CN212272674U - Double-valve-core full-hydraulic-control integrated pumping reversing system - Google Patents
Double-valve-core full-hydraulic-control integrated pumping reversing system Download PDFInfo
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- CN212272674U CN212272674U CN202020248881.XU CN202020248881U CN212272674U CN 212272674 U CN212272674 U CN 212272674U CN 202020248881 U CN202020248881 U CN 202020248881U CN 212272674 U CN212272674 U CN 212272674U
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Abstract
The utility model discloses a full hydraulic control integrated form pumping switching-over system of double-valve core, including first hydro-cylinder, second hydro-cylinder, its characterized in that, pumping switching-over system still includes first pumping switching-over valve, second pumping switching-over valve, first cartridge valve, second cartridge valve, first hydraulic control switching-over valve, second hydraulic control switching-over valve, swing valve, left side distribution valve actuating cylinder, right side distribution valve actuating cylinder. The utility model discloses a double-valve-core full hydraulic control integrated pumping reversing system and method, the main reversing valve is a double slide valve core, namely, both ends of the first pumping reversing valve are provided with springs, but do not participate in frequent reversing in work, and the service life of the springs is long; two ends of a second pumping reversing valve which participates in frequent reversing in work are not provided with springs; the utility model discloses a control signal valve is first cartridge valve, second cartridge valve and the first liquid accuse switching-over valve and the second liquid accuse check valve that do not have the spring band location, guarantees that the swing valve both ends have stable control pressure, makes the swing energy switching-over target in place, and the signal detection of being convenient for improves failure diagnosis efficiency.
Description
Technical Field
The utility model relates to a full hydraulically controlled integrated form pumping switching-over system of double-valve core belongs to hydraulic pressure switching-over technical field.
Background
The concrete pump truck has the advantages that the working environment is severe, the working conditions are complex and changeable, when the concrete pump truck works normally, the hydraulic pump is always in a high-pressure and high-flow state, double cylinders are frequently reversed, a hydraulic system is prone to failure, all elements of the hydraulic system work in a closed oil way, when the hydraulic system fails, the failure parts and the root causes are often not easy to find out immediately, the overhaul period is long, and therefore serious economic loss is caused, and therefore when the hydraulic system is designed, how to reduce the failure rate of the hydraulic elements is achieved, and the failure diagnosis efficiency is improved, and the concrete.
In the reversing moment of the prior art, the spring is compressed and reset instantly, so that the two ends of the pendulum valve only have control pressure in the reversing moment, the pendulum valve cannot be ensured to be replaced in place in a short time, and a control oil pressure signal cannot be detected.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the technical problem that overcome prior art's defect, provide a double-valve-element full hydraulic control integrated form pumping switching-over system, through development design hydraulic system, provide reliable switching-over signal to convenient and fast when detecting it, thereby reduce the fault rate of concrete pumping system, improve maintenance efficiency, shorten the failure diagnosis time, thereby realize the economic value of practicing thrift the cost.
In order to solve the technical problem, the utility model provides a full hydraulic control integrated form pumping switching-over system of double-valve core, including first hydro-cylinder, second hydro-cylinder, its characterized in that, the pumping switching-over system still includes first pumping switching-over valve, second pumping switching-over valve, first inserted valve, second inserted valve, first hydraulic control switching-over valve, second hydraulic control switching-over valve, swing valve, left side distributing valve actuating cylinder, right side distributing valve actuating cylinder;
the first pumping reversing valve is connected with the second pumping reversing valve, the second pumping reversing valve is respectively connected with a rodless cavity of the first oil cylinder and a rodless cavity of the second oil cylinder, a rod cavity of the first oil cylinder is connected with the first hydraulic control reversing valve through the first cartridge valve, a rod cavity of the second oil cylinder is connected with the first hydraulic control reversing valve through the second cartridge valve, the first hydraulic control reversing valve is connected with the second hydraulic control reversing valve, the second hydraulic control reversing valve is connected with the swing valve, the swing valve is respectively connected with the left distribution valve driving oil cylinder and the right distribution valve driving oil cylinder, and the second pumping reversing valve is connected with the swing valve; and the rod cavity of the first oil cylinder is connected with the rod cavity of the second oil cylinder.
In a preferred embodiment, the first pumping direction-changing valve has springs at two ends of a valve core, and the second pumping direction-changing valve has no springs at two ends of a valve core.
As a preferred embodiment, a fifth control oil port and a sixth control oil port are formed in the rod cavity side of the first oil cylinder, and the fifth control oil port and the sixth control oil port are respectively connected with the oil ports at the two ends of the first cartridge valve; a seventh control oil port and an eighth control oil port are formed in the rod cavity side of the second oil cylinder and are respectively connected with the oil ports at the two ends of the second cartridge valve.
As a preferred embodiment, the second pumping reversing valve is provided with a third control oil port and a fourth control oil port, and the third control oil port and the fourth control oil port are respectively connected with the swing valve.
As a preferred embodiment, the first pumping reversing valve is respectively provided with a first control oil port and a second control oil port, the first control oil port and the second control oil port are respectively externally connected with the high-pressure control oil, the first hydraulic control check valve is respectively provided with a ninth control oil port and a tenth control oil port, and the ninth control oil port and the tenth control oil port are respectively externally connected with the high-pressure control oil.
As a preferred embodiment, the pumping reversing system further comprises: assuming that the first control port P11 and the ninth control port (P71) are high-pressure control oil, the first pumping reversing valve 1 and the first hydraulic control reversing valve 7 are in a left-position connection state, high-pressure pumping oil input from the port P1 enters through a rodless cavity of the first oil cylinder 3, a piston rod of the first oil cylinder 3 extends out, when a piston of the first oil cylinder 3 moves to the position of the sixth control port P32, the sixth control port P32 outputs high-pressure signal oil, the high-pressure signal oil flows to the first cartridge valve 5, the hydraulic pressure of a fifth control port P31 at the upper end of the sixth control port P32 and the spring force of the first cartridge valve 5 are overcome, the first cartridge valve 5 is opened, the high-pressure signal oil output from the sixth control port P32 acts on the left end of the second hydraulic control reversing valve 8 through the first hydraulic control reversing valve 7, the second hydraulic control reversing valve 8 is in a left-position connection state, the high-pressure oil input from the port P2 of the second hydraulic control reversing valve 8 acts on the right end of the swing valve 9, the swing valve 9 is connected at the right position, high-pressure oil input from a port P3 of the swing valve 9 enters a large cavity end of a right distribution valve driving oil cylinder 11 through the swing valve 9 to push a piston rod of the right distribution valve driving oil cylinder 11 to extend, meanwhile, the high-pressure oil input from a port P3 acts on the right end of a second pumping reversing valve 2 to push a valve core of the second pumping reversing valve 2 to move leftwards, so that a piston of a first oil cylinder 3 retracts, the hydraulic pressure of a fifth control oil port P31 is not less than the hydraulic pressure of a sixth control oil port P32, the first cartridge valve 5 is closed, high-pressure signal oil output from the sixth control oil port P32 is stopped at the first cartridge valve 5, the left end control oil pressure of the second hydraulic reversing valve 8 is 0, and because springs are not arranged at two ends of the first hydraulic reversing valve 7 and the second hydraulic reversing valve 8 and a positioning device is arranged, the high-pressure oil input from a port P2 can still act on the right end of the swing valve 9 through the second, when the piston rod of the right distribution valve driving oil cylinder 11 is completely extended, the second pumping reversing valve 2 is switched on at the right position, the pumped high-pressure oil input from the port P1 enters the rodless cavity end of the second oil cylinder 4 through the first pumping reversing valve 1 and the second pumping reversing valve 2 to push the piston rod of the second oil cylinder 4 to extend, and the whole reversing process is completed.
As a preferred embodiment, the pumping reversing system further comprises: when the piston of the second oil cylinder 4 moves to an eighth control oil port P42, the eighth control oil port P42 outputs high-pressure signal oil, the high-pressure signal oil acts on the right end of the second hydraulic control reversing valve 8 through the second cartridge valve 6 and the first hydraulic control reversing valve 7 to reverse the direction of the second hydraulic control reversing valve 8 and is switched on at the right position, the high-pressure oil input from the port P2 enters the left end of the swing valve 9 through the second hydraulic control reversing valve 8 to push the spool of the swing valve 9 to move rightwards, the high-pressure oil input from the port P3 acts on the large cavity end of the left distribution valve driving oil cylinder 10 through the swing valve 9 to push the piston rod to extend, meanwhile, the high-pressure oil input from the port P1 acts on the third control oil port P21 on the left side of the second pumping reversing valve 2 to switch on the left position, the high-pressure oil input from the port P1 enters the rodless cavity end of the first oil cylinder 3 through the first pumping reversing valve 1 and the second pumping valve 2, the commutation process is completed.
The utility model discloses the beneficial effect who reaches: firstly, the main reversing valve of the utility model is a double slide valve core, namely, two ends of the first pumping reversing valve are provided with springs, but the springs do not participate in frequent reversing in work, and the service life of the springs is long; two ends of a second pumping reversing valve which participates in frequent reversing in work are not provided with springs; secondly, the control signal valves of the utility model are a first cartridge valve, a second cartridge valve, a first hydraulic control reversing valve and a second hydraulic control one-way valve which are positioned without spring bands, so that stable control pressure is ensured at two ends of the swing valve, the swing valve can be reversed in place, signal detection is convenient, and the failure diagnosis efficiency is improved; thirdly, the main reversing valve block of the utility model is integrated with the signal valve, thereby reducing the number of hydraulic elements, reducing pipelines and saving space; fourth, the utility model discloses a complete liquid accuse integrated form pumping switching-over system of double-valve core and method provides reliable switching-over signal on the whole to convenient and fast when detecting it, thereby reduce the fault rate of concrete pumping system, improve maintenance efficiency, shorten failure diagnosis time, thereby realize the economic value of saving the cost.
Drawings
Fig. 1 is a schematic diagram of the oil circuit connection principle of the preferred embodiment of the present invention.
The meanings of the symbols in the figures: 1-a first pumping reversing valve, 2-a second pumping reversing valve, 3-a first oil cylinder, 4-a second oil cylinder, 5-a first cartridge valve, 6-a second cartridge valve, 7-a first hydraulic control reversing valve, 8-a second hydraulic control reversing valve, 9-a swing valve, 10-a left side distributing valve driving oil cylinder, 11-a right side distributing valve driving oil cylinder, P11-a first control oil port, P12-a second control oil port, P21-a third control oil port, P22-a fourth control oil port, P31-a fifth control oil port, P32-a sixth control oil port, P41-a seventh control oil port, P42-an eighth control oil port, P71-a ninth control oil port and P72-a tenth control oil port.
Detailed Description
The present invention will be further described with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and the protection scope of the present invention is not limited thereby.
As shown in fig. 1, the utility model provides a double-valve-core full hydraulic control integrated pumping reversing system, including a first oil cylinder 3, a second oil cylinder 4, the pumping reversing system further includes a first pumping reversing valve 1, a second pumping reversing valve 2, a first cartridge valve 5, a second cartridge valve 6, a first hydraulic control reversing valve 7, a second hydraulic control reversing valve 8, a swing valve 9, a left side distribution valve driving oil cylinder 10, a right side distribution valve driving oil cylinder 11; the first pumping reversing valve 1 is connected with the second pumping reversing valve 2, the second pumping reversing valve 2 is respectively connected with a rodless cavity of the first oil cylinder 3 and a rodless cavity of the second oil cylinder 4, a rod cavity of the first oil cylinder 3 is connected with the first hydraulic control reversing valve 7 through the first cartridge valve 5, a rod cavity of the second oil cylinder 4 is connected with the first hydraulic control reversing valve 7 through the second cartridge valve 6, the first hydraulic control reversing valve 7 is connected with the second hydraulic control reversing valve 8, the second hydraulic control reversing valve 8 is connected with the swing valve 9, the swing valve 9 is respectively connected with the left distribution valve driving oil cylinder 10 and the right distribution valve driving oil cylinder 11, and the second pumping reversing valve 2 is connected with the swing valve 9; the rod cavity of the first oil cylinder 3 is connected with the rod cavity of the second oil cylinder 4.
In a preferred embodiment, the first pumping direction-changing valve 1 has springs at two ends of a valve core, and the second pumping direction-changing valve 2 has no springs at two ends of a valve core.
As a preferred embodiment, a fifth control port P31 and a sixth control port P32 are opened at the rod cavity side of the first oil cylinder 3, and the fifth control port P31 and the sixth control port P32 are respectively connected to ports at two ends of the first cartridge valve 5; a seventh control oil port P41 and an eighth control oil port P42 are formed in the rod cavity side of the second oil cylinder 4, and the seventh control oil port P41 and the eighth control oil port P42 are respectively connected with oil ports at two ends of the second cartridge valve 6.
As a preferred embodiment, the second pumping direction valve 2 is provided with a third control port P21 and a fourth control port P22, and the third control port P21 and the fourth control port P22 are respectively connected to the swing valve 9.
As a preferred embodiment, the first pumping direction valve 1 is provided with a first control port P11 and a second control port P12, the first control port P11 and the second control port P12 are respectively externally connected with high-pressure control oil, the first pilot operated check valve 7 is provided with a ninth control port P71 and a tenth control port P72, and the ninth control port P71 and the tenth control port P72 are respectively externally connected with high-pressure control oil.
As a preferred embodiment, the pumping reversing system further comprises: assuming that the first control port P11 and the ninth control port (P71) are high-pressure control oil, the first pumping directional control valve 1 and the first hydraulic directional control valve 7 are in a left-position connection state, oil is fed into a rodless cavity of the first oil cylinder 3, a piston rod of the first oil cylinder 3 extends out, when a piston of the first oil cylinder 3 moves to the sixth control port P32, the sixth control port P32 outputs high-pressure signal oil, the high-pressure signal oil flows to the first cartridge valve 5, the hydraulic pressure of a fifth control port P31 at the upper end of the sixth control port P32 and the spring force of the first cartridge valve 5 are overcome, the first cartridge valve 5 is opened, the high-pressure signal oil output from the sixth control port P32 acts on the left end of the second hydraulic directional control valve 8 through the first hydraulic directional control valve 7, the second hydraulic directional control valve 8 is connected in a left position, the high-pressure signal oil input from the P2 of the second hydraulic directional control valve 8 acts on the right end of the swing valve 9 through the second hydraulic directional control valve, the swing valve 9 is connected at the right position, high-pressure oil input from a port P3 of the swing valve 9 enters a large cavity end of a right distribution valve driving oil cylinder 11 through the swing valve 9 to push a piston rod of the right distribution valve driving oil cylinder 11 to extend, meanwhile, the high-pressure oil input from a port P3 acts on the right end of a second pumping reversing valve 2 to push a valve core of the second pumping reversing valve 2 to move leftwards, so that a piston of a first oil cylinder 3 retracts, the hydraulic pressure of a fifth control oil port P31 is not less than the hydraulic pressure of a sixth control oil port P32, the first cartridge valve 5 is closed, high-pressure signal oil output from the sixth control oil port P32 is stopped at the first cartridge valve 5, the left end control oil pressure of the second hydraulic reversing valve 8 is 0, and because springs are not arranged at two ends of the first hydraulic reversing valve 7 and the second hydraulic reversing valve 8 and a positioning device is arranged, the high-pressure oil input from a port P2 can still act on the right end of the swing valve 9 through the second, when the piston rod of the right distribution valve driving oil cylinder 11 is completely extended, the second pumping reversing valve 2 is switched on at the right position, the pumped high-pressure oil input from the port P1 enters the rodless cavity end of the second oil cylinder 4 through the first pumping reversing valve 1 and the second pumping reversing valve 2 to push the piston rod of the second oil cylinder 4 to extend, and the whole reversing process is completed.
As a preferred embodiment, the pumping reversing system further comprises: when the piston of the second oil cylinder 4 moves to an eighth control oil port P42, the eighth control oil port P42 outputs high-pressure signal oil, the high-pressure signal oil acts on the right end of the second hydraulic control reversing valve 8 through the second cartridge valve 6 and the first hydraulic control reversing valve 7 to reverse the direction of the second hydraulic control reversing valve 8 and is switched on at the right position, the high-pressure oil input from the port P2 enters the left end of the swing valve 9 through the second hydraulic control reversing valve 8 to push the spool of the swing valve 9 to move rightwards, the high-pressure oil input from the port P3 acts on the large cavity end of the left distribution valve driving oil cylinder 10 through the swing valve 9 to push the piston rod to extend, meanwhile, the high-pressure oil input from the port P1 acts on the third control oil port P21 on the left side of the second pumping reversing valve 2 to switch on the left position, the high-pressure oil input from the port P1 enters the rodless cavity end of the first oil cylinder 3 through the first pumping reversing valve 1 and the second pumping valve 2, the commutation process is completed.
The utility model also provides a full liquid accuse integrated form pumping switching-over method of double-valve core, a serial communication port, including following step: sequentially reversing; and reversing in a reverse order.
As a preferred embodiment, the sequential commutation step specifically includes: assuming that the first control port P11 and the ninth control port (P71) are high-pressure control oil, the first pumping reversing valve 1 and the first hydraulic control reversing valve 7 are in a left-position connection state, high-pressure pumping oil input from the port P1 enters through a rodless cavity of the first oil cylinder 3, a piston rod of the first oil cylinder 3 extends out, when a piston of the first oil cylinder 3 moves to the position of the sixth control port P32, the sixth control port P32 outputs high-pressure signal oil, the high-pressure signal oil flows to the first cartridge valve 5, the hydraulic pressure of a fifth control port P31 at the upper end of the sixth control port P32 and the spring force of the first cartridge valve 5 are overcome, the first cartridge valve 5 is opened, the high-pressure signal oil output from the sixth control port P32 acts on the left end of the second hydraulic control reversing valve 8 through the first hydraulic control reversing valve 7, the second hydraulic control reversing valve 8 is in a left-position connection state, the high-pressure oil input from the port P2 of the second hydraulic control reversing valve 8 acts on the right end of the swing valve 9, the swing valve 9 is connected at the right position, high-pressure oil input from a port P3 of the swing valve 9 enters a large cavity end of a right distribution valve driving oil cylinder 11 through the swing valve 9 to push a piston rod of the right distribution valve driving oil cylinder 11 to extend, meanwhile, the high-pressure oil input from a port P3 acts on the right end of a second pumping reversing valve 2 to push a valve core of the second pumping reversing valve 2 to move leftwards, so that a piston of a first oil cylinder 3 retracts, the hydraulic pressure of a fifth control oil port P31 is not less than the hydraulic pressure of a sixth control oil port P32, the first cartridge valve 5 is closed, high-pressure signal oil output from the sixth control oil port P32 is stopped at the first cartridge valve 5, the left end control oil pressure of the second hydraulic reversing valve 8 is 0, and because springs are not arranged at two ends of the first hydraulic reversing valve 7 and the second hydraulic reversing valve 8 and a positioning device is arranged, the high-pressure oil input from a port P2 can still act on the right end of the swing valve 9 through the second, when the piston rod of the right distribution valve driving oil cylinder 11 is completely extended, the second pumping reversing valve 2 is switched on at the right position, the pumped high-pressure oil input from the port P1 enters the rodless cavity end of the second oil cylinder 4 through the first pumping reversing valve 1 and the second pumping reversing valve 2 to push the piston rod of the second oil cylinder 4 to extend, and the whole reversing process is completed.
As a preferred embodiment, the reverse sequence reversing step specifically includes: when the piston of the second oil cylinder 4 moves to an eighth control oil port P42, the eighth control oil port P42 outputs high-pressure signal oil, the high-pressure signal oil acts on the right end of the second hydraulic control reversing valve 8 through the second cartridge valve 6 and the first hydraulic control reversing valve 7 to reverse the direction of the second hydraulic control reversing valve 8 and is switched on at the right position, the high-pressure oil input from the port P2 enters the left end of the swing valve 9 through the second hydraulic control reversing valve 8 to push the spool of the swing valve 9 to move rightwards, the high-pressure oil input from the port P3 acts on the large cavity end of the left distribution valve driving oil cylinder 10 through the swing valve 9 to push the piston rod to extend, meanwhile, the high-pressure oil input from the port P1 acts on the third control oil port P21 on the left side of the second pumping reversing valve 2 to switch on the left position, the high-pressure oil input from the port P1 enters the rodless cavity end of the first oil cylinder 3 through the first pumping reversing valve 1 and the second pumping valve 2, the commutation process is completed.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be considered as the protection scope of the present invention.
Claims (7)
1. A double-spool full-hydraulic control integrated pumping reversing system comprises a first oil cylinder (3) and a second oil cylinder (4), and is characterized by further comprising a first pumping reversing valve (1), a second pumping reversing valve (2), a first cartridge valve (5), a second cartridge valve (6), a first hydraulic control reversing valve (7), a second hydraulic control reversing valve (8), a swing valve (9), a left distribution valve driving oil cylinder (10) and a right distribution valve driving oil cylinder (11);
the first pumping reversing valve (1) is connected with the second pumping reversing valve (2), the second pumping reversing valve (2) is respectively connected with the rodless cavity of the first oil cylinder (3) and the rodless cavity of the second oil cylinder (4), the rod cavity of the first oil cylinder (3) is connected with the first hydraulic control reversing valve (7) through the first cartridge valve (5), the rod cavity of the second oil cylinder (4) is connected with the first hydraulic control reversing valve (7) through the second cartridge valve (6), the first hydraulic control reversing valve (7) is connected with the second hydraulic control reversing valve (8), the second hydraulic control reversing valve (8) is connected with the swing valve (9), the swing valve (9) is respectively connected with the left distribution valve driving oil cylinder (10) and the right distribution valve driving oil cylinder (11), the second pumping reversing valve (2) is connected with the oscillating valve (9); and the rod cavity of the first oil cylinder (3) is connected with the rod cavity of the second oil cylinder (4).
2. The dual-spool full hydraulic control integrated pumping reversing system according to claim 1, wherein springs are arranged at two ends of the spool of the first pumping reversing valve (1), and springs are not arranged at two ends of the spool of the second pumping reversing valve (2).
3. The dual-spool full hydraulic control integrated pumping reversing system according to claim 1, wherein a fifth control oil port (P31) and a sixth control oil port (P32) are formed in a rod cavity side of the first oil cylinder (3), and the fifth control oil port (P31) and the sixth control oil port (P32) are respectively connected with oil ports at two ends of the first cartridge valve (5); a seventh control oil port (P41) and an eighth control oil port (P42) are formed in the side of a rod cavity of the second oil cylinder (4), and the seventh control oil port (P41) and the eighth control oil port (P42) are respectively connected with oil ports at two ends of the second cartridge valve (6).
4. The dual-spool full hydraulic control integrated pumping reversing system according to claim 3, wherein a third control oil port (P21) and a fourth control oil port (P22) are respectively formed in the second pumping reversing valve (2), and the third control oil port (P21) and the fourth control oil port (P22) are respectively connected with the swing valve (9).
5. The double-valve-core full hydraulic control integrated pumping reversing system according to claim 4, wherein the first pumping reversing valve (1) is provided with a first control oil port (P11) and a second control oil port (P12), the first control oil port (P11) and the second control oil port (P12) are respectively externally connected with high-pressure control oil, the first hydraulic control reversing valve (7) is provided with a ninth control oil port (P71) and a tenth control oil port (P72), and the ninth control oil port (P71) and the tenth control oil port (P72) are respectively externally connected with high-pressure control oil.
6. The dual spool, full hydraulic control integrated pumping reversing system of claim 5, further comprising: the first pumping reversing valve (1) is communicated at a left position, a rodless cavity of the first oil cylinder (3) is filled with oil, a piston rod of the first oil cylinder (3) extends out, when a piston of the first oil cylinder (3) moves to a sixth control oil port (P32), the sixth control oil port (P32) outputs high-pressure signal oil which acts on the left end of the second hydraulic control reversing valve (8) through the first cartridge valve (5) and the first hydraulic control reversing valve (7) to enable the second hydraulic control reversing valve (8) to be communicated at the left position, high-pressure oil input by the second hydraulic control reversing valve (8) acts on the right end of the swing valve (9), the swing valve (9) is communicated at a right position, the high-pressure oil input by the swing valve (9) enters a large cavity end of the right distribution valve driving oil cylinder (11) to push the right distribution valve to drive the piston rod of the oil cylinder (11) to extend out, and the high-pressure oil input by the swing valve (9) simultaneously acts on the right end of the, the valve core of the second pumping reversing valve (2) is pushed to move leftwards, so that the piston of the first oil cylinder (3) retracts, the first cartridge valve (5) is closed, the oil pressure is controlled to be 0 at the left end of the second hydraulic control reversing valve (8), when the piston rod of the right distribution valve driving oil cylinder (11) completely extends out, the second pumping reversing valve (2) is connected at the right position, high-pressure oil pumped enters the rodless cavity end of the second oil cylinder (4) through the first pumping reversing valve (1) and the second pumping reversing valve (2), the piston rod of the second oil cylinder (4) is pushed to extend out, and the whole reversing process is completed.
7. The dual spool, full hydraulic control integrated pumping reversing system of claim 5, further comprising: when the piston of the second oil cylinder (4) moves to an eighth control oil port (P42), the eighth control oil port (P42) outputs high-pressure signal oil, the high-pressure signal oil acts on the right end of the second hydraulic control reversing valve (8) through the second cartridge valve (6) and the first hydraulic control reversing valve (7) to reverse the second hydraulic control reversing valve (8) and is communicated at the right position, the high-pressure oil enters the left end of the swing valve (9) through the second hydraulic control reversing valve (8), the swing valve (9) is communicated at the left position, the high-pressure oil input from the P3 port acts on the large cavity end of the left distribution valve driving oil cylinder (10) through the swing valve (9) to push the piston rod to extend out, meanwhile, the high-pressure signal oil acts on a third control oil port (P21) on the left side of the second pumping reversing valve (2) to enable the second pumping reversing valve (2) to be communicated at the left position, and the high-pressure oil enters the rodless cavity end of the first oil cylinder (3) through the first reversing valve (1, the piston rod of the first oil cylinder (3) is pushed to extend out, and the reversing process is completed.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020248881.XU CN212272674U (en) | 2020-03-04 | 2020-03-04 | Double-valve-core full-hydraulic-control integrated pumping reversing system |
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| CN202020248881.XU CN212272674U (en) | 2020-03-04 | 2020-03-04 | Double-valve-core full-hydraulic-control integrated pumping reversing system |
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| CN212272674U true CN212272674U (en) | 2021-01-01 |
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| CN202020248881.XU Active CN212272674U (en) | 2020-03-04 | 2020-03-04 | Double-valve-core full-hydraulic-control integrated pumping reversing system |
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