78699

This type of power transmission device is configured to generate a relative speed difference between the left and right traveling devices by causing the friction plate group of the soft clutch mechanism to slip or the friction plate group of the spin clutch mechanism to slip when the aircraft turns. There was a risk that the friction plate group of the soft clutch mechanism may be damaged, or the friction plate group of the spin clutch mechanism may be damaged.

The present invention was made in view of the above-mentioned problems, and its purpose is to provide a power transmission device and a valve unit that can always cool the friction plate group of a soft clutch mechanism or the friction plate group of a spin clutch mechanism.

In order to achieve the above-described object, the characteristic configuration of the power transmission device according to the present invention is configured to transmit power output from a power source to the left and right traveling devices, and the aircraft is turned by the speed difference between the left and right traveling devices. A power transmission device capable of transmitting power, comprising: a power input shaft through which power from the power source is input; a left side clutch mechanism capable of transmitting power output from the power input shaft to a left traveling device among the left and right traveling devices; and a left and right traveling device. A side clutch shaft equipped with a right side clutch mechanism that can be transmitted to the middle right traveling device, a wet multi-plate soft clutch mechanism that can reduce the power output from the power input shaft and transmit it to the side clutch shaft, and a soft clutch mechanism of a wet multi-plate type capable of transmitting the power output from the power input shaft to the side clutch shaft. a swing clutch shaft arranged with a wet multi-plate spin clutch mechanism capable of reversing power and transmitting it to the side clutch shaft; a valve unit capable of supplying and discharging hydraulic fluid discharged from a hydraulic pump to the soft clutch mechanism and the spin clutch mechanism; , a cooling mechanism is provided that has a cooling passage formed in the swing clutch shaft and is capable of supplying cooling oil to the friction plate group of the soft clutch mechanism and the friction plate group of the spin clutch mechanism through the cooling passage.

According to the above-described configuration, the cooling mechanism can always supply cooling oil to the friction plate group of the soft clutch mechanism or the friction plate group of the spin clutch mechanism through the cooling passage. Since the friction plate group of the soft clutch mechanism and the friction plate group of the spin clutch mechanism are always cooled by the always supplied cooling oil, the risk of burnout due to frictional heat generated by the sliding of the friction plate group when the aircraft turns is reduced. Additionally, the cooling mechanism may be a dedicated one, and for example, the valve unit may function as a cooling mechanism.

In the present invention, the valve unit is configured to supply and discharge hydraulic oil to the left side clutch mechanism and the right side clutch mechanism, and the hydraulic oil discharged from the hydraulic pump is supplied to the valve unit. It is provided with a hydraulic circuit that supplies a right side clutch mechanism, an unload valve and a relief valve installed in the hydraulic circuit, and the valve unit transfers hydraulic oil discharged from one or both of the unload valve and the relief valve to the cooling oil. It is suitable if it is configured to supply to the cooling passage.

The hydraulic oil supplied to the left side clutch mechanism and the right side clutch mechanism is pressurized by a hydraulic pump. An unload valve and relief valve are provided to protect the hydraulic circuit from the pressure of this hydraulic oil. Additionally, the unload valve is configured to place the hydraulic circuit in an unloaded state when the internal hydraulic pressure of the hydraulic circuit exceeds a predetermined value, and the relief valve is configured to maintain the internal hydraulic pressure of the hydraulic circuit at a specified value.

Therefore, the hydraulic oil discharged from the unload valve or relief valve has its own pressure. And, since hydraulic oil can be supplied to the cooling passage as cooling oil using this hydraulic pressure, there is no need to separately provide a hydraulic pump for supplying cooling oil. Since the valve unit can function as a cooling mechanism, the power transmission device as a whole can be miniaturized.

In the present invention, a main body casing accommodating the left side clutch mechanism, the right side clutch mechanism, the soft clutch mechanism, and the spin clutch mechanism, and a unit casing accommodating the unload valve and the relief valve are provided, The unit casing is provided with a cavity having an opening and is installed in the main body casing so that the opening is blocked by the outer surface of the main body casing, and the cavity is divided into a first chamber and a second chamber by a partition wall. Suitable.

According to the above-described configuration, the cavity provided in the unit casing can be made to function as an oil chamber simply by installing the valve unit in the main body casing, thereby eliminating the need to install a separate dedicated oil chamber, thereby reducing the overall size of the power transmission device. can do.

The hydraulic oil discharged from the hydraulic pump has a high pressure before being supplied to the left side clutch mechanism, the right side clutch mechanism, the soft clutch mechanism, and the spin clutch mechanism, and accordingly, the hydraulic oil discharged from the unload valve and relief valve also has high pressure.

In comparison, the hydraulic oil discharged from the left side clutch mechanism, right side clutch mechanism, soft clutch mechanism, and spin clutch mechanism has low pressure.

If the valve unit is configured to have only one oil chamber, the hydraulic oil discharged from the unload valve and relief valve, and the hydraulic oil discharged from the left side clutch mechanism, right side clutch mechanism, soft clutch mechanism, and spin clutch mechanism, are Since it is recovered as a single oil loss, the high pressure of the hydraulic oil discharged from the unload valve and relief valve cannot be effectively utilized.

As described above, the cavity is divided into a first oil chamber and a second oil chamber by a partition wall, so that the low-pressure hydraulic oil discharged from the left side clutch mechanism, right side clutch mechanism, soft clutch mechanism, and spin clutch mechanism can be transferred to either one of the chambers. The high-pressure hydraulic oil discharged from the unload valve and relief valve can be recovered from either oil chamber. Therefore, the high pressure of the hydraulic oil discharged from the unload valve and relief valve can be effectively utilized.

In the present invention, the hydraulic circuit includes a left side clutch valve that controls the supply and discharge of hydraulic oil to the left side clutch mechanism, a right side clutch valve that controls the supply and discharge of hydraulic oil to the right side clutch mechanism, and the soft A swing clutch valve for controlling the supply and discharge of hydraulic oil to the clutch mechanism and the spin clutch mechanism is provided, and a drain port is provided in the first oil chamber to each of the left side clutch valve, the right side clutch valve, and the swing clutch valve. is connected, and the drain port provided in each of the unload valve and the relief valve is connected to the second oil chamber.

Low-pressure hydraulic oil discharged from the left side clutch mechanism, right side clutch mechanism, soft clutch mechanism, and spin clutch mechanism is discharged into the first oil chamber. This hydraulic oil can be supplied as lubricant to the main body casing.

In the second oil chamber, hydraulic oil pressurized by the hydraulic pump of the valve unit is discharged through the unload valve and relief valve. The hydraulic oil discharged into this second oil chamber can be supplied to the cooling passage as cooling oil for the friction plate group of the soft clutch mechanism or the friction plate group of the spin clutch mechanism.

In the present invention, one end of the side clutch shaft and one end of the swing clutch shaft are configured to protrude from the main body casing, and the unit casing is arranged to span one end of the side clutch shaft and one end of the swing clutch shaft. , the hydraulic circuit is provided with a switching valve for switching the supply and discharge of hydraulic oil to the soft clutch mechanism and the spin clutch mechanism, the left side clutch valve, the right side clutch valve, the swing clutch valve, the switch valve, and The unload valve is composed of a direct-acting multi-port solenoid valve and is configured so that the moving direction of the spool is parallel, and the left side clutch valve, the right side clutch valve, and the unload valve are located on the outer periphery of the unit casing. It is suitable if it is disposed at a location close to the one end of the side clutch shaft, and the swing clutch valve and the switching valve are disposed at a location near the one end of the swing clutch shaft on the outer periphery of the unit casing.

By arranging each valve so that the moving direction of the spool provided in each valve is parallel, wiring of the feed line to the solenoid provided in each valve becomes easy. Additionally, since the installation portion of each valve and the arrangement of each flow path provided inside the unit casing can be simplified, the valve unit as a whole can be miniaturized. Even if any valve breaks down, only the broken valve can be replaced without removing the valve unit from the main body casing.

In the present invention, the hydraulic circuit is provided with a supply passage for supplying hydraulic oil after operating the left side clutch mechanism and the right side clutch mechanism to the swing clutch valve, and the supply passage is provided with a filter, It is suitable if an inspection port communicating with the supply passage is provided on the outer periphery of the unit casing, and the filter is configured to be exchangeable through the inspection port.

According to the above-described configuration, the filter can be replaced from outside the unit casing.

In the present invention, it is suitable if the partition wall is provided on one or both of the unit casing and the main body casing.

According to the above-described configuration, the degree of freedom in the method of providing the partition increases.

In order to achieve the above-described object, the characteristic configuration of the valve unit according to the present invention includes a left and right side clutch that switches between a power transmission state that transmits power to the left and right traveling devices and a blocking state that does not transmit power, and a plurality of It is a valve unit used in a power transmission device that is equipped with a swing clutch and enables turning by multiple types of swing patterns, and includes a hydraulic circuit for supplying and distributing hydraulic oil to the left and right side clutches and the swing clutch, and the hydraulic circuit. An unload valve and a relief valve are installed, and the first oil chamber is divided into a first oil chamber into which hydraulic oil flows after operating the left and right side clutches and the swing clutch, and a second oil chamber into which hydraulic oil from the unload valve and the relief valve flows. It is at the point that it is.

According to the above-described configuration, it is possible to provide a valve unit capable of always cooling the friction plate group of the soft clutch mechanism or the friction plate group of the spin clutch mechanism.

1 is a longitudinal front view of a power transmission device.
Figure 2 is an explanatory diagram of a hydraulic circuit.
Figure 3 is a front view of the valve unit.
Figure 4 is a cross-sectional view taken along line IV-IV of Figure 3.
Figure 5 is a cross-sectional view taken along line VV of Figure 3.
FIG. 6 is a cross-sectional view taken along line VI-VI of FIG. 3.
Figure 7 is a rear view of the valve unit.

Hereinafter, an embodiment of the power transmission device according to the present invention will be described based on the drawings in a case where it is adopted for a normal type combine as an example of a harvester. In addition, the embodiments described below are all examples of the present invention, and the present invention is not limited by the description, and the specific configuration of each part can be appropriately changed and designed within the range where the effects of the present invention are exhibited.

〔Overall composition〕

The body of a normal combine for harvesting rice, barley, etc. is equipped with left and right traveling devices that can be raised and lowered relative to the body, as well as a harvesting section that raises and harvests the grain in the field as the combine moves forward, and is sent from the harvesting section. A threshing section where whole grains are received and threshed by rapid processing, and the threshed material sent from the threshing section is separated into rice, which is the object of sorting, and waste such as discharged straw, using a sorting method such as specific gravity sorting. Each work section, such as a storage section that stores the rice sent from the sorting section and a discharge section that discharges the rice stored in the storage section to the outside of the combine, an engine as a power source for each work section, and the power of the engine is distributed to each work section. It is equipped with a power transmission device for the harvester that delivers the harvester, and a control unit that allows workers to board and perform driving operations.

The power transmission device for harvesters includes a belt-type transmission mechanism through which the engine power is input, a hydrostatic continuously variable transmission device that continuously changes the power output from the belt-type transmission mechanism, and a continuously variable transmission device that transmits the power output from the stepless transmission device to the left and right traveling devices. A power transmission device 10 (see FIG. 1) that is configured so as to be able to turn the aircraft by the speed difference between the left and right traveling devices is provided.

[Power transmission device]

As shown in FIG. 1, the power transmission device 10 is provided with a power input unit 13 on the upper part of the main body casing 11 to which the output shaft 12 of the continuously variable transmission can be splined. The power input unit 13 consists of a power input shaft 14 supported on the main body casing 11, and a high-speed gear 15 and a low-speed gear 16 splined to the power input shaft 14.

Downstream of the power input shaft 14, an auxiliary transmission transmission shaft 17 is supported on the main body casing 11. A high-speed gear 18 and a low-speed gear 19 are arranged on the auxiliary transmission shaft 17 so that relative rotation is possible. The high-speed gear 15 and the high-speed gear 18 are meshed, and the low-speed gear 16 and the low-speed gear 19 are meshed.

Between the high-speed gear 18 and the low-speed gear 19, a shifter ( 20) is provided. The shifter 20 is configured to be spline-coupled with the high-speed gear 18 or the low-speed gear 19 depending on the position along the axial direction of the auxiliary transmission shaft 17.

When the shifter 20 is slid toward the high-speed gear 18 and the shifter 20 and the high-speed gear 18 are splined, the rotation of the power input shaft 14 is caused by the high-speed gear 15, the high-speed gear 18, and the shifter. It is transmitted to the transmission shaft (17) for auxiliary transmission through (20).

When the shifter 20 is slid toward the low-speed gear 19 and the shifter 20 and the low-speed gear 19 are splined, the rotation of the power input shaft 14 is caused by the low-speed gear 16, the low-speed gear 19, and the shifter. It is transmitted to the transmission shaft (17) for auxiliary transmission through (20).

In this way, by switching the position of the shifter 20 between a state in which it is engaged with the high-speed gear 18 and a state in which it is engaged in the low-speed gear 19, the power of the power input shaft 14 is switched to two high and low speeds (high and low speeds). ) and is transmitted to the auxiliary transmission shaft (17).

On the auxiliary transmission shaft 17, a straight forward electric gear 21 and a turning electric gear 22 are arranged so that they can rotate together by spline coupling. Additionally, the auxiliary transmission shaft 17 is provided with a parking brake mechanism 23.

Downstream of the auxiliary transmission shaft 17, a side clutch shaft 30 and a swing clutch shaft 60 are provided, which are supported on the main body casing 11.

[Side clutch shaft]

The straight-forward electric gear 21 disposed on the secondary transmission electric shaft 17 is engaged with the side clutch shaft input gear 31 splined to the side clutch shaft 30, and the rotation of the power input shaft 14 is the secondary transmission. It is transmitted to the side clutch shaft 30 through the transmission shaft 17, the transmission gear 21 for straight movement, and the side clutch shaft input gear 31.

The side clutch shaft 30 includes a left side clutch mechanism 40 capable of transmitting the power output from the power input shaft 14 to the left traveling device among the left and right traveling devices, and a right side clutch mechanism 40 capable of transmitting the power output from the power input shaft 14 to the right traveling device among the left and right traveling devices. A clutch mechanism 50 is disposed. In addition, since the power transmission device 10 in FIG. 1 is drawn so that the front side is the front of the aircraft, the left side clutch mechanism 40 is disposed on the right, and the right side clutch mechanism 50 is disposed on the left. there is.

On the side clutch shaft 30, a left output gear 32 and a right output gear 33 are respectively disposed so as to be capable of relative rotation. The left output gear 32 is meshed with the left electric gear 24 that outputs power to the left traveling device, and the right output gear 33 is meshed with the right electric gear 25 that outputs power to the right traveling device.

[Left side clutch mechanism]

The left side clutch mechanism 40 is comprised of an engaging clutch. The side clutch shaft 30 can rotate integrally with the side clutch shaft 30 by spline engagement to the right of the left output gear 32 in FIG. 1, and is provided along the axial direction of the side clutch shaft 30. A slideable left engaging portion 41 is provided.

The left engaging portion 41 is pressed by a spring 42 to engage with the left output gear 32. As the left engaging portion 41 engages with the left output gear 32, rotation of the side clutch shaft 30 is transmitted to the left traveling device through the left engaging portion 41 and the left output gear 32. At this time, the left side clutch mechanism 40 is said to be in an engaged state (power transmission state).

From the valve unit 90 installed on the left side (right side in FIG. 1) of the main body casing 11, the left output gear 32 is supplied through the supply passage 34 formed inside the side clutch shaft 30. By supplying hydraulic oil to the inside of the oil chamber 43 formed between and the left engaging portion 41, the piston 44 moves to the right in FIG. 1, and the left engaging portion 41 resists the pressing force of the spring 42. As it moves to the right in FIG. 1, the engagement between the left output gear 32 and the left engaging portion 41 is released. At this time, the rotation of the side clutch shaft 30 is not transmitted to the left output gear 32 through the left engaging portion 41. At this time, the left side clutch mechanism 40 is said to be in a disengaged state (blocked state). In addition, a predetermined amount or more of the hydraulic fluid supplied to the oil chamber 43 is returned to the valve unit 90 through the return passage 36 formed inside the side clutch shaft 30.

When the supply of hydraulic oil to the oil chamber 43 is stopped, the left engaging portion 41 is moved to the left in FIG. 1 by the pressing force of the spring 42, and the left engaging portion 41 and the left output gear 32 are aligned. In conjunction with this, the piston 44 can also be moved to the left in FIG. 1, so the hydraulic oil is discharged from the oil chamber 43. This hydraulic oil is returned to the valve unit 90 through the supply passage 34.

[Right side clutch mechanism]

The right side clutch mechanism 50 is comprised of an engaging clutch. The side clutch shaft 30 can rotate integrally with the side clutch shaft 30 to the left of the right output gear 33 in FIG. 1 by spline engagement, and is provided along the axial direction of the side clutch shaft 30. A slideable right engaging portion 51 is provided.

The right engaging portion 51 is pressed by a spring 52 so as to engage with the right output gear 33. As the right engaging portion 51 engages with the right output gear 33, rotation of the side clutch shaft 30 is transmitted to the right traveling device through the right engaging portion 51 and the right output gear 33. At this time, the right side clutch mechanism 50 is said to be in an engaged state (power transmission state).

Hydraulic oil is supplied from the valve unit 90 to the inside of the oil chamber 53 formed between the right output gear 33 and the right engaging portion 51 through the supply passage 35 formed inside the side clutch shaft 30. As a result, the piston 54 moves to the left in FIG. 1, and the right engaging portion 51 resists the pressing force of the spring 52 and moves to the left in FIG. 1, so that the right output gear 33 and the right The engagement of the engaging portion 51 is released. At this time, the rotation of the side clutch shaft 30 is not transmitted to the right output gear 33 through the right engaging portion 51. At this time, the right side clutch mechanism 50 is said to be in a disengaged state (blocked state). In addition, a predetermined amount or more of the hydraulic fluid supplied to the oil chamber 53 is returned to the valve unit 90 through the return passage 36 formed inside the side clutch shaft 30.

When the supply of hydraulic oil to the oil chamber 53 is stopped, the right engaging portion 51 is moved to the right in FIG. 1 by the pressing force of the spring 52, and the right engaging portion 51 and the right output gear 33 are aligned. As the piston 54 also moves to the right in FIG. 1, the hydraulic oil is discharged from the oil chamber 53. Additionally, this hydraulic oil is returned to the valve unit 90 through the supply passage 35.

When both the left side clutch mechanism 40 and the right side clutch mechanism 50 are in a power transmission state, the aircraft travels straight. If either the left side clutch mechanism 40 or the right side clutch mechanism 50 is in the blocked state, the aircraft turns and runs as described below.

[Swivel clutch shaft]

On the swing clutch shaft 60, a soft clutch input gear 61 that engages with the input relay gear 37 disposed on the outer periphery of the right engaging portion 51 provided on the side clutch shaft 30 is arranged to be relatively rotatable. there is.

[Soft clutch mechanism]

A wet multi-plate soft clutch mechanism 70 is disposed between the swing clutch shaft 60 and the soft clutch input gear 61, which can reduce the power output from the power input shaft 14 and transmit it to the side clutch shaft 30. there is.

The soft clutch mechanism 70 is installed integrally with the swing clutch shaft 60 and the rotatable clutch housing 71 and the soft clutch input gear 61 by spline engagement, and is connected to the swing clutch shaft 60 and the clutch housing. A plurality of outer friction plates coupled to the barrel shaft 72 and the clutch housing 71 in a non-relatively rotationable manner positioned between (71) and a plurality of inner friction plates engaged to a non-relatively rotatable relationship to the barrel shaft 72 are arranged alternately. It is provided with a friction plate group 73, a piston 74 that presses the friction plate group 73, and a spring 75 that presses the piston 74 in a direction away from the friction plate group 73. .

The piston 74 is supplied from the valve unit 90 to the inside of the oil chamber 76 formed inside the clutch housing 71 through the supply passage 62 formed inside the swing clutch shaft 60. By moving to the left in 1, the friction plate group 73 is pressed and the slip between the outer friction plate and the inner friction plate is regulated, so that the clutch housing 71 and the barrel shaft 72 are in a power transmission state in which relative rotation is regulated. . The rotation of the soft clutch input gear 61 is transmitted to the swing clutch shaft 60 through the barrel shaft 72, the friction plate group 73, and the clutch housing 71. Additionally, hydraulic oil is supplied as cooling oil to the friction plate group 73 through the supply passage 62.

When the supply of hydraulic oil to the oil chamber 76 is stopped, the piston 74 is moved to the right in FIG. 1 by the pressing force of the spring 75, and the pressure on the friction plate group 73 is released to separate the outer friction plate and the inner friction plate. Slip between them is allowed, and the clutch housing 71 and the barrel 72 are in a blocked state in which relative rotation is allowed. Additionally, as the piston 74 moves to the right in FIG. 1, the hydraulic oil is discharged from the oil chamber 76. Additionally, this hydraulic oil is discharged into the inside of the main body casing 11 through the supply passage 62.

[Spin clutch mechanism]

The turning electric gear 22 provided on the auxiliary transmission transmission shaft 17 is engaged with the spin clutch input gear 63 arranged to be relatively rotatable on the turning clutch shaft 60. Therefore, the rotation direction of the turning electric gear 22 and the rotation direction of the spin clutch input gear 63 are opposite.

A wet multi-plate spin clutch mechanism 80 is disposed between the swing clutch shaft 60 and the spin clutch input gear 63 to reverse the power output from the power input shaft 14 and transmit it to the side clutch shaft 30. there is.

The spin clutch mechanism 80 is installed integrally with the swing clutch shaft 60, the swing clutch housing 81, and the spin clutch input gear 63, which can rotate integrally with the swing clutch shaft 60 by spline engagement. A plurality of outer friction plates engaged in a non-relatively rotationable manner with the tubular shaft 82 and the clutch housing 81 located between (81) and a plurality of inner friction plates engaged in a non-relatively rotatable manner with the tubular shaft 82 are arranged alternately. A friction plate group 83, a piston 84 that presses the friction plate group 83, and a spring 85 that presses the piston 84 in a direction away from the friction plate group 83 are provided.

The piston 84 is supplied from the valve unit 90 to the inside of the oil chamber 86 formed inside the clutch housing 81 through the supply passage 64 formed inside the swing clutch shaft 60. By moving to the right in 1, the friction plate group 83 is pressed and the slip between the outer friction plate and the inner friction plate is regulated, so that the clutch housing 81 and the barrel shaft 82 are in a power transmission state in which relative rotation is regulated. . The rotation of the spin clutch input gear 63 is transmitted to the swing clutch shaft 60 through the barrel shaft 82, the friction plate group 83, and the clutch housing 81. Additionally, hydraulic oil is supplied as cooling oil to the friction plate group 83 through the supply passage 64.

When the supply of hydraulic oil to the oil chamber 86 is stopped, the piston 84 is moved to the left in FIG. 1 by the pressing force of the spring 85, and the pressure on the friction plate group 83 is released to separate the outer friction plate and the inner friction plate. Slip between them is allowed, and the clutch housing 81 and the barrel 82 are in a blocked state in which relative rotation is allowed. Additionally, as the piston 84 moves to the left in FIG. 1, the hydraulic oil is discharged from the oil chamber 86. Additionally, this hydraulic oil is discharged into the inside of the main body casing 11 through the supply passage 64.

[Swivel output gear]

On the swing clutch shaft 60, a swing output gear 65 is disposed between the clutch housing 71 and the clutch housing 81 so as to be rotatable integrally by spline engagement. The turning output gear 65 is arranged to be capable of relative rotation with the side clutch shaft 30 between the left output gear 32 and the right output gear 33, which are respectively disposed to be relatively rotatable on the side clutch shaft 30. It is engaged with the output relay gear (38).

The power output through the soft clutch mechanism 70 or the spin clutch mechanism 80 is transmitted to the output relay gear 38 through the swing output gear 65.

A left swing clutch mechanism 45 is provided between the output relay gear 38 and the left output gear 32, and a right swing clutch mechanism 55 is provided between the output relay gear 38 and the right output gear 33. It is done.

The left swing clutch mechanism 45 and the right swing clutch mechanism 55 are both configured as wet multi-plate clutch mechanisms. In addition, the left swing clutch mechanism 45 and the right swing clutch mechanism 55 are arranged so that a plurality of friction plate groups are pressed against each other, and are configured to be in a reaction force transmission state even when the supply of hydraulic oil is stopped.

[Turn left]

When supplying hydraulic oil from the valve unit 90 to the inside of the oil chamber 43 through the supply passage 34 formed inside the side clutch shaft 30, the oil chamber 46 provided in the left swing clutch mechanism 45 Hydraulic oil is supplied to the system, the sliding of the plurality of friction plate groups is regulated, and the left swing clutch mechanism 45 is in a power transmission state.

At this time, as described above, since the left side clutch mechanism 40 is in a blocked state, power is not transmitted to the left output gear 32 through the left engaging portion 41.

However, power from the soft clutch mechanism 70 or the spin clutch mechanism 80 is transmitted to the left output gear 32 through the swing output gear 65, the output relay gear 38, and the left swing clutch mechanism 45. It can be. Accordingly, power at a lower speed or in the reverse direction is transmitted to the left output gear 32 than when power is transmitted through the left engaging portion 41, and the aircraft makes a slow turn or a slow turn to the left.

[Turn right]

When supplying hydraulic fluid from the valve unit 90 to the inside of the oil chamber 53 through the supply passage 35 formed inside the side clutch shaft 30, the oil chamber 56 provided in the right swing clutch mechanism 55 Hydraulic oil is also supplied, the sliding of the plurality of friction plate groups is regulated, and the right swing clutch mechanism 55 is in a power transmission state.

At this time, as described above, since the right side clutch mechanism 50 is in a blocked state, power is not transmitted to the right output gear 33 through the right engaging portion 51.

However, power from the soft clutch mechanism 70 or the spin clutch mechanism 80 is transmitted to the right output gear 33 through the swing output gear 65, the output relay gear 38, and the right swing clutch mechanism 55. It can be. Accordingly, power at a lower speed or in a reverse direction is transmitted to the right output gear 33 than when power is transmitted through the right engaging portion 51, and the aircraft makes a slow turn or a slow turn to the right.

A hydraulic pump 26 (see FIG. 2) driven by power output from the output shaft 12 of the continuously variable transmission is installed in the main body casing 11. The hydraulic pump 26 is configured to suck the lubricating oil stored inside the main body casing 11 and supply it to the valve unit 90 as operating oil.

[Valve unit]

The valve unit 90 is provided with left and right side clutches and a plurality of turning clutches that switch between a power transmission state that transmits power to the left and right traveling devices and a blocking state that does not transmit power, and turns by multiple types of turning patterns. It is used in the power transmission device 10 that makes it possible, and in this embodiment, as shown in FIGS. 2 to 7, the hydraulic oil discharged from the hydraulic pump 26 is transferred to the left side clutch mechanism 40, It is provided with a hydraulic circuit (92) that supplies and supplies power to each of the right side clutch mechanism (50), soft clutch mechanism (70), spin clutch mechanism (80), left swing clutch mechanism (45), and right swing clutch mechanism (55). there is.

In the hydraulic circuit 92, a left side clutch valve V1 that controls the supply and discharge of hydraulic oil to the left side clutch mechanism 40, and a right side clutch valve that controls the supply and discharge of hydraulic oil to the right side clutch mechanism 50. (V2), a swing clutch valve (V3) that controls supply and discharge of hydraulic fluid to the soft clutch mechanism 70 and the spin clutch mechanism 80, and hydraulic fluid to the soft clutch mechanism 70 and the spin clutch mechanism 80 A switching valve (V4) for switching the supply and discharge of the hydraulic circuit (92), an unloading valve (V5) for putting the hydraulic circuit (92) in an unloaded state when the hydraulic pressure inside the hydraulic circuit (92) becomes more than a predetermined value, and the hydraulic circuit (92) A relief valve (V6) is provided to maintain the internal hydraulic pressure at a specified value.

In particular, the left side clutch valve (V1), right side clutch valve (V2), swing clutch valve (V3), changeover valve (V4), and unload valve (V5) are composed of direct-acting multi-port solenoid valves. Additionally, the operation of each valve is controlled by a control device not shown.

As shown in FIG. 1, one end of the side clutch shaft 30 and one end of the swing clutch shaft 60 are configured to protrude from the main body casing 11, and as shown in FIGS. 4 and 6, the valve unit The unit casing 91 accommodating each valve of 90 is arranged so as to span one end of the side clutch shaft 30 and one end of the swing clutch shaft 60.

The unit casing 91 is manufactured by casting, and the above-described left side clutch valve (V1), right side clutch valve (V2), swing clutch valve (V3), changeover valve (V4) and unload valve (V5) are installed. Each section and each flow path described below is formed by cutting.

3 to 7, the unit casing 91 includes a left side clutch valve (V1), a right side clutch valve (V2), a swing clutch valve (V3), a changeover valve (V4), and an unload valve (V5). ) is arranged so that the moving direction of the spool is parallel.

The left side clutch valve (V1), right side clutch valve (V2), and unload valve (V5) are disposed on the outer circumference of the unit casing (91) at a location close to the insertion portion (93) of one end of the side clutch shaft (30). there is. Therefore, wiring of the feed line to each solenoid provided in the left side clutch valve (V1), right side clutch valve (V2), and unload valve (V5) is easy.

The swing clutch valve V3 and the switching valve V4 are disposed on the outer peripheral portion of the unit casing 91 at a location close to the insertion portion 94 of one end of the swing clutch shaft 60. Therefore, wiring of the feed line to each solenoid provided in the swing clutch valve V3 and the switching valve V4 is easy.

Additionally, since the installation portion of each valve and the arrangement of each flow path provided inside the unit casing 91 can be simplified, the valve unit 90 can be downsized as a whole. Even if any valve breaks down, only the broken valve can be replaced without removing the valve unit 90 from the main body casing 11.

The unit casing 91 is provided with a cavity C having an opening and is installed in the main body casing 11 so that the opening is blocked by the outer surface of the main body casing 11. The cavity C is divided into a first chamber C1 and a second chamber C2 by a partition wall 95 (see Fig. 7) provided integrally with the unit casing 91.

This is because the cavity C provided in the unit casing 91 can be made to function as the first oil chamber C1 or the second oil chamber C2 simply by installing the valve unit 90 in the main body casing 11. Since there is no need to install a separate dedicated oil room, the power transmission device 10 can be downsized as a whole.

The unit casing 91 is provided with an input portion 99 for hydraulic oil discharged from the hydraulic pump 26.

2, 4, and 6, the unit casing 91 includes a left side clutch valve (V1), a right side clutch valve (V2), an unload valve (V5), and a relief valve from the input portion 99. There is an input flow path (L1) that supplies hydraulic oil to each input port (P1, P2, P5, and P6) of (V6).

2 and 6, the supply/discharge port A1 of the left side clutch valve V1 is located at the insertion portion 93 of one end of the side clutch shaft 30 installed in the unit casing 91. The supply passage 34 formed in the clutch shaft 30 is connected to the supply and discharge passage L2 for supplying and discharging the hydraulic oil. The drain port T1 of the left side clutch valve V1 communicates with the first oil chamber C1 through the discharge passage L3.

2 and 5, the supply/discharge port A2 of the right side clutch valve V2 is located at the insertion portion 93 of one end of the side clutch shaft 30 installed in the unit casing 91. It is connected to a supply and discharge passage L4 that supplies and discharges hydraulic oil to the supply passage 35 formed in the clutch shaft 30. The drain port T2 of the right side clutch valve V2 communicates with the first oil chamber C1 through the discharge passage L5.

Additionally, as shown in FIG. 6 , in the insertion portion 93, a supply passage L6 that receives hydraulic oil from the conveyance passage 36 formed in the side clutch shaft 30 communicates. As shown in Figs. 2 and 5, the supply passage L6 communicates with the input port P3 of the swing clutch valve V3.

As shown in FIGS. 2 and 5, a filter 96 is provided in the supply passage L6. An inspection port 97 communicating with the supply flow passage L6 is provided on the outer periphery of the unit casing 91. The inspection port 97 is sealed by a removable cap 98. The filter 96 is configured to be replaceable from the outside of the unit casing 91 through an inspection opening 97.

2 and 5, the output port A3 of the swing clutch valve V3 communicates with the supply passage L7, and the input port P4 of the switching valve V4 is connected through the supply passage L7. ) is supplied with hydraulic oil. The drain port T3 of the swing clutch valve V3 communicates with the first oil chamber C1 through the discharge passage L8.

2 and 4, the output port A4 of the switching valve V4 is located at the insertion portion 94 of one end of the swing clutch shaft 60 provided in the unit casing 91. It is connected to a supply passage L9 that supplies hydraulic oil to the supply passage 62 formed at (60).

2 and 4, the output port B4 of the switching valve V4 is located at the insertion portion 94 of one end of the swing clutch shaft 60 provided in the unit casing 91. It is connected to a supply passage L10 that supplies hydraulic oil to the supply passage 64 formed at (60).

As described above, in the first oil chamber C1, there is a discharge passage L3 connected to the drain port T1 provided in the left side clutch valve V1, and a drain port T2 provided in the right side clutch valve V2. A discharge passage L5 communicating with and a discharge passage L8 communicating with the drain port T3 provided on the swing clutch valve V3 are connected.

As shown in FIG. 2, the side surface of the main body casing 11 is provided with a drain port 27 communicating with the first oil chamber C1, and the hydraulic oil discharged into the first oil chamber C1 is discharged from the drain port ( It is discharged into the interior of the main body casing 11 through 27) and used as lubricating oil.

As shown in FIGS. 2 and 4, a discharge flow path L11 connected to the output port A5 (and drain port T5) provided in the unload valve V5 is connected to the second oil chamber C2. , a discharge passage L12 connected to the drain port T6 provided in the relief valve V6 is connected to the discharge passage L11.

The second oil chamber C2 is separated from the main body casing 11 by a sealed bearing portion of the swing clutch shaft 60. The cooling passage 66 formed inside the swing clutch shaft 60 has an open end formed inside the second oil chamber C2. The hydraulic oil in the second oil chamber C2 is supplied to the cooling passage 66 from the open end.

When the aircraft moves straight, substantially all of the hydraulic oil discharged from the hydraulic pump 26 is supplied to the second oil chamber C2 from at least one or both of the unload valve V5 and the relief valve V6. Even when the aircraft is turning, a part of the hydraulic oil discharged from the hydraulic pump 26 is supplied to the second oil chamber C2 from one or both of the unload valve V5 and the relief valve V6.

At least a portion of the high-pressure hydraulic oil discharged from the hydraulic pump 26 is always supplied to the second oil chamber C2, and this hydraulic oil is used as cooling oil, and is formed in the cooling passage inside the swing clutch shaft 60 from the open end. Through (66), it is supplied to the friction plate group 73 of the soft clutch mechanism 70 and the friction plate group 83 of the spin clutch mechanism 80. As a result, the friction plate group 73 of the soft clutch mechanism 70 and the friction plate group 83 of the spin clutch mechanism 80 are not limited to when the soft clutch mechanism 70 or the spin clutch mechanism 80 is in a power transmission state. and is always cooled even when in a blocked state. The risk of burnout due to frictional heat generated by sliding of the friction plate group 73 or sliding of the friction plate group 83 when the aircraft is turning is reduced.

In this way, the valve unit 90 is configured to also function as a cooling mechanism that supplies the hydraulic oil discharged from one or both of the unload valve V5 and the relief valve V6 to the cooling passage 66 as cooling oil. . Additionally, the cooling mechanism may be a cooling-only mechanism provided separately from the valve unit 90.

In the above-described embodiment, the case where the partition wall 95 is provided integrally with the unit casing 91 has been described, but the case is not limited to this. The partition wall 95 may be provided integrally with the main body casing 11, or may be provided on each of the unit casing 91 and the main body casing 11. Additionally, the partition wall 95 may be provided separately on one or both of the unit casing 91 and the main body casing 11.

In the above-described embodiment, the case where the power transmission device according to the present invention is adopted in a normal type combine has been described, but the harvester may be a self-contained combine, and can be applied to various harvesters such as a corn harvester in addition to the combine. there is.

10: power transmission device
11: main body casing
14: Power input shaft
26: hydraulic pump
30: side clutch axis
40: Left side clutch mechanism
50: Right side clutch mechanism
60: Swivel clutch shaft
66: Cooling passage
70: Soft clutch mechanism
73: Friction plate group
80: Spin clutch mechanism
83: Friction plate group
90: valve unit
91: unit casing
92: hydraulic circuit
95: Bulkhead
96: filter
97: Inspection port
C: common part
C1: 1st loss
C2: Second loss
L6: Supply Euro
T1: drain port
T2: drain port
T3: drain port
T5: drain port
T6: drain port
V1: Left side clutch valve
V2: Right side clutch valve
V3: Swivel Clutch Valve
V4: Diverter valve
V5: Unload valve
V6: relief valve

Claims (9)

A power transmission device configured to transmit power output from a power source to the left and right traveling devices, and capable of turning the aircraft by the speed difference between the left and right traveling devices,
A power input shaft through which power from the power source is input,
A side clutch shaft having a left side clutch mechanism capable of transmitting power output from the power input shaft to a left traveling device among the left and right traveling devices and a right side clutch mechanism capable of transmitting the power output from the left and right traveling devices to a right traveling device among the left and right traveling devices;
A wet multi-plate soft clutch mechanism capable of decelerating the power output from the power input shaft and transmitting it to the side clutch shaft, and a wet multi-plate spin clutch mechanism capable of reversing the power output from the power input shaft and transmitting it to the side clutch shaft. An arranged swing clutch shaft,
a valve unit capable of supplying and discharging hydraulic oil discharged from a hydraulic pump to the soft clutch mechanism and the spin clutch mechanism;
a cooling mechanism having a cooling passage formed in the swing clutch shaft and capable of supplying cooling oil to the friction plate group of the soft clutch mechanism and the friction plate group of the spin clutch mechanism through the cooling passage,
The valve unit is configured to supply and discharge hydraulic oil to the left side clutch mechanism and the right side clutch mechanism,
The valve unit is provided with a hydraulic circuit that supplies hydraulic oil discharged from the hydraulic pump to the left side clutch mechanism and the right side clutch mechanism, and an unload valve and a relief valve installed in the hydraulic circuit,
The valve unit is configured to supply operating oil discharged from one or both of the unload valve and the relief valve to the cooling passage as the cooling oil,
a main body casing housing the left side clutch mechanism, the right side clutch mechanism, the soft clutch mechanism, and the spin clutch mechanism;
A unit casing accommodating the unload valve and the relief valve is provided,
The unit casing has a cavity having an opening and is installed in the main body casing so that the opening is blocked by an outer surface of the main body casing,
The cavity is divided into a first chamber and a second chamber by a partition,
In the hydraulic circuit, a left side clutch valve that controls the supply and discharge of hydraulic oil to the left side clutch mechanism, a right side clutch valve that controls the supply and discharge of hydraulic oil to the right side clutch mechanism, the soft clutch mechanism and the spindle. A swing clutch valve is provided to control the supply and discharge of hydraulic oil to the clutch mechanism,
Drain ports provided in each of the left side clutch valve, the right side clutch valve, and the swing clutch valve are connected to the first oil chamber,
A power transmission device in which drain ports provided in each of the unload valve and the relief valve are connected to the second oil chamber. delete delete delete The method of claim 1, wherein one end of the side clutch shaft and one end of the swing clutch shaft are configured to protrude from the main body casing,
The unit casing is arranged to span one end of the side clutch shaft and one end of the swing clutch shaft,
A switching valve is provided in the hydraulic circuit to switch the supply and discharge of hydraulic oil to the soft clutch mechanism and the spin clutch mechanism,
The left side clutch valve, the right side clutch valve, the swing clutch valve, the switching valve, and the unload valve are composed of direct-acting multi-port solenoid valves, and are configured so that the moving direction of the spool is parallel,
The left side clutch valve, the right side clutch valve, and the unload valve are disposed on the outer periphery of the unit casing at a location close to the one end of the side clutch shaft,
The power transmission device wherein the swing clutch valve and the switching valve are disposed on an outer peripheral portion of the unit casing at a location close to the one end of the swing clutch shaft. The method according to claim 1 or 5, wherein the hydraulic circuit is provided with a supply passage for supplying hydraulic oil after operating the left side clutch mechanism and the right side clutch mechanism to the swing clutch valve,
A filter is provided in the supply passage,
An inspection port communicating with the supply passage is provided on the outer periphery of the unit casing,
A power transmission device in which the filter is configured to be exchangeable through the inspection port. The power transmission device according to claim 1 or 5, wherein the partition wall is provided on one or both of the unit casing and the main body casing. Left and right side clutches and a plurality of turning clutches are provided to switch between a power transmission state that transmits power to the left and right traveling devices and a blocking state that does not transmit power, so that power transmission is possible through multiple types of turning patterns. It is a valve unit used in the device,
a hydraulic circuit for supplying and distributing hydraulic oil to the left and right side clutches and the swing clutch;
An unload valve and a relief valve installed in the hydraulic circuit are provided,
A first oil chamber into which hydraulic oil flows after operating the left and right side clutches and the swing clutch is partitioned, and a second oil chamber into which hydraulic oil from the unload valve and the relief valve flows,
In the hydraulic circuit, a left side clutch valve that controls the supply and discharge of hydraulic oil to the left side clutch mechanism, a right side clutch valve that controls the supply and discharge of hydraulic oil to the right side clutch mechanism, and hydraulic oil to the plurality of swing clutches. A swing clutch valve is provided to control supply and discharge,
Drain ports provided in each of the left side clutch valve, the right side clutch valve, and the swing clutch valve are connected to the first oil chamber,
A valve unit in which drain ports provided in each of the unload valve and the relief valve are connected to the second oil chamber. The power transmission device according to claim 6, wherein the partition wall is provided on one or both of the unit casing and the main body casing.

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