Hydraulic control sequential action hydraulic system

Abstract

The utility model provides a hydraulic control sequential action hydraulic system, which comprises an oil source, a hydraulic control system and a hydraulic control system, the first-stage oil cylinder comprises an oil cavity E and an oil cavity F which are separated by a piston rod, the oil cavity F is connected with an A port overflow branch provided with an A port overflow valve, and the A port overflow branch is connected with the oil port A through a Y port pressure relief branch provided with a Y port one-way valve; the secondary oil cylinder comprises an oil cavity G and an oil cavity H which are separated by a piston rod, the oil cavity G is connected with a B port overflow branch provided with a B port overflow valve, and the B port overflow branch is connected with the oil port B through an X port pressure relief branch provided with an X port one-way valve; the A port reversing valve is respectively connected with the oil port A, the oil cavity F, the oil cavity H, the A port overflow branch and the B port overflow branch; and the B port reversing valve is respectively connected with the oil port B, the oil cavity E, the oil cavity G, the A port overflow branch and the B port overflow branch. The hydraulic system can realize sequential action, is not influenced by external factors, is low in failure rate, and can avoid excessive energy consumption of the hydraulic system.

Description

Technical Field

[0001] The utility model relates to the field of sequential action hydraulic systems, in particular to a hydraulically controlled sequential action hydraulic system. Background Art

[0002] Sequential actions between two-stage cylinders are very common on garbage trucks. For example, between the closing cylinder and the locking cylinder of the box door, there is a sequential action of first closing the door and then locking it, or first unlocking and then opening the door.

[0003] At present, the sequential actions between two-stage oil cylinders are mostly realized by the following two methods: one is to control the oil cylinder to perform sequential actions by the corresponding solenoid valve after detection by the proximity switch. However, the proximity switch is easily affected by external factors and malfunctions, with a high failure rate, which can easily lead to disordered action sequences, damage to equipment, or inability to perform actions. In addition, electronic control is required, which is costly. The other is to use a hydraulic one-way sequential valve to use hydraulic pressure to achieve sequential actions. This solution requires adding an overflow valve to the oil circuit of the secondary oil cylinder, so that the hydraulic pressure of the pressure oil needs to be increased to overflow through the overflow valve before it can enter the secondary oil cylinder for the secondary action. However, this will cause the actual pressure of the pressure oil to be much greater than the pressure required for the secondary action, that is, the actual working pressure does not match the action requirement pressure, causing the hydraulic system to heat up and consume a lot of energy. It can be seen that both of the above-mentioned two existing technologies have corresponding technical problems.

[0004] Therefore, the purpose of this invention is to design a hydraulic control sequential action hydraulic system with low failure rate and low energy consumption in response to the problems existing in the above-mentioned prior art. Utility Model Content

[0005] In view of the problems existing in the above-mentioned prior art, the present invention provides a hydraulically controlled sequential action hydraulic system, which can effectively solve the problems existing in the above-mentioned prior art.

[0006] The technical solution of the utility model is:

[0007] A hydraulically controlled sequential action hydraulic system comprising:

[0008] Oil source, including oil port A and oil port B;

[0009] The first-stage oil cylinder includes an oil chamber E and an oil chamber F separated by a piston rod. The oil chamber F is connected to an A-port overflow branch provided with an A-port overflow valve. The A-port overflow branch is connected to the oil port A through a Y-port pressure relief branch provided with a Y-port check valve.

[0010] The secondary oil cylinder includes an oil chamber G and an oil chamber H separated by a piston rod. The oil chamber G is connected to a B-port overflow branch provided with a B-port overflow valve. The B-port overflow branch is connected to the oil port B through an X-port pressure relief branch provided with an X-port check valve.

[0011] The A-port reversing valve is respectively connected to the oil port A, the oil chamber F, the oil chamber H, the A-port overflow branch, and the B-port overflow branch; the A-port reversing valve includes an A-port primary station for connecting the oil port A and the oil chamber F and locking the oil chamber H, and an A-port secondary station for connecting the oil port A and the oil chamber H and locking the oil chamber F;

[0012] The B-port reversing valve is respectively connected to the oil port B, the oil chamber E, the oil chamber G, the A-port overflow branch, and the B-port overflow branch; the B-port reversing valve includes a B-port primary station for connecting the oil port B and the oil chamber E and locking the oil chamber G, and a B-port secondary station for connecting the oil port B and the oil chamber G and locking the oil chamber E;

[0013] The A port overflow branch is used to push the A port reversing valve and the B port reversing valve to the A port secondary station and the B port secondary station after the overflow is connected, and the B port overflow branch is used to push the A port reversing valve and the B port reversing valve to the A port primary station and the B port primary station after the overflow is connected.

[0014] Furthermore, the two ends of the A-port reversing valve include an oil port Y1 and an oil port X1 respectively connected to the A-port overflow branch and the B-port overflow branch, and the two ends of the B-port reversing valve include an oil port Y2 and an oil port X2 respectively connected to the A-port overflow branch and the B-port overflow branch; when the A-port reversing valve and the B-port reversing valve move to the A-port first-level station and the B-port first-level station, the Y-port pressure relief branch is used to relieve pressure on the oil ports Y1 and Y2; when the A-port reversing valve and the B-port reversing valve move to the A-port second-level station and the B-port second-level station, the X-port pressure relief branch is used to relieve pressure on the oil ports X1 and X2.

[0015] Furthermore, the A-port relief valve and the B-port relief valve both include an overflow oil inlet end and an overflow oil outlet end, the Y-port check valve and the X-port check valve both include a one-way oil inlet end and a one-way oil outlet end, the oil chamber F and the oil chamber G are respectively connected to the overflow oil inlet ends of the A-port relief valve and the B-port relief valve, the overflow oil outlet ends of the A-port relief valve and the B-port relief valve are respectively connected to the one-way oil inlet ends of the Y-port check valve and the B-port check valve, the one-way oil outlet ends of the Y-port check valve and the B-port check valve are respectively connected to the oil port A and the oil port B, the Y1 and the oil port Y2 are respectively connected between the overflow oil outlet end of the A-port relief valve and the one-way oil inlet end of the Y-port check valve, and the X1 and the oil port X2 are respectively connected between the overflow oil outlet end of the B-port relief valve and the one-way oil inlet end of the X-port check valve.

[0016] Furthermore, the B-port reversing valve includes an oil port C2, an oil port A2, an oil port B2, and an oil port D2 respectively connected to the oil port B, the oil chamber E, and the oil chamber G, and a locking oil port D2; when the B-port reversing valve is in the B-port first-level position, the oil port A2 is connected to the oil port C2, and the oil port B2 is connected to the oil port D2; when the B-port reversing valve is in the B-port second-level position, the oil port A2 is connected to the oil port D2, and the oil port B2 is connected to the oil port C2.

[0017] Furthermore, the A-port reversing valve includes oil port C1, oil port A1, oil port B1, and oil port D1 respectively connected to the oil port A, oil chamber F, and oil chamber H, and a locking oil port D1; when the A-port reversing valve is in the A-port first-level position, the oil port A1 is connected to the oil port C1, and the oil port B1 is connected to the oil port D1; when the A-port reversing valve is in the A-port second-level position, the oil port A1 is connected to the oil port D1, and the oil port B1 is connected to the oil port C1.

[0018] Furthermore, the oil chamber F and the oil chamber H are both rod chambers, the oil chamber E and the oil chamber G are both rodless chambers, the number of the first-level oil cylinders and the second-level oil cylinders are set to several, the oil chambers F of the several first-level oil cylinders are arranged in parallel, the oil chambers E are arranged in parallel, and the oil chambers G of the second-level oil cylinders are arranged in parallel, the oil chambers H are arranged in parallel.

[0019] Therefore, the present invention provides the following effects and / or advantages:

[0020] 1. By adding overflow branches at ports A and B, after the oil supply circuit supplies the first or second cylinder to actuate, the oil overflowing through the overflow branches at ports A or B can push the A and B reversing valves to switch positions, switching the oil supply circuit to supply the second or first cylinder, thereby achieving sequential actuation between the first and second cylinders. This sequential actuation is unaffected by external factors and has a low failure rate. Furthermore, the oil supply circuit directly supplies oil to the first or second cylinder through the A and B reversing valves. The oil source pressure only needs to provide the pressure required to support the load of the first or second cylinder, eliminating any excess pressure wasted and thus avoiding unnecessary energy consumption in the hydraulic system.

[0021] 2. Through the coordination of oil port Y1, oil port X1, oil port Y2, oil port X2 and the overflow branch of port A, the overflow branch of port B, the pressure relief branch of port Y and the pressure relief branch of port X, the balance and stability of the oil pressure in the hydraulic system can be maintained while pushing the switching position of the reversing valve of port A and the reversing valve of port B.

[0022] 3. When the overflow branch of port A is open, the pressure at the overflow inlet of the overflow valve of port A is greater than the pressure at the overflow outlet. Therefore, the oil pressure at the one-way outlet of the one-way check valve of port Y is greater than the oil pressure at the one-way inlet. Therefore, the one-way valve of port Y will not open to prevent the oil in the overflow branch of port A from being lost directly through the pressure relief branch of port Y. When the overflow branch of port B is open, the pressure at the overflow inlet of the overflow valve of port B is greater than the pressure at the overflow outlet. Therefore, the oil pressure at the one-way outlet of the one-way check valve of port X is greater than the oil pressure at the one-way inlet. Therefore, the one-way valve of port X will not open to prevent the oil in the overflow branch of port B from being lost directly through the pressure relief branch of port X.

[0023] It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are intended to provide further explanation of the invention as claimed. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a structural schematic diagram of the A-port reversing valve and the B-port reversing valve of a hydraulically controlled sequential action hydraulic system when they are in the A-port first-level position and the B-port first-level position.

[0025] Figure 2 This is a structural schematic diagram of the A-port reversing valve and the B-port reversing valve of a hydraulically controlled sequential action hydraulic system when they are in the A-port secondary position and the B-port secondary position. DETAILED DESCRIPTION

[0026] In order to facilitate understanding by those skilled in the art, the structure of the present invention is further described in detail with reference to the following embodiments and accompanying drawings:

[0027] refer to Figure 1-2 , a hydraulically controlled sequential action hydraulic system, comprising:

[0028] Oil source 1, including oil port A and oil port B;

[0029] The first-stage oil cylinder 2 includes an oil chamber E and an oil chamber F separated by a piston rod. The oil chamber F is connected to an A-port overflow branch 3 equipped with an A-port overflow valve 31. The A-port overflow branch 3 is connected to the oil port A through a Y-port pressure relief branch 4 equipped with a Y-port check valve 41.

[0030] The secondary oil cylinder 5 includes an oil chamber G and an oil chamber H separated by a piston rod. The oil chamber G is connected to a B-port overflow branch 6 equipped with a B-port overflow valve 61. The B-port overflow branch 6 is connected to the oil port B via an X-port pressure relief branch 7 equipped with an X-port check valve 71.

[0031] The A-port reversing valve 8 is respectively connected to the oil port A, the oil chamber F, the oil chamber H, the A-port overflow branch 3, and the B-port overflow branch 6; the A-port reversing valve 8 includes an A-port primary station for connecting the oil port A and the oil chamber F and locking the oil chamber H, and an A-port secondary station for connecting the oil port A and the oil chamber H and locking the oil chamber F;

[0032] The B-port reversing valve 9 is respectively connected to the oil port B, the oil chamber E, the oil chamber G, the A-port overflow branch 3, and the B-port overflow branch 6; the B-port reversing valve 9 includes a B-port primary station for connecting the oil port B and the oil chamber E and locking the oil chamber G, and a B-port secondary station for connecting the oil port B and the oil chamber G and locking the oil chamber E;

[0033] The A-port overflow branch 3 is used to push the A-port reversing valve 8 and the B-port reversing valve 9 to move to the A-port secondary station and the B-port secondary station after the overflow is connected, and the B-port overflow branch 6 is used to push the A-port reversing valve 8 and the B-port reversing valve 9 to move to the A-port primary station and the B-port primary station after the overflow is connected.

[0034] The above-described structure, through the addition of the A-port overflow branch 3 and the B-port overflow branch 6, enables the oil supply circuit to supply the first-stage cylinder 2 or the second-stage cylinder 5 for actuation. The oil overflowing through the A-port overflow branch 3 or the B-port overflow branch 6 can drive the A-port reversing valve 8 and the B-port reversing valve 9 to switch positions, causing the oil supply circuit to switch to supplying the second-stage cylinder 5 or the first-stage cylinder 2 for actuation, thereby achieving sequential actuation between the first-stage cylinder 2 and the second-stage cylinder 5. The above-described sequential actuation is not affected by external factors and has a low failure rate. Furthermore, the oil supply circuit directly supplies oil to the first-stage cylinder 2 or the second-stage cylinder 5 through the A-port reversing valve 8 and the B-port reversing valve 9. The oil pressure of the oil source 1 only needs to provide the pressure required by the load of the first-stage cylinder 2 or the second-stage cylinder 5, and no excess pressure is wasted, thereby avoiding unnecessary energy consumption in the hydraulic system.

[0035] Specifically, the two ends of the A-port reversing valve 8 include an oil port Y1 and an oil port X1 respectively connected to the A-port overflow branch 3 and the B-port overflow branch 6, and the two ends of the B-port reversing valve 9 include an oil port Y2 and an oil port X2 respectively connected to the A-port overflow branch 3 and the B-port overflow branch 6; when the A-port reversing valve 8 and the B-port reversing valve 9 move to the A-port first-level station and the B-port first-level station, the Y-port pressure relief branch 4 is used to relieve pressure on the oil ports Y1 and Y2, and when the A-port reversing valve 8 and the B-port reversing valve 9 move to the A-port second-level station and the B-port second-level station, the X-port pressure relief branch 7 is used to relieve pressure on the oil ports X1 and X2. Thus, through the cooperation of oil port Y1, oil port X1, oil port Y2, oil port X2 and A port overflow branch 3, B port overflow branch 6, Y port pressure relief branch 4, X port pressure relief branch 7, the balance and stability of the oil pressure in the hydraulic system can be maintained while pushing the A port reversing valve 8 and the B port reversing valve 9 to switch positions.

[0036] In order to improve the stability of the Y-port pressure relief branch 4 and the X-port pressure relief branch 7, the A-port relief valve 31 and the B-port relief valve 61 both include an overflow oil inlet end and an overflow oil outlet end, the Y-port check valve 41 and the X-port check valve 71 both include a one-way oil inlet end and a one-way oil outlet end, the oil chamber F and the oil chamber G are respectively connected to the overflow oil inlet end of the A-port relief valve 31 and the B-port relief valve 61, and the overflow oil outlet end of the A-port relief valve 31 and the B-port relief valve 61 are respectively connected The one-way oil inlet end of the Y-port one-way valve 41 and the B-port one-way valve, and the one-way oil outlet end of the Y-port one-way valve 41 and the B-port one-way valve are respectively connected to the oil port A and the oil port B, the Y1 and the oil port Y2 are respectively connected between the overflow oil outlet end of the A-port relief valve 31 and the one-way oil inlet end of the Y-port one-way valve 41, and the X1 and the oil port X2 are respectively connected between the overflow oil outlet end of the B-port relief valve 61 and the one-way oil inlet end of the X-port one-way valve 71. When the overflow branch 3 of port A is overflow-connected, the overflow inlet pressure of the overflow valve 31 of port A is greater than the overflow outlet pressure, so the oil pressure of the one-way outlet pressure of the one-way check valve 41 of port Y is greater than the one-way inlet pressure, so the one-way check valve 41 of port Y will not be opened to prevent the oil in the overflow branch 3 of port A from being directly lost through the pressure relief branch 4 of port Y; when the overflow branch 6 of port B is overflow-connected, the overflow inlet pressure of the overflow valve 61 of port B is greater than the overflow outlet pressure, so the oil pressure of the one-way outlet pressure of the one-way check valve 71 of port X is greater than the one-way inlet pressure, so the one-way check valve 71 of port X will not be opened to prevent the oil in the overflow branch 6 of port B from being directly lost through the pressure relief branch 7 of port X.

[0037] Specifically, the B-port reversing valve 9 includes an oil port C2, an oil port A2, an oil port B2, and an oil port D2 respectively connected to the oil port B, the oil chamber E, and the oil chamber G, and a locking oil port D2; when the B-port reversing valve 9 is in the B-port first-level position, the oil port A2 is connected to the oil port C2, and the oil port B2 is connected to the oil port D2; when the B-port reversing valve 9 is in the B-port second-level position, the oil port A2 is connected to the oil port D2, and the oil port B2 is connected to the oil port C2.

[0038] Specifically, the A-port reversing valve 8 includes an oil port C1, an oil port A1, an oil port B1, and an oil port D1 respectively connected to the oil port A, the oil chamber F, and the oil chamber H; when the A-port reversing valve 8 is in the A-port first-level position, the oil port A1 is connected to the oil port C1, and the oil port B1 is connected to the oil port D1; when the A-port reversing valve 8 is in the A-port second-level position, the oil port A1 is connected to the oil port D1, and the oil port B1 is connected to the oil port C1.

[0039] To achieve sequential operation between multiple cylinders, the oil chambers F and H are both rod chambers, and the oil chambers E and G are both rodless chambers. The number of primary cylinders 2 and secondary cylinders 5 is set to multiple. The oil chambers F and E of the multiple primary cylinders 2 are arranged in parallel, and the oil chambers G and H of the multiple secondary cylinders 5 are arranged in parallel. Specifically, in this embodiment, the number of primary cylinders 2 and secondary cylinders 5 is two.

[0040] Working principle:

[0041] 1. When oil is flowing into port A, refer to Figure 1 :

[0042] The A-port reversing valve 8 and the B-port reversing valve 9 are in the A-port first-stage position and the B-port first-stage position, respectively. The oil from the oil source 1 enters the oil chamber F through the oil ports A, C1, and A1. The oil in the oil chamber E flows back to the oil source 1 through the oil ports A2, C2, and B to drive the piston rod of the first-stage oil cylinder 2.

[0043] When the piston rod of the first-stage oil cylinder 2 moves to its full position, the pressure at the oil inlet end of the A-port relief valve 31 gradually increases to a value higher than the set pressure of the A-port relief valve 31, causing it to open. The overflowing oil continuously enters the oil port Y1 of the A-port reversing valve 8 and the oil port Y2 of the B-port reversing valve 9 through the A-port relief branch 3, and the oil in the oil port X1 of the A-port reversing valve 8 and the oil port X2 of the B-port reversing valve 9 flows back to the oil source 1 through the X-port pressure relief branch 7 and the oil port B, until the A-port reversing valve 8 and the B-port reversing valve 9 are pushed to move to the A-port secondary station and the B-port secondary station to realize reversal.

[0044] The oil from the oil source 1 then enters the oil chamber H through the oil ports A, C1, and B1. The oil in the oil chamber G flows back to the oil source 1 through the oil ports B2, C2, and B to drive the piston rod of the secondary cylinder 5, thereby completing the sequential actions of first driving the primary cylinder 2 and then driving the secondary cylinder 5.

[0045] 2. When oil is flowing into port B, refer to Figure 2 :

[0046] The A-port reversing valve 8 and the B-port reversing valve 9 are in the A-port secondary position and the B-port secondary position, respectively. The oil from the oil source 1 enters the oil chamber G through the oil ports B, C2, and B2. The oil in the oil chamber H flows back to the oil source 1 through the oil ports B1, C1, and A to drive the piston rod of the secondary oil cylinder 5.

[0047] When the piston rod of the secondary oil cylinder 5 moves to its full position, the pressure at the oil inlet end of the B-port relief valve 61 gradually increases to a level higher than the set pressure of the B-port relief valve 61, causing it to open. The overflowing oil continuously enters the oil port X1 of the A-port reversing valve 8 and the oil port X2 of the B-port reversing valve 9 through the B-port overflow branch 6, and the oil in the oil port Y1 of the A-port reversing valve 8 and the oil port Y2 of the B-port reversing valve 9 flows back to the oil source 1 through the Y-port pressure relief branch 4 via the oil port A, until the A-port reversing valve 8 and the B-port reversing valve 9 are pushed to move to the A-port first-level station and the B-port first-level station to realize reversal.

[0048] The oil from the oil source 1 then enters the oil chamber E through the oil ports B, C2, and A2. The oil in the oil chamber F flows back to the oil source 1 through the oil ports A1, C1, and A to drive the piston rod of the first-stage cylinder 2, thereby completing the sequential actions of first driving the second-stage cylinder 5 and then driving the first-stage cylinder 2.

[0049] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that the present invention is susceptible to various modifications and variations. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention.

Claims

1. A hydraulically controlled sequential action hydraulic system, characterized in that: include: An oil source (1), including an oil port A and an oil port B; The first-stage oil cylinder (2) comprises an oil chamber E and an oil chamber F separated by a piston rod, wherein the oil chamber F is connected to an A-port overflow branch (3) provided with an A-port overflow valve (31), and the A-port overflow branch (3) is connected to the oil port A via a Y-port pressure relief branch (4) provided with a Y-port check valve (41); The secondary oil cylinder (5) comprises an oil chamber G and an oil chamber H separated by a piston rod, wherein the oil chamber G is connected to a B-port overflow branch (6) provided with a B-port overflow valve (61), and the B-port overflow branch (6) is connected to the oil port B via an X-port pressure relief branch (7) provided with an X-port check valve (71); The A-port reversing valve (8) is respectively connected to the oil port A, the oil chamber F, the oil chamber H, the A-port overflow branch (3), and the B-port overflow branch (6); the A-port reversing valve (8) includes an A-port primary station for connecting the oil port A and the oil chamber F and locking the oil chamber H, and an A-port secondary station for connecting the oil port A and the oil chamber H and locking the oil chamber F; The B-port reversing valve (9) is respectively connected to the oil port B, the oil chamber E, the oil chamber G, the A-port overflow branch (3), and the B-port overflow branch (6); the B-port reversing valve (9) includes a B-port primary station for connecting the oil port B and the oil chamber E and locking the oil chamber G, and a B-port secondary station for connecting the oil port B and the oil chamber G and locking the oil chamber E; The A-port overflow branch (3) is used to push the A-port reversing valve (8) and the B-port reversing valve (9) to move to the A-port secondary station and the B-port secondary station after the overflow is conducted, and the B-port overflow branch (6) is used to push the A-port reversing valve (8) and the B-port reversing valve (9) to move to the A-port primary station and the B-port primary station after the overflow is conducted.

2. A hydraulically controlled sequential action hydraulic system according to claim 1, characterized in that: The two ends of the A-port reversing valve (8) include an oil port Y1 and an oil port X1 respectively connected to the A-port overflow branch (3) and the B-port overflow branch (6); the two ends of the B-port reversing valve (9) include an oil port Y2 and an oil port X2 respectively connected to the A-port overflow branch (3) and the B-port overflow branch (6); when the A-port reversing valve (8) and the B-port reversing valve (9) move to the A-port first-level station and the B-port first-level station, the Y-port pressure relief branch (4) is used to relieve pressure on the oil ports Y1 and Y2; when the A-port reversing valve (8) and the B-port reversing valve (9) move to the A-port second-level station and the B-port second-level station, the X-port pressure relief branch (7) is used to relieve pressure on the oil ports X1 and X2.

3. A hydraulic control sequential action hydraulic system according to claim 1, characterized in that: The A-port overflow valve (31) and the B-port overflow valve (61) both include an overflow oil inlet end and an overflow oil outlet end, the Y-port one-way valve (41) and the X-port one-way valve (71) both include a one-way oil inlet end and a one-way oil outlet end, the oil chamber F and the oil chamber G are respectively connected to the overflow oil inlet ends of the A-port overflow valve (31) and the B-port overflow valve (61), and the overflow oil outlet ends of the A-port overflow valve (31) and the B-port overflow valve (61) are respectively connected to the Y-port one-way valve (41). ) and the one-way oil inlet end of the B-port one-way valve, the one-way oil outlet ends of the Y-port one-way valve (41) and the B-port one-way valve are connected to the oil port A and the oil port B respectively, the Y1 and the oil port Y2 are connected between the overflow oil outlet end of the A-port overflow valve (31) and the one-way oil inlet end of the Y-port one-way valve (41) respectively, and the X1 and the oil port X2 are connected between the overflow oil outlet end of the B-port overflow valve (61) and the one-way oil inlet end of the X-port one-way valve (71) respectively.

4. A hydraulically controlled sequential action hydraulic system according to claim 1, characterized in that: The B-port reversing valve (9) comprises an oil port C2, an oil port A2, an oil port B2 respectively connected to the oil port B, the oil chamber E, and the oil chamber G, and an oil port D2 with a locking arrangement; when the B-port reversing valve (9) is in the B-port primary position, the oil port A2 is connected to the oil port C2, and the oil port B2 is connected to the oil port D2; when the B-port reversing valve (9) is in the B-port secondary position, the oil port A2 is connected to the oil port D2, and the oil port B2 is connected to the oil port C2.

5. The hydraulic control sequential action hydraulic system according to claim 1, characterized in that: The A-port reversing valve (8) comprises an oil port C1, an oil port A1, an oil port B1, which are respectively connected to the oil port A, the oil chamber F, and the oil chamber H, and an oil port D1 with a locking arrangement; when the A-port reversing valve (8) is in the A-port primary position, the oil port A1 is connected to the oil port C1, and the oil port B1 is connected to the oil port D1; when the A-port reversing valve (8) is in the A-port secondary position, the oil port A1 is connected to the oil port D1, and the oil port B1 is connected to the oil port C1.

6. The hydraulic control sequential action hydraulic system according to claim 1, characterized in that: The oil chamber F and the oil chamber H are both rod chambers, the oil chamber E and the oil chamber G are both rodless chambers, the number of the first-stage oil cylinder (2) and the second-stage oil cylinder (5) are both set to be several, the oil chambers F of the first-stage oil cylinder (2) are arranged in parallel, the oil chambers E are arranged in parallel, and the oil chambers G of the second-stage oil cylinder (5) are arranged in parallel, the oil chambers H are arranged in parallel.

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