阅读说明：本技术 液压控制系统 (Hydraulic control system ) 是由 鄢勇 张三喜 洪威 于 2019-08-30 设计创作，主要内容包括：本发明公开了一种液压控制系统,属于液压控制领域。控制马达时,从液压控制系统的进油点输送油液,油液进入限流阀的控制油口控制限流阀换到左位。油液被限流阀限流后再流出限流阀的出油口,限流阀的出油口处的油液压力与液控溢流阀的控制油口处的油液压力相等。若液控溢流阀的设定压力较低,限流阀的出油口处的油液压力小于液控换向阀的控制油口处的压力,液控换向阀不换向,液控换向阀与液控调速阀不通,液控调速阀的阀芯关闭,油液不进入马达。调高液控溢流阀的设定压力,限流阀的出油口处的油液压力大于液控换向阀的控制油口处的压力,液控换向阀换向,油液进入马达。整体通过液压进行控制,没有电火花的问题,提高了船舶航行时的安全性。(The invention discloses a hydraulic control system, and belongs to the field of hydraulic control. When the motor is controlled, oil is conveyed from an oil inlet point of the hydraulic control system, and the oil enters a control oil port of the flow limiting valve to control the flow limiting valve to change to the left position. The oil flows out of the oil outlet of the flow limiting valve after being limited by the flow limiting valve, and the oil pressure at the oil outlet of the flow limiting valve is equal to the oil pressure at the oil outlet of the hydraulic control overflow valve. If the set pressure of the hydraulic control overflow valve is lower, the oil pressure at the oil outlet of the flow limiting valve is lower than the pressure at the oil opening of the hydraulic control reversing valve, the hydraulic control reversing valve does not reverse, the hydraulic control reversing valve is not communicated with the hydraulic control speed regulating valve, the valve core of the hydraulic control speed regulating valve is closed, and oil does not enter the motor. And increasing the set pressure of the hydraulic control overflow valve, wherein the oil pressure at the oil outlet of the flow limiting valve is greater than the pressure at the oil outlet of the hydraulic control reversing valve, the hydraulic control reversing valve reverses, and oil enters the motor. The whole hydraulic control system is controlled through hydraulic pressure, the problem of electric sparks is solved, and the safety of the ship during navigation is improved.)

1. A hydraulic control system is characterized by comprising a flow limiting valve (1), a hydraulic control overflow valve (2), a hydraulic control reversing valve (3), a hydraulic control speed regulating valve (4) and a motor (5),

the oil inlet of the flow limiting valve (1) is communicated with an oil inlet point (H) of the hydraulic control system, the control oil port of the flow limiting valve (1) is communicated with the oil inlet of the flow limiting valve (1), the oil outlet of the flow limiting valve (1) is communicated with the oil inlet of the hydraulic control overflow valve (2), the oil inlet of the hydraulic control overflow valve (2) is communicated with the control oil port of the hydraulic control overflow valve (2), the oil outlet of the hydraulic control overflow valve (2) is communicated with an oil return point (E) of the hydraulic control system,

the oil outlet of the flow limiting valve (1) is also communicated with a P oil port of the hydraulic control reversing valve (3), a control oil port of the hydraulic control reversing valve (3) is communicated with the P oil port of the hydraulic control reversing valve (3), an A oil port of the hydraulic control reversing valve (3) is communicated with a control oil port (4a) of the hydraulic control speed regulating valve (4), a T oil port of the hydraulic control reversing valve (3) is communicated with an oil return point (E) of the hydraulic control system,

the oil pressure of the oil port A of the hydraulic control reversing valve (3) is used for controlling the opening and closing of the oil way of the hydraulic control speed regulating valve (4), the oil inlet (4b) of the hydraulic control speed regulating valve (4) is communicated with the oil inlet point (H) of the hydraulic control system, the oil outlet (4c) of the hydraulic control speed regulating valve (4) is communicated with the oil inlet of the motor (5), and the oil return port of the motor (5) is communicated with the oil return point (E) of the hydraulic control system.

2. The hydraulic control system of claim 1, further comprising a heating element (6), the heating element (6) being configured to heat oil in the hydraulic control system.

3. The hydraulic control system according to claim 2, wherein the heating element (6) comprises a normally closed stop valve (61) and a heating block (62), the normally closed stop valve (61) and the heating block (62) are both arranged on a connecting pipeline (7) communicating an oil inlet point (H) of the hydraulic control system with an oil return point (E) of the hydraulic control system, and a plurality of damping holes are arranged on the heating block (62).

4. The hydraulic control system according to claim 3, wherein a thickness (D) of the heating block (62) in an axial direction of the connecting pipe (7) is 10 to 20 cm.

5. The hydraulic control system according to claim 3, characterized in that one side of the heating block (62) is provided with an oil measuring point (C).

6. The hydraulic control system according to any one of claims 1-5, further comprising a filter (8), wherein the filter (8) is arranged between an oil inlet point (H) of the hydraulic control system and an oil inlet of the flow restriction valve (1).

7. The hydraulic control system according to claim 6, further comprising a first normally open stop valve (9), the first normally open stop valve (9) being arranged between an oil feed point (H) of the hydraulic control system and the filter (8).

8. The hydraulic control system according to any one of claims 1 to 5, further comprising a second normally open stop valve (10), wherein the second normally open stop valve (10) is arranged between an oil inlet point (H) of the hydraulic control system and the hydraulic control speed regulating valve (4).

9. The hydraulic control system according to any one of claims 1-5, characterized in that the hydraulic control system further comprises a first check valve (11), an oil inlet of the first check valve (11) is communicated with an oil outlet of the hydraulic control overflow valve (2), and an oil outlet of the first check valve (11) is communicated with an oil return point (E) of the hydraulic control system.

10. The hydraulic control system according to any one of claims 1-5, characterized in that the hydraulic control system further comprises a second check valve (12), an oil inlet of the second check valve (12) is communicated with an oil outlet of the motor (5), and an oil outlet of the second check valve (12) is communicated with an oil return point (E) of the hydraulic control system.

Technical Field

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

Background

Ships are very common water transport vehicles, and some of the ships are used for transporting crude oil or chemicals, which are required to ensure a very high explosion-proof level.

Therefore, if the motor structure exists on the ship, the electromagnetic valve and the proportional valve in the hydraulic system for controlling the motor are usually replaced by the explosion-proof electromagnetic valve and the explosion-proof proportional valve, so as to ensure the explosion-proof grade of the ship and improve the safety of the ship during navigation.

However, the explosion-proof electromagnetic valve and the explosion-proof proportional valve still have the possibility of generating electric sparks in the use process, and the safety of the ship during navigation cannot be guaranteed to the maximum extent.

Disclosure of Invention

The embodiment of the invention provides a hydraulic control system which can improve the safety of a ship during navigation.

The technical scheme is as follows:

a hydraulic control system comprises a flow limiting valve, a hydraulic control overflow valve, a hydraulic control reversing valve, a hydraulic control speed regulating valve and a motor,

the oil inlet of the flow limiting valve is communicated with the oil inlet point of the hydraulic control system, the control oil port of the flow limiting valve is communicated with the oil inlet of the flow limiting valve, the oil outlet of the flow limiting valve is communicated with the oil inlet of the hydraulic control overflow valve, the oil inlet of the hydraulic control overflow valve is communicated with the control oil port of the hydraulic control overflow valve, the oil outlet of the hydraulic control overflow valve is communicated with the oil return point of the hydraulic control system,

the oil outlet of the flow limiting valve is also communicated with a P oil port of the hydraulic control reversing valve, a control oil port of the hydraulic control reversing valve is communicated with the P oil port of the hydraulic control reversing valve, an A oil port of the hydraulic control reversing valve is communicated with a control oil port of the hydraulic control speed regulating valve, a T oil port of the hydraulic control reversing valve is communicated with an oil return point of the hydraulic control system,

the oil pressure of the oil port A of the hydraulic control reversing valve is used for controlling the opening and closing of an oil way of the hydraulic control speed regulating valve, the oil inlet of the hydraulic control speed regulating valve is communicated with the oil inlet point of the hydraulic control system, the oil outlet of the hydraulic control speed regulating valve is communicated with the oil inlet of the motor, and the oil return port of the motor is communicated with the oil return point of the hydraulic control system.

Optionally, the hydraulic control system further comprises a heating element for heating oil in the hydraulic control system.

Optionally, the heating element includes normally closed stop valve and heating block, the normally closed stop valve with the heating block all sets up the intercommunication hydraulic control system's oil feed point with on the connecting tube between hydraulic control system's the oil return point, be provided with a plurality of damping holes on the heating block.

Optionally, the thickness of the heating block in the axial direction of the connecting pipeline is 10-20 cm.

Optionally, one side of the heating block is provided with an oil measuring point.

Optionally, the hydraulic control system further comprises a filter, and the filter is arranged between an oil inlet of the hydraulic control system and an oil inlet of the flow limiting valve.

Optionally, the hydraulic control system further comprises a first normally open stop valve, and the first normally open stop valve is arranged between the oil inlet point of the hydraulic control system and the filter.

Optionally, the hydraulic control system further comprises a second normally open stop valve, and the second normally open stop valve is arranged between the oil inlet point of the hydraulic control system and the hydraulic control speed regulating valve.

Optionally, the hydraulic control system further includes a first check valve, an oil inlet of the first check valve is communicated with an oil outlet of the hydraulic control overflow valve, and an oil outlet of the first check valve is communicated with an oil return point of the hydraulic control system.

Optionally, the hydraulic control system further includes a second check valve, an oil inlet of the second check valve is communicated with an oil outlet of the motor, and an oil outlet of the second check valve is communicated with an oil return point of the hydraulic control system.

The technical scheme provided by the embodiment of the invention has the following beneficial effects: when the motor is controlled, oil is conveyed from an oil inlet point of the hydraulic control system, and the oil enters a control oil port of the flow limiting valve to control the flow limiting valve to change to the left position. The oil flows out of the oil outlet of the flow limiting valve after being limited by the flow limiting valve, and the oil pressure at the oil outlet of the flow limiting valve is equal to the oil pressure at the oil outlet of the hydraulic control overflow valve. If the set pressure of the hydraulic control overflow valve is lower, the oil pressure at the oil outlet of the flow limiting valve is lower than the pressure at the oil opening of the hydraulic control reversing valve, at the moment, the hydraulic control reversing valve does not reverse, the oil path between the hydraulic control reversing valve and the hydraulic control speed regulating valve is in a closed state, the valve core of the hydraulic control speed regulating valve is in a closed state, and oil cannot enter the motor through the hydraulic control speed regulating valve. When the motor needs to work, the set pressure of the hydraulic control overflow valve is increased, the oil pressure at the oil outlet of the flow limiting valve is larger than the pressure at the oil outlet of the hydraulic control reversing valve, the hydraulic control reversing valve reverses, the valve core of the hydraulic control speed regulating valve is opened, the oil inlet of the hydraulic control speed regulating valve is communicated with the oil inlet of the hydraulic control system, the oil outlet of the hydraulic control speed regulating valve is communicated with the oil inlet of the motor, oil can enter the hydraulic control speed regulating valve and then enter the motor, finally flows back to the oil outlet, and the motor is controlled to work. The whole control of the motor is controlled through hydraulic pressure, the problem of electric sparks is solved, and the safety of the ship during navigation is improved.

Drawings

FIG. 1 is a schematic diagram of a hydraulic control system for a cylinder according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of a pilot-controlled speed regulating valve provided in the embodiment of the 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 control system of an oil cylinder according to an embodiment of the present invention, and as shown in fig. 1, the hydraulic control system includes a flow limiting valve 1, a hydraulic control overflow valve 2, a hydraulic control directional valve 3, a hydraulic control speed regulating valve 4, and a motor 5.

An oil inlet of the flow limiting valve 1 is communicated with an oil inlet point H of the hydraulic control system, a control oil port of the flow limiting valve 1 is communicated with an oil inlet of the flow limiting valve 1, an oil outlet of the flow limiting valve 1 is communicated with an oil inlet of the hydraulic control overflow valve 2, an oil inlet of the hydraulic control overflow valve 2 is communicated with a control oil port of the hydraulic control overflow valve 2, and an oil outlet of the hydraulic control overflow valve 2 is communicated with an oil return point E of the hydraulic control system.

The oil outlet of the flow limiting valve 1 is also communicated with a P oil port of the hydraulic control reversing valve 3, a control oil port of the hydraulic control reversing valve 3 is communicated with the P oil port of the hydraulic control reversing valve 3, an A oil port of the hydraulic control reversing valve 3 is communicated with a control oil port 4a of the hydraulic control speed regulating valve 4, and a T oil port of the hydraulic control reversing valve 3 is communicated with an oil return point E of a hydraulic control system.

The oil pressure of the oil port A of the hydraulic control reversing valve 3 is used for controlling the opening and closing of an oil way of the hydraulic control speed regulating valve 4, an oil inlet 4b of the hydraulic control speed regulating valve 4 is communicated with an oil inlet point H of the hydraulic control system, an oil outlet 4c of the hydraulic control speed regulating valve 4 is communicated with an oil inlet of the motor 5, and an oil return port of the motor 5 is communicated with an oil return point E of the hydraulic control system.

When the motor 5 is controlled, oil is conveyed from an oil inlet point H of the hydraulic control system, and the oil enters a control oil port of the flow limiting valve 1 to control the flow limiting valve 1 to change to the left position. The oil flows out of the oil outlet of the flow limiting valve 1 after being limited by the flow limiting valve 1, and the oil pressure at the oil outlet of the flow limiting valve 1 is equal to the oil pressure at the control oil port of the hydraulic control overflow valve 2. If the set pressure of the hydraulic control overflow valve 2 is lower, and the oil pressure at the oil outlet of the flow limiting valve 1 is lower than the pressure at the control oil port of the hydraulic control reversing valve 3, the hydraulic control reversing valve 3 does not reverse, the oil path between the hydraulic control reversing valve 3 and the hydraulic control speed regulating valve 4 is in a closed state, the valve core of the hydraulic control speed regulating valve 4 is in a closed state, and oil cannot enter the motor 5 through the hydraulic control speed regulating valve 4. When the motor 5 needs to work, the set pressure of the hydraulic control overflow valve 2 is increased, the oil pressure at the oil outlet of the flow limiting valve 1 is greater than the pressure at the control oil port of the hydraulic control reversing valve 3, the hydraulic control reversing valve 3 reverses, the valve core of the hydraulic control speed regulating valve 4 is opened, the oil inlet 4b of the hydraulic control speed regulating valve 4 is communicated with the oil inlet point H of the hydraulic control system, the oil outlet 4c of the hydraulic control speed regulating valve 4 is communicated with the oil inlet of the motor 5, oil can enter the hydraulic control speed regulating valve 4 and then enter the motor 5, and finally returns to the oil outlet point E, so that the motor 5 is controlled to work. The whole control of the motor 5 is controlled by hydraulic pressure, so that the problem of electric sparks is solved, and the safety of the ship during navigation is improved.

And finally, returning the oil in the hydraulic control system to an oil return point E of the hydraulic control system, and then circulating.

It should be noted that the arrangement of the flow limiting valve 1 can further improve the safety of the hydraulic motor 5, and reduce the impact that the pilot operated directional control valve 3 and the pilot operated relief valve 2 may receive.

Optionally, the oil pressure at the oil outlet of the pilot-operated directional control valve 3 is also used to control the degree of opening of the spool of the pilot-operated speed control valve 4.

At this time, according to the difference of the pressure of the oil at the outlet of the hydraulic control reversing valve 3 (equal to the pressure at the control oil port of the hydraulic control reversing valve 3), the opening degree of the valve core of the hydraulic control speed regulating valve 4 is different, the flow of the oil entering the motor 5 is different, the motor 5 can be controlled to work at different rotating speeds, and the rotating speed of the motor 5 can be conveniently adjusted.

As shown in fig. 1, the hydraulic control system may further include a heating element 6, and the heating element 6 is used to heat oil in the hydraulic control system.

The provision of the heating element 6 can heat oil in the hydraulic control system through the heating element 6 when the ship navigation environment is at a low temperature, so as to ensure the normal work of the hydraulic control system and ensure the normal work of the hydraulic motor 5.

Wherein, heating element 6 can include normally closed stop valve 61 and heating block 62, and normally closed stop valve 61 and heating block 62 all set up on connecting tube 7 between the oil feed point H that communicates hydraulic control system and the oil return point E of hydraulic control system, are provided with a plurality of damping holes on the heating block 62.

In the arrangement, when oil needs to be heated, the normally closed stop valve 61 is opened, the oil can pass through the connecting pipeline 7, and when the oil passes through the damping holes in the heating block 62 in the connecting pipeline 7, friction heat generation is performed to complete heating of the oil. The arrangement is also safe and does not risk electrical sparks.

Illustratively, the thickness D of the heating block 62 in the axial direction of the connecting pipe 7 may be 10 to 20 cm.

When the thickness D of the heating block 62 in the axial direction of the connecting pipe 7 is within the range, the damping hole in the heating block 62 can heat oil well, and the problem of poor heating is avoided.

As shown in fig. 1, one side of the heating block 62 may be provided with an oil measuring point C.

The survey oil point C that one side of heating block 62 set up can detect the condition of fluid heating, avoids fluid heating temperature too high or the condition of crossing excessively to appear.

Further, an oil measuring point C may also be provided on the other side of the heating block 62.

The both sides of heating block 62 all set up survey oil point C, can detect whether there is the change in the temperature of the fluid of zone of heating both sides, detect whether fluid is by normal heating.

As shown in fig. 1, the hydraulic control system may further include a filter 8, and the filter 8 is disposed between an oil inlet point H of the hydraulic control system and an oil inlet of the flow restriction valve 1.

The added filter 8 can improve the use safety of the hydraulic control system and prevent impurities from entering the motor 5 to influence the work of the motor 5.

Wherein, hydraulic control system still can include first normally open stop valve 9, and first normally open stop valve 9 sets up between hydraulic control system's oil feed point H and filter 8.

The first normally open stop valve 9 is arranged to close the first stop valve when the hydraulic control system needs to be maintained or detected, and the filter 8 and elements behind the filter 8 are detected.

Optionally, the hydraulic control system may further include a second normally-open stop valve 10, where the second normally-open stop valve 10 is disposed between the oil inlet point H of the hydraulic control system and the hydraulic control speed regulating valve 4.

The second normally open stop valve 10 is additionally arranged, so that the detection and maintenance of the hydraulic control speed regulating valve 4 are facilitated.

Optionally, the hydraulic control system may further include a first check valve 11, an oil inlet of the first check valve 11 is communicated with an oil outlet of the hydraulic control overflow valve 2, and an oil outlet of the first check valve 11 is communicated with an oil return point E of the hydraulic control system.

The arrangement of the first check valve 11 can prevent the oil from flowing back to the hydraulic control overflow valve 2 from the oil return point E of the hydraulic control system, and the normal work of the hydraulic control system is ensured.

Optionally, the hydraulic control system may further include a second check valve 12, an oil inlet of the second check valve 12 is communicated with an oil outlet of the motor 5, and an oil outlet of the second check valve 12 is communicated with an oil return point E of the hydraulic control system.

The second check valve 12 can prevent oil from flowing back to the motor 5, so that the normal operation of the motor 5 is ensured, and the use safety of the motor 5 is improved.

To facilitate understanding of the present invention, fig. 2 is provided here, and fig. 2 is a schematic structural diagram of a pilot-controlled speed regulating valve according to an embodiment of the present invention, and as shown in fig. 2, the pilot-controlled speed regulating valve 4 may include a valve body 41, a barrel valve sleeve 42, a barrel valve core 43, a control block 44, a spring 45, and a valve cover 46. One end of the valve body 41 is opened with a mounting groove 411, the barrel valve sleeve 42 is inserted in the mounting groove 411, and the opening of the barrel valve sleeve 42 faces one end of the valve body 41. The cylindrical valve core 43 is arranged in the barrel-shaped valve sleeve 42 in a sliding mode, the control block 44 is sealed with the barrel-shaped valve sleeve 42, the control block 44 is arranged at a position spaced from the cylindrical valve core 43, and the control block 44 is located between one end of the valve body 41 and the cylindrical valve core 43. The sliding directions of the control block 44 and the cylindrical spool 43 are both parallel to the length direction of the barrel valve sleeve 42.

A spring 45 is coaxially and fixedly connected in the cylindrical valve core 43, the length of the spring 45 in the axial direction of the cylindrical valve core 43 is larger than that of the cylindrical valve core 43, one end of the spring 45 is abutted against the closed end of the barrel-shaped valve sleeve 42, and the other end of the spring 45 is abutted against the control block 44. The valve cover 46 is provided at one end of the valve body 41, and fixes the barrel valve sleeve 42 to the valve body 41, and the valve cover 46 abuts against one end of the control block 44.

The side wall of the barrel-shaped valve sleeve 42 is provided with a first circulation oil port 421, when no external force acts, the barrel-shaped valve core 43 closes the first circulation oil port 421, the side wall of the valve body 41 is provided with an oil inlet 4b of the hydraulic control speed regulating valve 4, and the first circulation oil port 421 is communicated with the oil inlet 4b of the hydraulic control speed regulating valve 4. The closed end of the barrel-shaped valve sleeve 42 is provided with a second circulation oil port 422, the other end of the valve body 41 is provided with an oil outlet 4c of the hydraulic control speed regulating valve 4, and the second circulation oil port 422 is communicated with the oil outlet 4c of the hydraulic control speed regulating valve 4. The valve cover 46 is provided with a control oil port 4a of the pilot-controlled speed control valve 4. The hydraulic control speed regulating valve 4 shown in fig. 2 is in a working state, when the hydraulic control speed regulating valve 4 works, oil flowing out from the oil outlet 4c of the hydraulic control reversing valve 3 enters the control oil port 4a of the hydraulic control speed regulating valve 4, the oil entering the control oil port 4a pushes the control block 44 to move towards the closed end of the barrel-shaped valve sleeve 42, the control block 44 compresses the spring 45, the barrel-shaped valve core 43 moves towards the closed end of the barrel-shaped valve sleeve 42 along with the spring 45, the barrel-shaped valve core 43 does not close the first circulation oil port 421 any more, and the hydraulic control speed regulating valve 4 is turned. The oil from the oil inlet 4b of the pilot-controlled speed control valve 4 flows through the first circulation oil port 421, the gap G between the control block 44 and the cylindrical valve core 43 in sequence, then flows through the inside of the cylindrical valve core 43 to enter the second circulation oil port 422 of the barrel-shaped valve sleeve 42, and finally flows out through the oil outlet 4c of the pilot-controlled speed control valve 4.

When the hydraulic pressure applied to the control block 44 is different, the control block 44 can push the spring 45 to have different lengths from the spool, and the gap G between the control block 44 and the cylindrical spool 43 has different sizes, so that the function of adjusting the flow rate of the outlet oil of the hydraulic control speed regulating valve 4 is achieved. The valve structure can conveniently realize the functions of hydraulic control and speed regulation at the same time.

When the pilot operated speed control valve 4 is in a non-working state, the control block 44 is pushed by the spring 45, the control block 44 is located at the opening end of the barrel-shaped valve sleeve 42, the barrel-shaped valve core 43 moves to a position where the first flow oil port 421 is closed along with the spring 45, and no oil flows in the pilot operated speed control valve 4.

In other embodiments provided by the present invention, the hydraulic control speed regulating valve 4 may also be configured such that a spring and a stopper are added at the oil inlet of the speed regulating valve, and in a normal state, the spring pushes the stopper to block the oil inlet of the speed regulating valve. The oil from the hydraulic control reversing valve 3 exerts an acting force opposite to the spring on the stop block to push the stop block to open the oil inlet of the speed regulating valve, and the speed regulating valve is conducted. Oil can enter the motor 5 from the hydraulic control reversing valve 3 to push the motor 5 to work. The structure of the pilot-operated speed regulating valve 4 is not limited in the invention.

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.