阅读说明：本技术 液压离合器控制系统 (Hydraulic clutch control system ) 是由 张三喜 ***亮 于 2019-08-22 设计创作，主要内容包括：本发明公开了一种液压离合器控制系统,属于液压控制领域。离合器需要从分离状态转变为闭合状态时,第一溢流阀工作,进油点进入的油液无法推动油缸的活塞杆。控制第一电磁球阀失电,第一电磁球阀封闭,第一溢流阀不工作,第二溢流阀工作,进油点进入的油液推动活塞杆伸出,但不能完全推出油缸的活塞杆,使离合器处于半闭合状态。控制第二电磁球阀失电,第二溢流阀不工作,第三溢流阀工作,进油点进入的油液将活塞杆完全推出油缸,实现离合器的完全闭合。这种设置中,离合器不是一次性完全闭合,而是先进入半闭合状态,再进入完全闭合状态,离合器闭合时存在缓冲,离合器在工作过程中产生的冲击、工作噪声以及摩擦片的磨损均较小。(The invention discloses a hydraulic clutch control system, and belongs to the field of hydraulic control. When the clutch needs to be changed from a separation state to a closing state, the first overflow valve works, and oil entering from the oil inlet point cannot push a piston rod of the oil cylinder. And controlling the first electromagnetic ball valve to lose power, closing the first electromagnetic ball valve, enabling the first overflow valve to not work, enabling the second overflow valve to work, and enabling oil entering from an oil inlet point to push a piston rod to extend out but not to completely push the piston rod of the oil cylinder so as to enable the clutch to be in a semi-closed state. And controlling the second electromagnetic ball valve to lose power, the second overflow valve to stop working, the third overflow valve to work, and the oil entering from the oil inlet point completely pushes the piston rod out of the oil cylinder to realize the complete closing of the clutch. In the arrangement, the clutch is not completely closed at one time, but enters a half-closed state firstly and then enters a completely closed state, buffering exists when the clutch is closed, and impact, working noise and abrasion of the friction plate generated in the working process of the clutch are small.)

1. A hydraulic clutch control system is characterized by comprising a two-position two-way reversing valve (1), a buffer valve group (2) and an oil cylinder (3),

an oil inlet point (H) of the hydraulic control system is communicated with a P oil port of the two-position two-way reversing valve (1) and an oil inlet of the buffer valve group (2), an oil port A of the two-position two-way reversing valve (1) is communicated with a rodless cavity of the oil cylinder (3), an oil port T of the two-position two-way reversing valve (1) is communicated with an oil return point (E) of the hydraulic control system and an oil outlet of the buffer valve group (2),

the buffer valve group (2) comprises a cartridge valve (201), a first overflow valve (202), a second overflow valve (203), a third overflow valve (204), a first electromagnetic ball valve (205) and a second electromagnetic ball valve (206), an oil inlet of the cartridge valve (201) is communicated with an oil inlet point (H) of the hydraulic clutch control system, a control oil port of the cartridge valve (201) is communicated with an oil inlet of the cartridge valve (201), an oil outlet of the cartridge valve (201) is communicated with a T oil port of the two-position two-way reversing valve (1),

an oil inlet of the first overflow valve (202), an oil inlet of the second overflow valve (203) and an oil inlet of the third overflow valve (204) are communicated with an oil inlet of the cartridge valve (201), an oil outlet of the first overflow valve (202) is communicated with an oil inlet of the first electromagnetic ball valve (205), an oil outlet of the second overflow valve (203) and an oil outlet of the first electromagnetic ball valve (205) are communicated with an oil inlet of the second electromagnetic ball valve (206), an oil outlet of the second electromagnetic ball valve (206) is communicated with an oil outlet of the third overflow valve (204), and an oil outlet of the third overflow valve (204) is communicated with a T oil port of the two-position two-way reversing valve (1),

the set pressure of the first overflow valve (202) is smaller than the force required for pushing the piston rod (31) of the oil cylinder (3), the set pressure of the second overflow valve (203) is larger than the force required for pushing the piston rod (31) of the oil cylinder (3), the set pressure of the second overflow valve (203) is smaller than the force required for pushing the piston rod (31) of the oil cylinder (3) to fully extend, and the set pressure of the third overflow valve (204) is equal to the force required for fully extending the piston rod (31) of the oil cylinder (3).

2. The hydraulic clutch control system according to claim 1, further comprising a first pressure switch (207), wherein the first pressure switch (207) is arranged between the port A of the two-position two-way selector valve (1) and the rodless cavity of the cylinder (3), and the critical pressure of the first pressure switch (207) is equal to the set pressure of the third relief valve (204).

3. The hydraulic clutch control system of claim 1, further comprising a second pressure switch (208), the second pressure switch (208) in communication with an oil feed (H) of the hydraulic control system, a threshold pressure of the second pressure switch (208) being less than a set pressure of the first spill valve (202).

4. The hydraulic clutch control system according to any one of claims 1 to 3, further comprising a controller (209), wherein the controller (209) is configured to control the operating states of the first electromagnetic ball valve (205), the second electromagnetic ball valve (206) and the two-position two-way reversing valve (1).

5. The hydraulic clutch control system according to any one of claims 1-3, further comprising a pressure gauge (210), wherein the pressure gauge (210) is in communication with an oil inlet point (H) of the hydraulic clutch control system.

6. The hydraulic clutch control system according to any one of claims 1-3, characterized in that the hydraulic clutch control system further comprises a filter (211), and the filter (211) is arranged between an oil inlet point (H) of the hydraulic control system and an oil inlet of the cartridge valve (201).

7. The hydraulic clutch control system according to claim 6, further comprising a first one-way valve (212), wherein an oil inlet of the first one-way valve (212) is communicated with an oil outlet of the filter (211), and an oil outlet of the first one-way valve (212) is communicated with an oil inlet of the cartridge valve (201).

8. The hydraulic clutch control system according to any one of claims 1 to 3, further comprising a second one-way valve (213), wherein an oil inlet of the second one-way valve (213) is communicated with a T oil port of the two-position two-way reversing valve (1), and an oil outlet of the second one-way valve (213) is communicated with an oil return point (E) of the hydraulic control system.

9. The hydraulic clutch control system according to any one of claims 1 to 3, characterized in that a first orifice (214) is provided between an oil inlet of the cartridge valve (201) and a control oil port of the cartridge valve (201).

10. The hydraulic clutch control system as claimed in any one of claims 1-3, characterized in that a second throttle hole (215) is arranged between the oil outlet of the cartridge valve (201) and the T oil port of the two-position two-way reversing valve (1).

Technical Field

The invention relates to the field of hydraulic control, in particular to a hydraulic clutch control system.

Background

At present, the full-turning rudder propeller is mainly driven by a diesel engine, and the driving force between the full-turning rudder propeller and the diesel engine is usually cut off or transmitted in a connecting mode through a hydraulic clutch.

The hydraulic clutch generally controls the extension and retraction of a piston rod of a cylinder of the hydraulic clutch to realize the separation and closing of the friction plates of the cylinder and the hydraulic clutch. However, when the oil cylinder of the hydraulic clutch is controlled, the piston rod of the oil cylinder of the hydraulic clutch is pushed by high-pressure oil, so that the engagement between the oil cylinder of the hydraulic clutch and the friction plate is relatively quick, the hydraulic clutch can generate relatively large impact in the working process, the working noise is relatively high, and the friction plate of the hydraulic clutch is relatively quickly abraded.

Disclosure of Invention

The embodiment of the invention provides a hydraulic clutch control system, which can reduce the impact generated in the working process of a clutch and reduce the working noise and the abrasion of a friction plate. The technical scheme is as follows:

a hydraulic clutch control system comprises a two-position two-way reversing valve, a buffer valve group and an oil cylinder,

an oil inlet of the hydraulic control system is communicated with a P oil port of the two-position two-way reversing valve and an oil inlet of the buffer valve group, an oil port A of the two-position two-way reversing valve is communicated with a rodless cavity of the oil cylinder, a T oil port of the two-position two-way reversing valve is communicated with an oil return point of the hydraulic control system and an oil outlet of the buffer valve group,

the buffer valve group comprises a cartridge valve, a first overflow valve, a second overflow valve, a third overflow valve, a first electromagnetic ball valve and a second electromagnetic ball valve, an oil inlet of the cartridge valve is communicated with an oil inlet point of the hydraulic clutch control system, a control oil port of the cartridge valve is communicated with the oil inlet of the cartridge valve, an oil outlet of the cartridge valve is communicated with a T oil port of the two-position two-way reversing valve,

the oil inlet of the first overflow valve, the oil inlet of the second overflow valve and the oil inlet of the third overflow valve are communicated with the oil inlet of the cartridge valve, the oil outlet of the first overflow valve is communicated with the oil inlet of the first electromagnetic ball valve, the oil outlet of the second overflow valve and the oil outlet of the first electromagnetic ball valve are communicated with the oil inlet of the second electromagnetic ball valve, the oil outlet of the second electromagnetic ball valve is communicated with the oil outlet of the third overflow valve, the oil outlet of the third overflow valve is communicated with the T oil port of the two-position two-way reversing valve,

the set pressure of the first overflow valve is smaller than the force for pushing the piston rod of the oil cylinder, the set pressure of the second overflow valve is larger than the force for pushing the piston rod of the oil cylinder, the set pressure of the second overflow valve is smaller than the force required when the piston rod of the oil cylinder extends completely, and the set pressure of the third overflow valve is equal to the force required when the piston rod of the oil cylinder extends completely.

Optionally, the hydraulic clutch control system further includes a first pressure switch, the first pressure switch is disposed between the oil port a of the two-position two-way directional valve and the rodless cavity of the oil cylinder, and a critical pressure of the first pressure switch is equal to a set pressure of the third overflow valve.

Optionally, the hydraulic clutch control system further includes a second pressure switch, the second pressure switch is communicated with an oil inlet point of the hydraulic control system, and a critical pressure of the second pressure switch is smaller than a set pressure of the first overflow valve.

Optionally, the hydraulic clutch control system further includes a controller, and the controller is configured to control operating states of the first electromagnetic ball valve, the second electromagnetic ball valve, and the two-position two-way directional valve.

Optionally, the hydraulic clutch control system further comprises a pressure gauge, and the pressure gauge is communicated with the oil inlet point of the hydraulic control system.

Optionally, the hydraulic clutch control system further includes a filter, and the filter is disposed between an oil inlet of the hydraulic control system and an oil inlet of the cartridge valve.

Optionally, the hydraulic clutch control system further includes a first one-way valve, an oil inlet of the first one-way valve is communicated with an oil outlet of the filter, and an oil outlet of the first one-way valve is communicated with an oil inlet of the cartridge valve.

Optionally, the hydraulic clutch control system further includes a second check valve, an oil inlet of the second check valve is communicated with the T oil port of the two-position two-way reversing valve, and an oil outlet of the second check valve is communicated with an oil return point of the hydraulic control system.

Optionally, a first throttle hole is arranged between the oil inlet of the cartridge valve and the control oil port of the cartridge valve.

Optionally, a second throttle hole is arranged between the oil outlet of the cartridge valve and the T oil port of the two-position two-way reversing valve.

The technical scheme provided by the embodiment of the invention has the following beneficial effects: when the clutch is in a separation state, the two-position two-way reversing valve in the hydraulic clutch control system is in a left position, and no oil flows into a rodless cavity of the oil cylinder. And meanwhile, when the clutch is in a separation state, the first electromagnetic ball valve and the second electromagnetic ball valve in the buffer valve group are both controlled to be in an electrified state, oil passages from oil outlets of the first electromagnetic ball valve and the second electromagnetic ball valve to an oil tank are both communicated, and the first overflow valve is in a working state. When the clutch needs to be changed from a separation state to a closing state, the two-position two-way reversing valve is switched to the right position, the PA oil path of the two-position two-way reversing valve is communicated, oil entering from an oil inlet point can enter a rodless cavity of the oil cylinder from the PA oil path, the first overflow valve is in a working state at the moment, the pressure of the oil entering from the oil inlet point is equal to the pressure of an oil inlet and the pressure of an oil outlet of the cartridge valve are equal to the set pressure of the first overflow valve, and a piston rod of the. And then controlling the first electromagnetic ball valve to lose power, closing the first electromagnetic ball valve, not operating the first overflow valve, still electrifying the second electromagnetic ball valve at the moment, enabling the second overflow valve to be in an operating state, enabling the pressure of oil entering an oil inlet point to be equal to the pressure of an oil inlet and an oil outlet of the cartridge valve to be equal to the set pressure of the second overflow valve, enabling the oil entering the oil inlet point to enter a rodless cavity of the oil cylinder at the moment, pushing a piston rod to extend out, but not completely pushing the piston rod of the oil cylinder out, and enabling the clutch to be in a semi-closed. After the clutch is in a semi-closed state, the second electromagnetic ball valve is controlled to lose power, the second overflow valve does not work, the pressure of oil entering from an oil inlet point is equal to the pressure of an oil inlet and an oil outlet of the cartridge valve and equal to the set pressure of the third overflow valve, and the oil entering from the oil inlet point completely pushes the piston rod out of the oil cylinder, so that the clutch is completely closed. In the arrangement, the clutch is not completely closed at one time, but enters a half-closed state firstly and then enters a completely closed state, buffering exists when the clutch is closed, and impact, working noise and abrasion of the friction plate generated in the working process of the clutch are small.

Drawings

Fig. 1 is a schematic diagram of a hydraulic clutch control system according to an embodiment of the present invention.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Fig. 1 is a schematic diagram of a hydraulic clutch control system according to an embodiment of the present invention, and as shown in fig. 1, the hydraulic clutch control system includes a two-position two-way directional valve 1, a cushion valve group 2, and an oil cylinder 3.

An oil inlet point H of the hydraulic control system is communicated with an oil port P of the two-position two-way reversing valve 1 and an oil inlet of the buffer valve group 2, an oil port A of the two-position two-way reversing valve 1 is communicated with a rodless cavity of the oil cylinder 3, and an oil port T of the two-position two-way reversing valve 1 is communicated with an oil return point E of the hydraulic control system and an oil outlet of the buffer valve group 2.

The cushion valve group 2 comprises a cartridge valve 201, a first overflow valve 202, a second overflow valve 203, a third overflow valve 204, a first electromagnetic ball valve 205 and a second electromagnetic ball valve 206, an oil inlet of the cartridge valve 201 is communicated with an oil inlet point H of the hydraulic clutch control system, a control oil port of the cartridge valve 201 is communicated with an oil inlet of the cartridge valve 201, and an oil outlet of the cartridge valve 201 is communicated with a T oil port of the two-position two-way reversing valve 1.

An oil inlet of the first overflow valve 202, an oil inlet of the second overflow valve 203 and an oil inlet of the third overflow valve 204 are communicated with an oil inlet of the cartridge valve 201, an oil outlet of the first overflow valve 202 is communicated with an oil inlet of the first electromagnetic ball valve 205, an oil outlet of the second overflow valve 203 and an oil outlet of the first electromagnetic ball valve 205 are communicated with an oil inlet of the second electromagnetic ball valve 206, an oil outlet of the second electromagnetic ball valve 206 is communicated with an oil outlet of the third overflow valve 204, and an oil outlet of the third overflow valve 204 is communicated with a T oil port of the two-position two-way reversing valve 1.

The set pressure of the first overflow valve 202 is smaller than the force required for pushing the piston rod 31 of the oil cylinder 3, the set pressure of the second overflow valve 203 is larger than the force required for pushing the piston rod 31 of the oil cylinder 3, the set pressure of the second overflow valve 203 is smaller than the force required for pushing the piston rod 31 of the oil cylinder 3 to be fully extended, and the set pressure of the third overflow valve 204 is equal to the force required for pushing the piston rod 31 of the oil cylinder 3 to be fully extended.

When the clutch is in a separation state, the two-position two-way reversing valve 1 in the hydraulic clutch control system is in a left position, and no oil flows into a rodless cavity of the oil cylinder 3. Meanwhile, when the clutch is in a separation state, the first electromagnetic ball valve 205 and the second electromagnetic ball valve 206 in the cushion valve group 2 are both controlled to be in an electrified state, oil passages from oil outlets of the first electromagnetic ball valve 205 and the second electromagnetic ball valve 206 to an oil tank are both communicated, and the first overflow valve 202 is in a working state. When the clutch needs to be changed from a separation state to a closing state, the two-position two-way reversing valve 1 is switched to the right position, the PA oil path of the two-position two-way reversing valve 1 is communicated, oil entering from the oil inlet point H can enter the rodless cavity of the oil cylinder 3 from the PA oil path, at the moment, the first overflow valve 202 is in a working state, the pressure of the oil entering from the oil inlet point H is equal to the pressure of the oil inlet and the pressure of the oil outlet of the cartridge valve 201 are equal to the set pressure of the first overflow valve 202, and the piston rod 31 of the oil. And then controlling the first electromagnetic ball valve 205 to lose power, closing the first electromagnetic ball valve 205, not operating the first overflow valve 202, still electrifying the second electromagnetic ball valve 206 at the moment, enabling the second overflow valve 203 to be in an operating state, enabling the pressure of oil entering the oil inlet point H to be equal to the pressure of an oil inlet and an oil outlet of the cartridge valve 201 to be equal to the set pressure of the second overflow valve 203, enabling the oil entering the oil inlet point H to enter a rodless cavity of the oil cylinder 3 at the moment, pushing the piston rod 31 to extend out, but not completely pushing out the piston rod 31 of the oil cylinder 3, and enabling the clutch to be in a semi-closed state. After the clutch is in a semi-closed state, the second electromagnetic ball valve 206 is controlled to lose power, the second overflow valve 203 does not work, the pressure of oil entering from an oil inlet point H is equal to the pressure of an oil inlet and an oil outlet of the cartridge valve 201 is equal to the set pressure of the third overflow valve 204, and then the piston rod 31 is completely pushed out of the oil cylinder 3, so that the clutch is completely closed. In the arrangement, the clutch is not completely closed at one time, but enters a half-closed state firstly and then enters a completely closed state, buffering exists when the clutch is closed, and impact, working noise and abrasion of the friction plate generated in the working process of the clutch are small.

It should be noted that, when the clutch needs to be in the disengaged state, the two-position two-way directional valve 1 in the hydraulic clutch control system is in the left position, the AT oil passage of the two-position two-way directional valve 1 is communicated, the spring 32 force of the spring 32 in the rod chamber of the oil cylinder 3 retracts the piston rod 31 of the oil cylinder 3, and the oil in the rodless chamber of the oil cylinder 3 enters the oil return point E of the hydraulic clutch control system through the AT oil passage for oil return.

As shown in fig. 1, the hydraulic clutch control system may further include a first pressure switch 207, the first pressure switch 207 is disposed between the port a of the two-position two-way selector valve 1 and the rodless cavity of the cylinder 3, and a critical pressure of the first pressure switch 207 is equal to a set pressure of the third relief valve 204.

The first pressure switch 207 can be used for monitoring the oil pressure at the rodless cavity of the oil cylinder 3, and particularly when the clutch is in a closed state, if the oil pressure at the rodless cavity is smaller than the critical pressure of the first pressure switch 207, the first pressure switch 207 can send out an alarm signal to remind a worker to check the working state of the clutch, so that the use safety of the clutch can be improved.

Optionally, the hydraulic clutch control system may further include a second pressure switch 208, the second pressure switch 208 being in communication with the oil feed point H of the hydraulic control system, the threshold pressure of the second pressure switch 208 being less than the set pressure of the first spill valve 202.

If the oil pressure at the oil inlet point H is smaller than the critical pressure of the second pressure switch 208, the second pressure switch 208 can send out an alarm signal, and a worker can control the clutch to enter a separation state under the reminding of the second pressure switch 208, so that the working efficiency of the clutch is improved.

Optionally, an oil measuring point C may be provided at the oil return point E.

When the first pressure switch 207 has a problem, the oil pressure can be detected through the oil detection point C, and the safety factor of the hydraulic clutch control system is improved.

As shown in fig. 1, the hydraulic clutch control system may further include a controller 209, and the controller 209 is configured to control the operating states of the first electromagnetic ball valve 205, the second electromagnetic ball valve 206, and the two-position two-way selector valve 1.

The controller 209 can improve the automation degree of the clutch operation and reduce the workload of workers.

For example, the controller 209 may control the first electromagnetic ball valve 205 to be de-energized for 2 seconds, and then control the second electromagnetic ball valve 206 to be de-energized.

After the first electromagnetic ball valve 205 loses power for 2 seconds, the clutch is already stabilized in a semi-closed state, and then the second electromagnetic ball valve 206 is controlled to lose power, so that the problem that the clutch is damaged due to the fact that the second electromagnetic ball valve 206 is switched when the clutch is not stabilized is solved.

As shown in fig. 1, the hydraulic clutch control system further includes a pressure gauge 210, and the pressure gauge 210 is communicated with an oil inlet point H of the hydraulic control system.

The pressure gauge 210 is convenient for directly observing the pressure of the oil liquid, and the safety factor of the hydraulic clutch control system is improved.

Optionally, an oil measuring point C can be arranged at the oil inlet point H.

When the second pressure switch 208 and the pressure gauge 210 have problems, the oil pressure can be detected through the oil detection point C, and the safety factor of the hydraulic clutch control system is improved.

For example, the hydraulic clutch control system may further include a filter 211, and the filter 211 is disposed between the oil inlet point H of the hydraulic control system and the oil inlet of the cartridge valve 201.

The filter 211 can prevent impurities from entering the cushion valve group 2 and the oil cylinder 3, and ensure the stable operation of the clutch.

Optionally, the hydraulic clutch control system may further include a first one-way valve 212, an oil inlet of the first one-way valve 212 is communicated with an oil outlet of the filter 211, and an oil outlet of the first one-way valve 212 is communicated with an oil inlet of the cartridge valve 201.

The first check valve 212 can prevent the backflow of oil, and the safety of the hydraulic clutch control system is improved.

As shown in fig. 1, the hydraulic clutch control system may further include a second check valve 213, an oil inlet of the second check valve 213 is communicated with the T oil port of the two-position two-way selector valve 1, and an oil outlet of the second check valve 213 is communicated with an oil return point E of the hydraulic control system.

Optionally, a first orifice 214 is provided between the oil inlet of the cartridge valve 201 and the control oil port of the cartridge valve 201.

The first throttling hole 214 can play a role in throttling and draining, and the stable work of the cartridge valve 201 is ensured.

For example, a second throttle hole 215 may be provided between the oil outlet of the cartridge valve 201 and the T port of the two-position, two-way directional valve 1.

The second throttling hole 215 can play a role in buffering, so that the oil cylinder 3 is prevented from being impacted by large oil, and the use stability of the hydraulic clutch control system is improved.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.