Pressure-reducing and speed-reducing buffer loop of oil cylinder

Abstract

The utility model discloses a pressure reducing and speed reducing buffer loop of an oil cylinder, which comprises a first electromagnetic directional valve, a pressure reducing valve, a first overflow valve, a two-way cartridge valve, a throttle valve and a second electromagnetic directional valve, the first electromagnetic directional valve is connected with the pressure reducing valve, the pressure reducing valve is connected with the first overflow valve, the two-way cartridge valve is connected with the second electromagnetic directional valve, and the throttle valve is connected with the second electromagnetic directional valve. The throttle valve is connected with the two-way cartridge valve, the two-way cartridge valve is communicated with a rodless cavity of the oil cylinder, and the throttle valve is communicated with the rodless cavity of the oil cylinder. On the premise that a proportional reversing valve is not used, the stretching speed of the oil cylinder is regulated and controlled, the cost is low, the control mode is simpler, and pressure reduction and speed reduction of the oil cylinder can be achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of oil cylinders, in particular to a decompression and deceleration buffer circuit of an oil cylinder. Background Art

[0002] The cylinder is a hydraulic actuator that converts hydraulic energy into mechanical energy and performs linear reciprocating motion. The cylinder is generally composed of a cylinder barrel, a cylinder head, a piston, a piston rod, a sealing device and other components. During the telescopic movement of the cylinder, due to the continuous change of the load, the cylinder will be subjected to a large impact when the piston rod is fully extended. In the prior art, a proportional electromagnetic reversing valve is usually used to control the speed of the cylinder to reduce the impact of the impact. However, the proportional control circuit has strict requirements on the use environment and has high requirements on the cleanliness of the oil. For application scenarios that do not require precise control, using a proportional electromagnetic reversing valve to improve the impact of the impact will increase the cost too much. Utility Model Content

[0003] The technical problem to be solved by the utility model is that the solution of using a proportional reversing valve to improve the impact at the end of the oil cylinder in the prior art has the technical problem of high cost.

[0004] To this end, the utility model provides a decompression and deceleration buffer circuit of an oil cylinder, which can control the extension speed of the oil cylinder without using a proportional reversing valve, and has lower cost.

[0005] The technical solution adopted by the utility model to solve its technical problems is: a pressure reducing and decelerating buffer circuit of an oil cylinder, comprising: a first electromagnetic reversing valve, a pressure reducing valve, a first overflow valve, a two-way cartridge valve, a throttle valve and a second electromagnetic reversing valve, the first electromagnetic reversing valve is connected to the pressure reducing valve, the pressure reducing valve is connected to the first overflow valve, the two-way cartridge valve is connected to the second electromagnetic reversing valve, the throttle valve is connected to the two-way cartridge valve, the two-way cartridge valve is connected to the rodless chamber of the oil cylinder, and the throttle valve is connected to the rodless chamber of the oil cylinder.

[0006] Furthermore, it also includes: a third electromagnetic reversing valve and a second overflow valve, the third electromagnetic reversing valve is connected to the pressure reducing valve, and the second overflow valve is connected to the third electromagnetic reversing valve.

[0007] Furthermore, it also includes: a one-way valve, the oil inlet of the one-way valve is connected to the rodless chamber of the oil cylinder, and the oil outlet of the one-way valve is connected to the oil outlet of the hydraulic pump.

[0008] Furthermore, the pilot port of the pressure reducing valve is communicated with the first relief valve.

[0009] Further, the A port of the two-way cartridge valve is communicated with the rodless chamber of the oil cylinder, and the B port of the two-way cartridge valve is communicated with the throttle valve.

[0010] Furthermore, it also includes: a ball valve, which is used to control the connection between the oil leakage path and the oil tank.

[0011] Furthermore, it also includes: a first pressure measuring joint, wherein the first pressure measuring joint is connected to the pressure reducing valve.

[0012] Furthermore, it also includes: a second pressure measuring joint, wherein the second pressure measuring joint is connected to the first overflow valve.

[0013] Furthermore, it also includes a valve block, in which the pressure reducing valve, the first relief valve, the two-way cartridge valve, and the throttle valve are all installed, and the first electromagnetic reversing valve and the second electromagnetic reversing valve are installed on the valve block.

[0014] Furthermore, the valve block is provided with an oil inlet A1, an oil outlet B1 and an oil return port Y1, the oil inlet A1 is communicated with the pressure reducing valve, the oil outlet B1 is communicated with the rodless chamber of the oil cylinder, and the oil return port Y1 is communicated with the oil tank.

[0015] The beneficial effects of the utility model are:

[0016] When the oil cylinder starts to work, the first solenoid reversing valve is energized, causing the pressure reducing valve to release oil through the first relief valve. At this time, the maximum pressure of the oil cylinder is the sum of the pressure setting value of the pressure reducing valve and the pressure setting value of the first relief valve. At this time, the second solenoid reversing valve is energized, causing the two-way cartridge valve to open, and hydraulic oil can enter the oil cylinder at a larger flow rate.

[0017] When the oil cylinder no longer needs a large pressure to push the piston rod, the first electromagnetic reversing valve loses power, and the pressure reducing valve leaks oil through the first electromagnetic reversing valve. At this time, the maximum pressure of the oil cylinder is the pressure setting value of the pressure reducing valve.

[0018] When the oil cylinder is about to be fully extended, the second solenoid reversing valve loses power, causing the two-way cartridge valve to close. At this time, the hydraulic oil only enters the oil cylinder through the throttle valve, and the speed of the oil cylinder is reduced, achieving deceleration buffering.

[0019] The utility model realizes the regulation of the extension speed of the oil cylinder without using a proportional reversing valve, has low cost, and a simpler control method, and can realize the decompression and deceleration of the oil cylinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The utility model is further described below in conjunction with the accompanying drawings and embodiments.

[0021] Figure 1 It is a structural schematic diagram of the first embodiment of the utility model.

[0022] Figure 2 It is a schematic diagram of the working state of the oil cylinder and the jacking actuator of the utility model.

[0023] Figure 3 It is a structural schematic diagram of the second embodiment of the utility model.

[0024] In the figure: 1. first solenoid reversing valve; 2. pressure reducing valve; 3. first overflow valve; 4. two-way cartridge valve; 5. throttle valve; 6. second solenoid reversing valve; 7. third solenoid reversing valve; 8. second overflow valve; 9. check valve; 10. ball valve; 11. first pressure measuring joint; 12. second pressure measuring joint; 13. valve block. DETAILED DESCRIPTION

[0025] Now the utility model is further described in detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, which only illustrate the basic structure of the utility model in a schematic manner, and therefore only show the components related to the utility model.

[0026] In the description of the present utility model, it is necessary to understand that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present utility model. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.

[0027] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0028] Embodiment 1

[0029] like Figure 1As shown, the pressure reducing and decelerating buffer circuit of the oil cylinder of this embodiment comprises: a first solenoid reversing valve 1, a pressure reducing valve 2, a first overflow valve 3, a two-way cartridge valve 4, a throttle valve 5 and a second solenoid reversing valve 6. The first solenoid reversing valve 1 is connected to the pressure reducing valve 2, the pressure reducing valve 2 is connected to the first overflow valve 3, the two-way cartridge valve 4 is connected to the second solenoid reversing valve 6, the throttle valve 5 is connected to the two-way cartridge valve 4, the two-way cartridge valve 4 is connected to the rodless chamber of the oil cylinder, and the throttle valve 5 is connected to the rodless chamber of the oil cylinder.

[0030] When the oil cylinder starts to work, the first electromagnetic reversing valve 1 is energized, causing the pressure reducing valve 2 to release oil through the first relief valve 3. At this time, the maximum pressure of the oil cylinder is the sum of the pressure setting value of the pressure reducing valve 2 and the pressure setting value of the first relief valve 3. At this time, the second electromagnetic reversing valve 6 is energized, causing the two-way cartridge valve 4 to open, and the hydraulic oil can enter the oil cylinder at a larger flow rate.

[0031] When the oil cylinder no longer needs a large pressure to push the piston rod, the first electromagnetic reversing valve 1 loses power, and the pressure reducing valve 2 leaks oil through the first electromagnetic reversing valve 1. At this time, the maximum pressure of the oil cylinder is the pressure setting value of the pressure reducing valve 2.

[0032] When the oil cylinder is about to be fully extended, the second electromagnetic reversing valve 6 loses power, causing the two-way cartridge valve 4 to close. At this time, the hydraulic oil enters the oil cylinder only through the throttle valve 5, and the speed of the oil cylinder is reduced, achieving deceleration buffering.

[0033] This embodiment achieves the regulation of the extension speed of the oil cylinder without using a proportional reversing valve, has low cost, and a simpler control method, and can achieve the decompression and deceleration of the oil cylinder.

[0034] Specifically, the decompression and deceleration buffer circuit also includes a one-way valve 9, the oil inlet of the one-way valve 9 is connected to the rodless chamber of the oil cylinder, and the oil outlet of the one-way valve 9 is connected to the oil outlet of the hydraulic pump. The pilot port of the pressure reducing valve 2 is connected to the first overflow valve 3. The pilot port of the pressure reducing valve 2 is connected to the first electromagnetic reversing valve 1. The A port of the two-way cartridge valve 4 is connected to the rodless chamber of the oil cylinder, and the B port of the two-way cartridge valve 4 is connected to the throttle valve 5.

[0035] It should be noted that the pressure reducing and decelerating buffer circuit also includes: a valve block 13, a pressure reducing valve 2, a first relief valve 3, a two-way cartridge valve 4, and a throttle valve 5 are all installed in the valve block 13, and a first electromagnetic reversing valve 1 and a second electromagnetic reversing valve 6 are installed on the valve block 13. The valve block 13 is provided with an oil inlet A1, an oil outlet B1, and an oil return port Y1. The oil inlet A1 is connected to the pressure reducing valve 2, the oil outlet B1 is connected to the rodless chamber of the oil cylinder, and the oil return port Y1 is connected to the oil tank. The valve block 13 is installed on the oil cylinder.

[0036] The oil outlet of the hydraulic pump is connected to the oil inlet A1, and the hydraulic oil can flow to the rodless chamber of the oil cylinder through the pressure reducing valve 2 and the two-way cartridge valve 4 to push the piston rod to move. The first overflow valve 3 is connected to the oil return port Y1. The P port of the second electromagnetic reversing valve 6 is connected to the pressure reducing valve 2, and the A port of the second electromagnetic reversing valve 6 is connected to the upper chamber of the two-way cartridge valve 4. When the upper chamber of the two-way cartridge valve 4 is filled with oil, the two-way cartridge valve 4 is closed, and when the upper chamber of the two-way cartridge valve 4 is not filled with oil, the two-way cartridge valve 4 is opened. The T port of the second electromagnetic reversing valve 6 is connected to the oil return port Y1.

[0037] When the first electromagnetic reversing valve 1 is energized, the pilot port of the pressure reducing valve 2 is not connected to the P port of the first electromagnetic reversing valve 1, and the A port of the first electromagnetic reversing valve 1 is connected to the oil return port Y1. At this time, the pressure reducing valve 2 leaks oil through the first relief valve 3. When the first electromagnetic reversing valve 1 loses power, the pilot port of the pressure reducing valve 2 is connected to the P port of the first electromagnetic reversing valve 1, and the pressure reducing valve 2 leaks oil through the first electromagnetic reversing valve 1.

[0038] When the second electromagnetic reversing valve 6 is energized, the upper chamber of the two-way cartridge valve 4 is connected to the oil return port Y1, and the two-way cartridge valve 4 is opened. When the second electromagnetic reversing valve 6 is de-energized, the upper chamber of the two-way cartridge valve 4 is connected to the hydraulic oil, and the two-way cartridge valve 4 is closed.

[0039] For example, the decompression and deceleration buffer circuit also includes: a ball valve 10, which is used to control the connection and disconnection between the oil leakage path and the oil tank. The ball valve 10 is installed at the oil return port Y1. When the circuit needs to be inspected and maintained, the oil leakage path can be closed by the ball valve 10.

[0040] For example, the pressure reducing and decelerating buffer circuit further includes: a first pressure measuring joint 11 and a second pressure measuring joint 12, wherein the first pressure measuring joint 11 is connected to the pressure reducing valve 2, and the second pressure measuring joint 12 is connected to the first relief valve 3. The pressure value of the pressure reducing valve 2 and the pressure value of the first relief valve 3 can be set according to the actual working conditions, for example, the pressure value of the pressure reducing valve 2 is set to 100 bar, and the pressure value of the first relief valve 3 is set to 200 bar. During the setting process, the first pressure measuring joint 11 and the second pressure measuring joint 12 can be used to judge whether the pressure reducing valve 2 and the first relief valve 3 have reached the set value.

[0041] Working principle:

[0042] like Figure 2 As shown, taking the actuator as a lifting action as an example, from left to right, the angle of the actuator opening becomes larger and larger until it is fully opened at 90°. During the whole process, the force of the actuator on the cylinder is gradually reduced, and when it is fully opened, the force on the cylinder is reduced to zero. The pressure setting value of the pressure reducing valve 4 is 100 bar, and the pressure setting value of the first relief valve 3 is 200 bar.

[0043] When the lifting starts, the load on the oil cylinder is the largest, the first electromagnetic reversing valve 1 and the second electromagnetic reversing valve 6 are energized, the pilot port of the pressure reducing valve 4 is drained through the first relief valve 3, and the maximum pressure of the oil cylinder is 300 bar. The upper chamber of the two-way cartridge valve 4 is connected to the oil return port Y1, and the two-way cartridge valve 4 is opened. At this time, the hydraulic oil can enter the rodless chamber of the oil cylinder at the maximum flow rate.

[0044] When the actuator opening angle reaches 60°, the piston rod of the oil cylinder no longer needs a large pressure to push, the first solenoid reversing valve 1 loses power, the pilot port of the pressure reducing valve 2 leaks oil through the first solenoid reversing valve 1, and the maximum pressure of the oil cylinder is reduced to 100 bar.

[0045] When the opening angle of the actuator reaches 85°, the second electromagnetic reversing valve 6 loses power, the upper chamber of the two-way cartridge valve 4 is connected to the hydraulic oil, and the two-way cartridge valve 4 is closed. At this time, the hydraulic oil only enters the rodless chamber of the cylinder through the throttle valve 5, and the extension speed of the cylinder is reduced.

[0046] As a result, during the opening process of the actuator, pressure reduction is achieved; when the actuator is about to be fully opened, deceleration is achieved, thereby reducing impact and being beneficial to protecting equipment.

[0047] Embodiment 2

[0048] like Figure 3 As shown, the difference between the second embodiment and the first embodiment is that a third electromagnetic reversing valve 7 and a second relief valve 8 are added, the third electromagnetic reversing valve 7 is connected to the pressure reducing valve 2, and the second relief valve 8 is connected to the third electromagnetic reversing valve 7. By adding the third electromagnetic reversing valve 7 and the second relief valve 8, multi-level pressure selection of the circuit can be achieved. In practical applications, the number of the third electromagnetic reversing valve 7 and the second relief valve 8 can be one or more, and can be set according to the pressure selected according to actual needs.

[0049] For example, the P port of the third electromagnetic reversing valve 7 is connected to the first port of the pressure reducing valve 2 , the T port of the third electromagnetic reversing valve 7 is connected to the oil return port Y1 , and the B port of the third electromagnetic reversing valve 7 is connected to the third overflow valve 8 .

[0050] Working principle:

[0051] For example, the pressure value of the third electromagnetic reversing valve 7 is set to 100 bar.

[0052] When both the first electromagnetic reversing valve 1 and the third electromagnetic reversing valve 7 lose power, the pilot port of the pressure reducing valve 2 leaks oil through the first electromagnetic reversing valve 1. At this time, the maximum pressure of the oil cylinder is 100 bar (the pressure setting value of the pressure reducing valve 2 itself).

[0053] When the first electromagnetic reversing valve 1 is energized and the third electromagnetic reversing valve 7 is de-energized, the pilot port of the pressure reducing valve 2 leaks oil through the first relief valve 3. At this time, the maximum pressure of the oil cylinder is 100 bar + 200 bar = 300 bar.

[0054] When the first electromagnetic reversing valve 1 and the third electromagnetic reversing valve 7 are both energized, the pressure reducing valve 2 leaks oil through the first relief valve 3 and the third relief valve 8. At this time, the maximum pressure of the oil cylinder is 100 bar+100 bar=200 bar.

[0055] In this way, multi-level pressure selection of the circuit can be achieved.

[0056] In summary, the decompression and deceleration buffer circuit of the oil cylinder of the utility model uses low-cost components to achieve decompression and deceleration of the oil cylinder, reduces the impact force at the end of the oil cylinder, and is conducive to improving the service life of the equipment. Through structural improvement, multi-level pressure selection can be achieved to cope with more working conditions.

[0057] Based on the above ideal embodiments of the utility model, the relevant staff can make various changes and modifications without departing from the technical concept of the utility model through the above description. The technical scope of the utility model is not limited to the content of the specification, and its technical scope must be determined according to the scope of the claims.

Claims

1. A decompression and deceleration buffer circuit of an oil cylinder, characterized in that: include: A first electromagnetic reversing valve (1), a pressure reducing valve (2), a first overflow valve (3), a two-way cartridge valve (4), a throttle valve (5) and a second electromagnetic reversing valve (6), wherein the first electromagnetic reversing valve (1) is connected to the pressure reducing valve (2), the pressure reducing valve (2) is connected to the first overflow valve (3), the two-way cartridge valve (4) is connected to the second electromagnetic reversing valve (6), the throttle valve (5) is connected to the two-way cartridge valve (4), the two-way cartridge valve (4) is in communication with a rodless chamber of an oil cylinder, and the throttle valve (5) is in communication with the rodless chamber of the oil cylinder.

2. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: Also includes: A third electromagnetic reversing valve (7) and a second overflow valve (8), wherein the third electromagnetic reversing valve (7) is connected to the pressure reducing valve (2), and the second overflow valve (8) is connected to the third electromagnetic reversing valve (7).

3. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: Also includes: A one-way valve (9), wherein an oil inlet of the one-way valve (9) is communicated with the rodless chamber of the oil cylinder, and an oil outlet of the one-way valve (9) is communicated with the oil outlet of the hydraulic pump.

4. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: The pilot port of the pressure reducing valve (2) is in communication with the first relief valve (3).

5. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: The port A of the two-way cartridge valve (4) is in communication with the rodless chamber of the oil cylinder, and the port B of the two-way cartridge valve (4) is in communication with the throttle valve (5).

6. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: Also includes: A ball valve (10) is used to control the connection and disconnection between the oil leakage path and the oil tank.

7. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: Also includes: A first pressure measuring joint (11), wherein the first pressure measuring joint (11) is connected to the pressure reducing valve (2).

8. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: Also includes: A second pressure measuring joint (12), wherein the second pressure measuring joint (12) is connected to the first overflow valve (3).

9. The decompression and deceleration buffer circuit of the oil cylinder according to claim 1, characterized in that: It also comprises a valve block (13), wherein the pressure reducing valve (2), the first relief valve (3), the two-way cartridge valve (4), and the throttle valve (5) are all installed in the valve block (13), and the first electromagnetic reversing valve (1) and the second electromagnetic reversing valve (6) are installed on the valve block (13).

10. The decompression and deceleration buffer circuit according to claim 9, characterized in that: The valve block (13) is provided with an oil inlet A1, an oil outlet B1 and an oil return port Y1, the oil inlet A1 is connected to the pressure reducing valve (2), the oil outlet B1 is connected to the rodless chamber of the oil cylinder, and the oil return port Y1 is connected to the oil tank.

Images