CN210600137U - Power reversing and power high-low hydraulic control system and tractor comprising same - Google Patents

Abstract

The utility model relates to a power switching-over and power height hydraulic control system and tractor, power switching-over and power height hydraulic control system include power switching-over oil circuit, power height oil circuit, lubricated oil circuit, advance oil pipe way and return oil pipe way, power switching-over oil circuit and power height oil circuit equally divide do not with advance oil pipe way and return oil pipe way intercommunication, the one end of lubricated oil circuit with advance oil pipe way intercommunication, the other end communicates with power switching-over oil circuit and power height oil circuit respectively, be equipped with the overflow valve on the lubricating oil circuit, the oil inlet and the oil pipe way intercommunication of advancing of overflow valve, the oil-out of overflow valve communicates with power switching-over oil circuit and power height oil circuit respectively. The multi-gear switching can be realized, only one oil inlet pipeline is needed, the structure is compact, the cost is low, and the multi-gear switching device can be used for tractors of various models.

Description

Power reversing and power high-low hydraulic control system and tractor comprising same

Technical Field

The utility model relates to the field of agricultural machinery, concretely relates to power switching-over and power height hydraulic control system and contain its tractor.

Background

The informatization of the traction machinery is an important component of modern agricultural production, is an important supporting technology of intelligent agricultural machinery, carries out deep research on the traction machinery, and meets the requirements of national development strategy. There are two modes of traditional tractor shifting, mechanical shifting and power shifting.

For power gear shifting, a high-end machine type has a small number of electric proportional systems, good control can be achieved, the cost is high, the cleanliness of oil liquid of the system needs to be guaranteed, and the requirement on maintenance is high. The electric proportional control system has high control precision and high requirement on a control strategy, can realize proportional control change of a two-gear switching system of a vehicle, has higher price and weaker anti-pollution capacity, and has higher cost if an independent hydraulic control system is used. The tractor steering system can be selected to use an oil return way to realize the auxiliary function, for the tractor, particularly a multipurpose hydraulic oil system shared by the tractor and a transmission system, the cleanliness control of the hydraulic system is high in cost, the maintenance requirement of the system is stricter, otherwise, the clamping stagnation phenomenon is easy to occur, serious hidden dangers exist, and the stability and the reliability are relatively low. Most of systems controlled by common conventional on-off solenoid valves have low cost, but cannot realize precise control. The conventional switch electromagnetic valve has the advantages of low cost, pollution resistance superior to that of a proportional valve, no requirement on a high control strategy and only application to realizing forward gear and reverse gear switching or high-gear and low-gear switching of a vehicle. The conventional switching electromagnetic valve has low control precision, cannot avoid serious impact in work, and has higher requirements on the material, the manufacturing process and the like of a transmission system structural member.

In the prior art, a hydraulic system for realizing power reversing and power high-low switching by adopting a switching electromagnetic valve is not adopted.

SUMMERY OF THE UTILITY MODEL

The utility model aims to solve the technical problem that a tractor that realizes accurate control and low cost's power switching-over and power height hydraulic control system and contain it is provided.

The utility model provides an above-mentioned technical problem's technical scheme as follows: the utility model provides a power switching-over and power height hydraulic control system, includes power switching-over oil circuit, power height oil circuit, lubricated oil circuit, advances oil pipe way and returns oil pipe way, power switching-over oil circuit with power height oil circuit equally divide respectively with advance oil pipe way with return oil pipe way intercommunication, lubricated oil circuit's one end with advance oil pipe way intercommunication, the other end respectively with power switching-over oil circuit with power height oil circuit intercommunication, be equipped with the overflow valve on the lubricating oil circuit, the oil inlet of overflow valve with advance oil pipe way intercommunication, the oil-out of overflow valve respectively with power switching-over oil circuit with power height oil circuit intercommunication.

The utility model has the advantages that: the power reversing and power high-low hydraulic control system is a hydraulic control system capable of realizing multi-gear switching, a power reversing oil path and a power high-low oil path are connected with oil inlet pipelines, switching of a high gear and a low gear of an advancing gear, switching of a high gear and a low gear of a reversing gear and switching of the advancing gear and the reversing gear can be realized, only one oil inlet pipeline is needed, the structure is compact, the cost is low, and the power reversing and power high-low hydraulic control system can be used for tractors of various models.

On the basis of the technical scheme, the utility model discloses can also do following improvement.

Further, the power reversing oil way comprises a forward gear clutch, a reverse gear clutch, a first reversing device, a inching valve, a first energy accumulator and a first throttling device; the power reversing oil path has a first state and a second state, and the first reversing device is used for switching the first state and the second state; the forward gear clutch, the reverse gear clutch and the inching valve are all connected with the first reversing device through pipelines, the oil return pipeline is connected with the first reversing device, the inching valve is connected with the first throttling device through a pipeline, the first throttling device is communicated with the oil inlet pipeline, and a pipeline between the inching valve and the first throttling device is connected with the first energy accumulator through a first branch pipeline; in the first state, the inching valve is communicated with the forward gear clutch, and the reverse gear clutch is communicated with the oil return pipeline; in the second state, the inching valve is communicated with the reverse gear clutch, and the forward gear clutch is communicated with the oil return pipeline; and the oil outlet of the overflow valve is respectively communicated with the forward gear clutch and the reverse gear clutch.

The beneficial effect of adopting the further scheme is that: the first throttling device, the inching valve and the first energy accumulator are communicated with the forward gear clutch or the reverse gear clutch, so that the forward gear clutch or the reverse gear clutch is slowly combined. The first reversing device switches the state of the power reversing oil way, and the forward gear clutch or the reverse gear clutch is communicated with the oil return pipeline, so that the quick separation function is realized. The power reversing oil circuit can prevent discomfort to human bodies caused by unsmooth work due to impact generated by rapid combination, has good control precision, and can reduce system impact. The inching valve is adopted in the pipeline, so that the pressure in the oil way can be flexibly adjusted by adjusting the inching valve according to the use requirement, and the vehicle can keep a half-clutch state for a long time and run at a low speed. And high-pressure hydraulic oil overflows through the overflow valve and enters the forward clutch and the reverse clutch to lubricate the device.

Further, the power reversing oil way is also provided with a third state, the first reversing device is used for switching the first state, the second state and the third state, and in the third state, the forward gear clutch and the reverse gear clutch are both disconnected with the inching valve and are both communicated with the oil return pipeline.

The beneficial effect of adopting the further scheme is that: and the third state is a non-working state, hydraulic oil is unloaded, and the forward clutch and the reverse clutch are directly returned to the oil tank.

Further, the power high-low oil way comprises a high-gear clutch, a low-gear clutch, a second reversing device, a second energy accumulator and a second throttling device; the power high-low oil path is provided with a fourth state and a fifth state, and the second reversing device is used for switching the fourth state and the fifth state; the high-gear clutch, the low-gear clutch and the second throttling device are all connected with the second reversing device through pipelines, the oil return pipeline is connected with the second reversing device, the second throttling device is communicated with the oil inlet pipeline, and a pipeline between the second throttling device and the second reversing device is connected with the second energy accumulator through a third branch pipeline; in the fourth state, the second throttling device is communicated with the high-gear clutch, and the low-gear clutch is communicated with the oil return pipeline; in the fifth state, the second throttling device is communicated with the low-gear clutch, and the high-gear clutch is communicated with the oil return pipeline; and the oil outlet of the overflow valve is respectively communicated with the high-gear clutch and the low-gear clutch.

The beneficial effect of adopting the further scheme is that: the gear shifting control device can realize accurate control of gear shifting without adopting an electric proportional control valve, reduces cost and can be widely applied to the field of tractors. And the second throttling device and the second energy accumulator are communicated with the high-gear clutch or the low-gear clutch, so that the slow combination of the high-gear clutch or the low-gear clutch is realized. The second reversing device switches the state of the power high-low oil way, and the high-gear clutch or the low-gear clutch is communicated with the oil return pipeline, so that the quick separation function is realized. The dynamic high-low oil way can prevent the impact caused by the rapid combination of the high-gear clutch or the low-gear clutch, so that the discomfort caused by the unsmooth work can be avoided to the human body, the control precision is good, and the impact of the system can be reduced. And high-pressure hydraulic oil overflows through the overflow valve and enters the high-gear clutch and the low-gear clutch to lubricate the device.

Further, the power high-low oil path further has a sixth state, the second reversing device is used for switching the fourth state, the fifth state and the sixth state, and in the sixth state, the high-gear clutch and the low-gear clutch are both disconnected from the second throttling device and are both communicated with the oil return pipeline.

The beneficial effect of adopting the further scheme is that: and the sixth state is a non-working state, and the hydraulic oil is unloaded and directly returned to the oil tank from the high-gear clutch and the low-gear clutch.

Further, the first reversing device and the second reversing device are both electromagnetic reversing valves.

The beneficial effect of adopting the further scheme is that: the electromagnetic directional valve has low cost and better anti-pollution capability than a proportional valve.

Further, the first energy accumulator and the second energy accumulator are gravity type energy accumulators, spring type energy accumulators or airbag type energy accumulators.

Further, the first throttling device and the second throttling device are both throttling valves or throttling joints.

Further, an oil pump is arranged on the oil inlet pipeline, an inlet of the oil pump is communicated with an oil tank through the oil inlet pipeline, and an outlet of the oil pump is communicated with the power reversing oil way and the power high-low oil way through the oil inlet pipeline respectively.

The beneficial effect of adopting the further scheme is that: the oil pump supplies the hydraulic oil in the oil tank to the power reversing oil path and the power high-low oil path.

Further, still be provided with on the oil inlet pipeline and inhale oil filter and export filter, the import of oil pump with between the oil tank be equipped with on the oil inlet pipeline inhale oil filter, the exit of oil pump be equipped with on the oil inlet pipeline export filter, export filter respectively through the oil inlet pipeline with power switching-over oil circuit with power dynamic high-low oil circuit is linked together.

The beneficial effect of adopting the further scheme is that: inhale oil cleaner and export filter and filter the impurity in the hydraulic oil, guarantee the cleanliness that gets into in the oil circuit, avoid appearing the jamming phenomenon.

The utility model discloses still relate to a tractor, include power switching-over and power height hydraulic control system.

Drawings

Fig. 1 is a schematic structural diagram of a power reversing and power high-low hydraulic control system of the present invention;

fig. 2 is the pressure change curve of the power reversing and power height hydraulic control system of the utility model.

In the drawings, the components represented by the respective reference numerals are listed below:

1. a power reversing oil way, 10, a forward gear clutch, 20, a reverse gear clutch, 30, a first reversing device, 40, an inching valve, 50, a first energy accumulator, 51, a first branch pipeline, 52, a second branch pipeline, 60, a first throttling device,

2. 70 parts of power high and low oil way, a high gear clutch, 80 parts of low gear clutch, 90 parts of second reversing device, 100 parts of second energy accumulator, 101 parts of third branch pipeline, 102 parts of fourth branch pipeline, 110 parts of second throttling device,

3. a lubricating oil passage, 120, an overflow valve,

4. an oil inlet pipeline 130, an outlet filter 140, an oil pump 150, an oil suction filter,

5. an oil return pipeline is arranged on the oil pipe,

160. and an oil tank.

Detailed Description

The principles and features of the present invention are described below in conjunction with the following drawings, the examples given are only intended to illustrate the present invention and are not intended to limit the scope of the present invention.

As shown in fig. 1-2, a power reversing and power high-low hydraulic control system includes a power reversing oil path 1, a power high-low oil path 2, a lubricating oil path 3, an oil inlet pipeline 4 and an oil return pipeline 5, wherein the power reversing oil path 1 and the power high-low oil path 2 are respectively communicated with the oil inlet pipeline 4 and the oil return pipeline 5, one end of the lubricating oil path 3 is communicated with the oil inlet pipeline 4, the other end of the lubricating oil path 3 is respectively communicated with the power reversing oil path 1 and the power high-low oil path 2, an overflow valve 120 is arranged on the lubricating oil path 3, an oil inlet of the overflow valve 120 is communicated with the oil inlet pipeline 4, and an oil outlet of the overflow valve 120 is respectively communicated with the power reversing oil path 1 and the power high-low oil path 2.

As a further scheme of the embodiment, the power reversing oil path 1 comprises a forward clutch 10, a reverse clutch 20, a first reversing device 30, a cunning valve 40, a first accumulator 50 and a first throttling device 60; the power reversing oil path 1 has a first state and a second state, and the first reversing device 30 is used for switching the first state and the second state; the forward gear clutch 10, the reverse gear clutch 20 and the inching valve 40 are all connected with the first reversing device 30 through pipelines, the oil return pipeline 5 is connected with the first reversing device 30, the inching valve 40 is connected with the first throttling device 60 through a pipeline, the first throttling device 60 is communicated with the oil inlet pipeline 4, and a pipeline between the inching valve 40 and the first throttling device 60 is connected with the first energy accumulator 50 through a first branch pipeline 51; in the first state, the inching valve 40 is communicated with the forward clutch 10, and the reverse clutch 20 is communicated with the oil return pipeline 5; in the second state, the inching valve 40 is communicated with the reverse clutch 20, and the forward clutch 10 is communicated with the oil return pipeline 5; the oil outlet of the overflow valve 120 is respectively communicated with the forward clutch 10 and the reverse clutch 20.

Specifically, the inching valve 40 is used for adjusting the pressure of the power reversing oil path 1 by operating a valve core in a mechanical operation mode to move, and the pressure in the oil path can be flexibly adjusted through the inching valve 40 according to use requirements, so that a vehicle can be kept in a half-clutch state for a long time.

Specifically, the first accumulator 50 is internally divided into a first cavity and a second cavity by a first accumulator piston, a first energy storage mechanism is arranged in the second cavity, two ends of the first energy storage mechanism are respectively abutted to the first accumulator piston and the inner wall of the first accumulator 50 and used for storing energy, the first branch pipeline 51 is communicated with the first cavity, the oil return pipeline 5 is communicated with the second cavity of the first accumulator 50 by a second branch pipeline 52, and a small amount of hydraulic oil flowing from the first cavity to the second cavity can flow to the oil return pipeline 5 along the second branch pipeline 52 due to a gap between the first accumulator piston and the side wall of the first accumulator 50. The first energy accumulating means may be a spring.

As a further solution of this embodiment, the power reversing oil path 1 further has a third state, and the first reversing device 30 is configured to switch the first state, the second state, and the third state, and in the third state, both the forward clutch 10 and the reverse clutch 20 are disconnected from the inching valve 40 and both are communicated with the oil return line 5.

As a further aspect of the present embodiment, the power high-low oil path 2 includes a high gear clutch 70, a low gear clutch 80, a second reversing device 90, a second accumulator 100, and a second throttling device 110; the power high-low oil passage 2 has a fourth state and a fifth state, and the second reversing device 90 is used for switching the fourth state and the fifth state; the high-gear clutch 70, the low-gear clutch 80 and the second throttling device 110 are all connected with the second reversing device 90 through pipelines, the oil return pipeline 5 is connected with the second reversing device 90, the second throttling device 110 is communicated with the oil inlet pipeline 4, and a pipeline between the second throttling device 110 and the second reversing device 90 is connected with the second energy accumulator 100 through a third branch pipeline 101; in the fourth state, the second throttling device 110 is communicated with the high clutch 70, and the low clutch 80 is communicated with the oil return pipeline 5; in the fifth state, the second throttling device 110 is communicated with the low clutch 80, and the high clutch 70 is communicated with the oil return pipeline 5; the oil outlet of the relief valve 120 is communicated with the high clutch 70 and the low clutch 80, respectively.

Specifically, the second accumulator 100 is divided into a third cavity and a fourth cavity by a second accumulator piston, a second energy storage mechanism is arranged in the fourth cavity, two ends of the second energy storage mechanism are respectively abutted to the second accumulator piston and the inner wall of the second accumulator 100 and used for storing energy, the third branch pipe 101 is communicated with the third cavity, the oil return pipe 5 is communicated with the fourth cavity of the second accumulator 100 by a fourth branch pipe 102, and a small amount of hydraulic oil flowing from the third cavity into the fourth cavity can flow to the oil return pipe 5 along the fourth branch pipe 102 due to a gap between the second accumulator piston and the side wall of the second accumulator 100. The second energy accumulating means may be a spring.

As a further solution of this embodiment, the high-low power oil path 2 further has a sixth state, and the second reversing device 90 is configured to switch the fourth state, the fifth state and the sixth state, where in the sixth state, both the high clutch 70 and the low clutch 80 are disconnected from the second throttling device 110 and both are communicated with the oil return line 5.

As a further solution of this embodiment, the first direction changing device 30 and the second direction changing device 90 are both electromagnetic direction changing valves.

Specifically, preferably, as shown in fig. 1, the first reversing device 30 is a three-position four-way electromagnetic reversing valve, and the second reversing device 90 is a three-position four-way electromagnetic reversing valve. The electromagnetic directional valve is a hydraulic system control module, and is used for a direction control device of pressure oil in a hydraulic system to realize a pressure oil directional function, the first directional device 30 realizes switching between oil paths of the forward clutch 10 and the reverse clutch 20, and the second directional device 90 realizes switching between oil paths of the high clutch 70 and the low clutch 80. The switching mode of the electromagnetic directional valve is the prior art in the field.

As shown in FIG. 1, when the left position of the first reversing device 30 is in communication, the flow passages ① → ② are in communication and the flow passages ② 0 → ② 1 are in communication, when the right position of the first reversing device 30 is in communication, the flow passages ② → ③ are in communication and the flow passages ① → ④ are in communication, when the middle position of the first reversing device 30 is in communication, the flow passages ② → ③ are in communication and the flow passages ④ → ③ are in communication.

As shown in FIG. 1, when the left position of the second reversing device 90 is in communication, the flow passages ⑤ → ⑥ are in communication and the flow passages ⑥ 0 → ⑥ 1 are in communication, when the right position of the second reversing device 90 is in communication, the flow passages ⑥ → ⑦ are in communication and the flow passages ⑤ → ⑧ are in communication, when the neutral position of the second reversing device 90 is in communication, the flow passages ⑥ → ⑦ are in communication and the flow passages ⑧ → ⑦ are in communication.

As a further solution of this embodiment, the first energy accumulator 50 and the second energy accumulator 100 are both gravity type energy accumulators, spring type energy accumulators, or airbag type energy accumulators.

Specifically, the first accumulator 50 and the second accumulator 100 are energy storage devices, and the energy accumulators can convert energy in the system into compression energy or potential energy, absorb pressure impact, and play a role in adjusting the pressure of the hydraulic system.

As a further solution of this embodiment, the first throttling device 40 and the second throttling device 110 are both throttle valves or throttle joints.

Specifically, the first throttling device 40 and the second throttling device 110 are devices which are installed in a hydraulic pipeline and achieve a hydraulic oil throttling function, and the size of the throttling hole can directly influence the pressure on two sides of the throttling device. The first throttling device 40 plays a role in buffering when pressure oil enters the forward clutch 10 or the reverse clutch 20; the second throttle device 110 achieves a certain buffering effect when the pressure oil enters the high clutch 70 or the low clutch 80.

The person skilled in the art can flexibly select the models of the first throttle device 40, the second throttle device 110, the first accumulator 50 and the second accumulator 100 to meet the requirements of different control accuracies.

As a further scheme of this embodiment, an oil pump 140 is disposed on the oil inlet pipeline 4, an inlet of the oil pump 140 is communicated with an oil tank 160 through the oil inlet pipeline 4, and an outlet of the oil pump 140 is respectively communicated with the power reversing oil path 1 and the power high-low oil path 2 through the oil inlet pipeline 4.

As a further scheme of this embodiment, the oil inlet pipeline 4 is further provided with an oil suction filter 150 and an outlet filter 130, the oil inlet pipeline 4 between the inlet of the oil pump 140 and the oil tank 160 is provided with the oil suction filter 150, the oil inlet pipeline 4 at the outlet of the oil pump 140 is provided with the outlet filter 130, and the outlet filter 130 is respectively communicated with the power reversing oil path 1 and the power high-low oil path 2 through the oil inlet pipeline 4.

The working process of the power reversing and power high-low hydraulic control system in the embodiment is as follows:

as shown in fig. 2, a curve C1 represents the pressure of the hydraulic oil received by the forward clutch 10 or the high clutch 70, and a curve C2 represents the pressure of the hydraulic oil received by the reverse clutch 20 or the low clutch 80.

When the oil pump 140 is operated, hydraulic oil in the oil tank 160 passes through the oil suction filter 150, enters the oil pump 140, and passes through the outlet filter 130.

The pressure of hydraulic oil entering the forward clutch 10 does not increase instantaneously but gradually increases according to bernoulli's principle, the first accumulator 50 regulates the line pressure within a set pressure range so that the pressure increases gradually instead of rapidly increasing, the pressure of hydraulic oil entering the forward clutch 10 increases gradually under the action of the first throttle device 60, the pressure of hydraulic oil entering the intermediate region is increased gradually under the action of the first accumulator 50, the pressure of hydraulic oil entering the intermediate region is increased gradually but not rapidly increasing under the action of the first accumulator 50, the pressure of hydraulic oil entering the intermediate region is increased gradually, the pressure of hydraulic oil entering the intermediate region is decreased gradually, the hydraulic oil entering the intermediate region is increased gradually, the reverse clutch 10 is increased gradually, the pressure of hydraulic oil entering the intermediate region is decreased gradually, the intermediate region is increased, the pressure of hydraulic oil entering the intermediate region C60, the reverse clutch 10 is decreased gradually, the hydraulic oil entering the intermediate region C15, the intermediate region is increased gradually, the hydraulic oil entering the intermediate region C60, the reverse clutch 10, the hydraulic oil is increased smoothly, the hydraulic oil is reduced smoothly, the hydraulic oil is smoothly and the hydraulic oil is smoothly returned to the intermediate region, the hydraulic oil is smoothly returned to the intermediate region of the intermediate region 20, the intermediate region, the hydraulic oil tank 30, the hydraulic oil tank 20, the hydraulic oil is stably returned to the hydraulic oil tank 20, the hydraulic oil is stably returned to the hydraulic oil tank 20, and the hydraulic oil tank 20.

When the right position of the first reversing device 30 is switched on, namely in a second state, hydraulic oil flows to the inching valve 40 through the first throttling device 60, the valve core of the inching valve 40 is operated to move in a mechanical operation mode, the opening of the inching valve 40 is gradually opened, the pressure in the pipeline is increased, a flow passage ① → ④ of the first reversing device 30 is communicated, the reverse clutch 20 is pushed to be slowly combined, meanwhile, the first energy accumulator 50 absorbs pressure energy, the pressure of the hydraulic oil entering the reverse clutch 20 is gradually increased under the action of the first throttling device 60, the pressure of the reverse clutch 20 is gradually increased under the action of the first energy accumulator 50, the reverse clutch 20 is pushed to be slowly combined, the process is reflected in a curve C2 of a region D in the figure 2, a small end stable pressure change region at the front section is gradually increased, the pressure is completely combined with the reverse clutch 20 at the last stage, the problem of impact gear shifting is well solved, the rest has good smoothness, the hydraulic oil flow of the forward gear is directly unloaded from a middle region D120 of the reverse clutch 20 through a quick clutch 10, and a quick oil return valve 35 of the quick clutch 20, and a quick oil return valve 35 of the hydraulic oil return clutch 7, the quick oil return valve 20, which is directly reflected by a quick oil return valve 10 of the quick clutch 10, which is blocked by the first throttling device 60.

When the first reversing device 30 is de-energized, i.e. the power reversing oil path is in the third state, the hydraulic oil is delivered to the lubrication line 3 through the relief valve 120.

The pressure in the hydraulic fluid entering the high clutch 70 is not instantaneously increased to a maximum value but gradually increased according to bernoulli's principle by switching the second reversing device 90 as shown in fig. 1, when the left position of the second reversing device 90 is engaged, i.e., in a fourth state, the hydraulic fluid is communicated to the second reversing device 90 through the second throttling device 110, the flow passage ⑤ → ⑥ of the second reversing device 90, pushing the high clutch 70 to be slowly engaged, the flow rate of the hydraulic fluid is controlled under the action of the second throttling device 110, the pressure of the hydraulic fluid entering the high clutch 70 is not instantaneously increased to a maximum value but gradually increased according to bernoulli's principle, the second accumulator 100 regulates the pressure in the line within a set pressure range, the pressure is gradually increased rather than rapidly increased, the pressure of the high clutch 70 is gradually increased under the action of the second accumulator 100, the high clutch 70 is pushed to be slowly engaged, the process is reflected in a curve C1 of a region B in fig. 2, a small end steady pressure change interval of the front section, the pressure is gradually increased to a region B → the pressure of the high clutch 70 is completely increased, the hydraulic fluid is completely returned to the high clutch 70, the flow path of the second reversing device 90, the second throttling device 90, the flow path is directly returned to the low clutch 70, the flow path of the second throttling device 90, the flow path 3680, the flow path is smoothly returned to the second reversing device 90, the flow path 3680, the flow path is smoothly, the flow path 3680, the flow path is smoothly returned to the high clutch 70, the flow path is smoothly lubricated region C of the second reversing device 3680, the low clutch 70, the.

The second reversing device 90 is switched, when the right position of the second reversing device 90 is switched on, namely in a fifth state, hydraulic oil is communicated with the second reversing device 90 through the second throttling device 110, a flow passage ⑤ → ⑧ of the second reversing device 90 pushes the low clutch 80 to be slowly combined, and meanwhile, the second energy accumulator 100 absorbs pressure energy, under the action of the second throttling device 110, the pressure of the hydraulic oil entering the low clutch 80 is gradually increased, under the action of the second energy accumulator 100, the pressure of the low clutch 80 is gradually increased, and the low clutch 80 is pushed to be slowly combined, the process is reflected in a curve C2 of a region D in the figure 2, a small end of a front section is in a stable pressure change interval, the pressure is gradually increased, and the last low clutch 80 is completely combined, so that the impact problem of gear shifting is well reduced, the smoothness is good, the rest of the hydraulic oil blocked by the second throttling device 110 lubricates the high clutch 70 and the low clutch 80 through an overflow valve 120, the pressure of the high clutch 70 is directly reflected in a high-gear oil return pipeline ⑦, and the hydraulic oil pressure of the high clutch 70 is directly reflected in a high-gear oil return pipeline ⑦.

When the second reversing device 90 is de-energized, i.e. the power reversing oil path is in the sixth state, the hydraulic oil is delivered to the lubrication line 3 through the relief valve 120.

In this embodiment, the power reversing and power high-low hydraulic control system can realize switching among the following gears:

1. forward gear high gear: the first commutation device 30 is switched on to the left and the second commutation device 90 is switched on to the left.

2. Forward gear low gear: the first commutation device 30 is switched on to the left and the second commutation device 90 is switched on to the right.

3. Reverse gear high gear: the first commutation device 30 is switched on to the right and the second commutation device 90 is switched on to the left.

4. Reverse gear and low gear: the first commutation device 30 is switched on to the right and the second commutation device 90 is switched on to the right.

5. And (3) non-working state: the first commutation device 30 is switched on in neutral and the second commutation device 90 is switched on in neutral.

The utility model discloses still relate to a tractor, include power switching-over and power height hydraulic control system.

In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship indicated based on the drawings, and are only for convenience of description and simplification of the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present application, unless expressly stated or limited otherwise, the first feature may be directly on or directly under the second feature or indirectly via intermediate members. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

The above description is only for the preferred embodiment of the present invention, and is not intended to limit the present invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included within the protection scope of the present invention.

Claims (10)

1. A power reversing and power high-low hydraulic control system is characterized by comprising a power reversing oil way (1), a power high-low oil way (2), a lubricating oil way (3), an oil inlet pipeline (4) and an oil return pipeline (5), the power reversing oil way (1) and the power high-low oil way (2) are respectively communicated with the oil inlet pipeline (4) and the oil return pipeline (5), one end of the lubricating oil path (3) is communicated with the oil inlet pipeline (4), the other end of the lubricating oil path is respectively communicated with the power reversing oil path (1) and the power high-low oil path (2), an overflow valve (120) is arranged on the lubricating oil path (3), an oil inlet of the overflow valve (120) is communicated with the oil inlet pipeline (4), and an oil outlet of the overflow valve (120) is respectively communicated with the power reversing oil way (1) and the power high-low oil way (2).

2. The power reversing and power high-low hydraulic control system according to claim 1, wherein the power reversing oil circuit (1) comprises a forward clutch (10), a reverse clutch (20), a first reversing device (30), a inching valve (40), a first accumulator (50) and a first throttling device (60); the power reversing oil path (1) has a first state and a second state, and the first reversing device (30) is used for switching the first state and the second state; the forward gear clutch (10), the reverse gear clutch (20) and the inching valve (40) are connected with the first reversing device (30) through pipelines, the oil return pipeline (5) is connected with the first reversing device (30), the inching valve (40) is connected with the first throttling device (60) through a pipeline, the first throttling device (60) is communicated with the oil inlet pipeline (4), and a pipeline between the inching valve (40) and the first throttling device (60) is connected with the first energy accumulator (50) through a first branch pipeline (51); in the first state, the inching valve (40) is communicated with the forward clutch (10), and the reverse clutch (20) is communicated with the oil return pipeline (5); in the second state, the inching valve (40) is communicated with the reverse clutch (20), and the forward clutch (10) is communicated with the oil return pipeline (5); an oil outlet of the overflow valve (120) is respectively communicated with the forward gear clutch (10) and the reverse gear clutch (20).

3. A power reversing and power high-low hydraulic control system according to claim 2, characterized in that the power reversing oil path (1) further has a third state, the first reversing device (30) is used for switching the first state, the second state and the third state, and in the third state, the forward clutch (10) and the reverse clutch (20) are both disconnected from the inching valve (40) and both communicated with the oil return line (5).

4. A power reversing and power high and low hydraulic control system according to claim 2, characterized in that the power high and low oil passage (2) comprises a high gear clutch (70), a low gear clutch (80), a second reversing device (90), a second accumulator (100) and a second throttling device (110); the power high-low oil path (2) has a fourth state and a fifth state, and the second reversing device (90) is used for switching the fourth state and the fifth state; the high-gear clutch (70), the low-gear clutch (80) and the second throttling device (110) are connected with the second reversing device (90) through pipelines, the oil return pipeline (5) is connected with the second reversing device (90), the second throttling device (110) is communicated with the oil inlet pipeline (4), and a pipeline between the second throttling device (110) and the second reversing device (90) is connected with the second energy accumulator (100) through a third branch pipeline (101); in the fourth state, the second throttling device (110) is communicated with the high-gear clutch (70), and the low-gear clutch (80) is communicated with the oil return pipeline (5); in the fifth state, the second throttling device (110) is communicated with the low-gear clutch (80), and the high-gear clutch (70) is communicated with the oil return pipeline (5); an oil outlet of the overflow valve (120) is respectively communicated with the high-gear clutch (70) and the low-gear clutch (80).

5. A power reversing and power high-low hydraulic control system according to claim 4, characterized in that the power high-low oil passage (2) further has a sixth state in which the high range clutch (70) and the low range clutch (80) are both open-circuited to the second throttle device (110) and both in communication with the return line (5), and the second reversing device (90) is used to switch the fourth state, the fifth state and the sixth state.

6. A power reversing and power high-low hydraulic control system according to claim 5, characterized in that the first reversing device (30) and the second reversing device (90) are electromagnetic reversing valves.

7. A power reversing and power high-low hydraulic control system according to claim 5, characterized in that the first accumulator (50) and the second accumulator (100) are both gravity accumulators, spring accumulators or gas bag accumulators.

8. The power reversing and power high-low hydraulic control system according to any one of claims 1 to 7, characterized in that an oil pump (140) is arranged on the oil inlet pipeline (4), an inlet of the oil pump (140) is communicated with an oil tank (160) through the oil inlet pipeline (4), and an outlet of the oil pump (140) is respectively communicated with the power reversing oil path (1) and the power high-low oil path (2) through the oil inlet pipeline (4).

9. The power reversing and power high-low hydraulic control system according to claim 8, wherein an oil suction filter (150) and an outlet filter (130) are further arranged on the oil inlet pipeline (4), the oil suction filter (150) is arranged on the oil inlet pipeline (4) between an inlet of the oil pump (140) and the oil tank (160), the outlet filter (130) is arranged on the oil inlet pipeline (4) at an outlet of the oil pump (140), and the outlet filter (130) is respectively communicated with the power reversing oil path (1) and the power high-low oil path (2) through the oil inlet pipeline (4).

10. A tractor comprising a power reversal and power high-low hydraulic control system according to any one of claims 1 to 9.

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