A hydraulic static pile driver and its hydraulic control system

Abstract

The present invention discloses a hydraulic static pile driver and its hydraulic control system. The hydraulic control system includes a multi-way valve main valve, a quick pressure valve group, a quick return valve group, a main pressure oil cylinder, and a secondary pressure oil cylinder. The quick pressure valve group is integrated with the main pressure oil cylinder, and the quick return valve group is integrated with the secondary pressure oil cylinder. The multi-way valve main valve is connected to the quick pressure valve group, and the multi-way valve main valve is connected to the quick return valve group. The above-mentioned hydraulic control system can realize the integrated arrangement of the multi-way valve main valve and the hydraulic valve group, thereby simplifying the pipeline layout, reducing the labor intensity of operation, reducing energy consumption and improving work efficiency. The system has a high pressure level, which is sufficient to meet the development requirements of high-pressure equipment.

Description

Technical Field

[0001] The present invention relates to the field of hydraulic control technology, and in particular to a hydraulic control system. The present invention also relates to a hydraulic static pile driver having the hydraulic control system. Background Art

[0002] Hydraulic static pile driver is a widely used basic construction equipment. Its core hydraulic control components include multiple manual multi-way control valves such as pile driving multi-way valve, travel multi-way valve, outrigger multi-way valve, as well as multiple dispersed control valve groups such as confluence valve group and oil drain valve group.

[0003] In the hydraulic system of the prior art, when the oil return from the small chamber of the cylinder is in a fast pressure condition, it first passes through a long pipeline, then passes through the fast pressure connection inside the multi-way valve, and then returns to the large chamber of the cylinder through a long pipeline, resulting in high pressure loss and large energy waste, which is not conducive to improving equipment efficiency.

[0004] Therefore, as the requirements for optimization of the pile driver control system become increasingly higher and the control of energy conservation becomes more stringent, it is necessary for technical personnel in this field to timely propose a pile driver hydraulic control system with high integration, low pressure loss and high working efficiency. Summary of the Invention

[0005] The present invention aims to provide a hydraulic control system that integrates control valves and hydraulic piping, thereby simplifying piping layout, reducing operating labor, lowering energy consumption, and improving operating efficiency. Another object of the present invention is to provide a hydraulic static pile driver incorporating the aforementioned hydraulic control system.

[0006] To achieve the above-mentioned objectives, the present invention provides a hydraulic control system, including a multi-way valve main valve, a quick pressure valve group, a quick return valve group, a main pressure oil cylinder and a secondary pressure oil cylinder, the quick pressure valve group is integrated on the main pressure oil cylinder, the quick return valve group is integrated on the secondary pressure oil cylinder, the multi-way valve main valve is connected to the quick pressure valve group, and the multi-way valve main valve is connected to the quick return valve group.

[0007] Optionally, the multi-way valve main valve includes a multi-way valve body and a main overflow valve two-stage control valve group, and the main overflow valve two-stage control valve group is integrated on the multi-way valve body.

[0008] Optionally, the multi-way valve body includes a first half-integral valve and a second half-integral valve;

[0009] The first half of the integral valve includes a pile clamping unit, a main pressure unit, an oil inlet unit 1, a longitudinal shift unit 2, a longitudinal shift unit 1, a support leg 4 unit and a support leg 3 unit;

[0010] The second half integral valve includes a first auxiliary pressure unit, a second auxiliary pressure unit, a second oil inlet unit, a second transverse movement unit, a first transverse movement unit, a second support leg unit and a first support leg unit.

[0011] Optionally, the multi-way valve main valve further includes a main oil return line provided inside the multi-way valve body and connected to the oil return tank;

[0012] The main relief valve two-stage control valve group includes a first bypass cut-off control valve, a first damping orifice, a second bypass cut-off control valve, a second damping orifice, a secondary relief valve and a main relief valve;

[0013] The first bypass cut-off control valve is connected to a first external pilot oil source via an external control oil port X1. After the first external pilot oil source is connected to the external control oil port X1, the first external pilot oil source acts on the first bypass cut-off control valve via the first damping orifice.

[0014] The second bypass cut-off control valve is connected to a second external pilot oil source via the external control oil port X2. After the second external pilot oil source is connected to the external control oil port X2, it acts on the second bypass cut-off control valve via the second damping orifice.

[0015] The control port of the main relief valve is connected in series with the first bypass cut-off control valve and the second bypass cut-off control valve through a control oil circuit and then communicates with the main oil return circuit;

[0016] The oil inlet of the secondary relief valve is communicated with the series pipeline between the first bypass cut-off control valve and the second bypass cut-off control valve, and the oil outlet and control oil port of the secondary relief valve are both communicated with the main oil return line.

[0017] Optionally, it further comprises an upper signal control path connected to the first bypass cut-off control valve and a lower signal control path connected to the second bypass cut-off control valve;

[0018] The upper signal control circuit is connected in series with the auxiliary pressure unit 1, the auxiliary pressure unit 2, the clamping pile unit and the main pressure unit, and then communicated with the main oil return circuit;

[0019] The lower signal control circuit is connected in series with the longitudinal shift second unit, the longitudinal shift first unit, the support leg quadruple unit, the support leg triple unit, the support leg first unit, the support leg second unit, the transverse shift first unit and the transverse shift second unit in sequence and then communicated with the main oil return circuit.

[0020] Optionally, the oil inlet link 1 and the oil inlet link 2 are connected through a channel and then branched into a lower parallel path 1 and a lower parallel path 2, the lower parallel path 1 is connected in parallel to the second longitudinal movement link, the first longitudinal movement link, the fourth support leg link and the third support leg link, the lower parallel path 2 is connected in parallel to the second transverse movement link, the first transverse movement link, the second support leg link, the first support leg link and the oil inlet of the main relief valve, and the oil return port of the main relief valve is connected to the main oil return path;

[0021] The oil inlet link 1 includes a pump oil inlet P1, and the oil inlet link 2 includes a pump oil inlet P2. The pump oil inlet P1 is connected to the forward oil inlet of the one-way valve 2, and the pump oil inlet P2 is connected to the forward oil inlet of the one-way valve 1. The forward oil outlet of the one-way valve 2 and the forward oil outlet of the one-way valve 1 are connected through a flow channel and then branched into an upper parallel path 1 and an upper parallel path 2. The upper parallel path 1 is connected in parallel to the main pressure link and the clamping pile link, and the upper parallel path 2 is connected in parallel to the auxiliary pressure link 1 and the auxiliary pressure link 2.

[0022] Optionally, the fast pressure valve group includes a fast pressure valve body and a fast pressure switching valve, a flow channel is provided inside the fast pressure valve body, the fast pressure switching valve is provided on the fast pressure valve body, the forward oil inlet of the fast pressure switching valve is connected to the small chamber of the main pressure oil cylinder, the forward working oil port A22 of the fast pressure switching valve is connected to the large chamber of the main pressure oil cylinder, the forward working oil port B22 of the fast pressure switching valve is connected to the main valve of the multi-way valve, and the hydraulic control oil port of the fast pressure switching valve is connected to an external control source.

[0023] Optionally, the quick return valve group includes a large-cavity hydraulically controlled one-way valve and a small-cavity hydraulically controlled one-way valve, the forward oil outlet of the large-cavity hydraulically controlled one-way valve is connected to the large cavity of the secondary pressure oil cylinder, the hydraulically controlled oil port of the large-cavity hydraulically controlled one-way valve is connected to an external control source, the forward oil inlet of the large-cavity hydraulically controlled one-way valve is connected to the forward oil inlet of the small-cavity hydraulically controlled one-way valve and an external oil tank, and the forward oil outlet of the small-cavity hydraulically controlled one-way valve is connected to the small cavity of the secondary pressure oil cylinder.

[0024] Optionally, it further comprises an oil drain valve group, wherein the main valve of the multi-way valve is connected to the quick pressure valve group through the oil drain valve group, and the oil drain valve group is connected to an external oil tank;

[0025] The oil drain valve group includes a hydraulically controlled one-way valve 1, the forward oil inlet of the hydraulically controlled one-way valve 1 is connected to the external oil tank, the forward oil outlet of the hydraulically controlled one-way valve 1 is connected to the large chamber of the main pressure oil cylinder, and the hydraulic oil port of the hydraulically controlled one-way valve 1 is connected to an external control source; the hydraulically controlled one-way valve 1 is opened by the external control source to enable the hydraulic oil in the large chamber of the main pressure oil cylinder to flow back through the hydraulically controlled one-way valve 1 and return to the external oil tank during pile lifting operation.

[0026] The present invention also provides a hydraulic static pile driver, comprising any one of the hydraulic control systems described above.

[0027] Compared with the above background technology, the hydraulic control system provided by the embodiment of the present invention includes a multi-way valve main valve, a quick pressure valve group, a quick return valve group, a main pressure oil cylinder and a secondary pressure oil cylinder, wherein the quick pressure valve group is integrated on the main pressure oil cylinder to realize the quick pressure function; the quick return valve group is integrated on the secondary pressure oil cylinder to realize the quick return function; the multi-way valve main valve is connected to the quick pressure valve group, and the multi-way valve main valve is connected to the quick return valve group to realize the pile driver's pile driving, pile clamping, force application, walking, lifting and other functions.

[0028] When performing fast pressure operation, the passage from the small cavity of the main pressure cylinder to the main valve of the multi-way valve is blocked by the fast pressure valve group, so that the hydraulic oil in the small cavity of the main pressure cylinder passes through the fast pressure valve group and merges with the hydraulic oil from the main valve of the multi-way valve at the entrance of the large cavity of the main pressure cylinder, and directly flows back to the large cavity of the main pressure cylinder. Since the fast pressure valve group is directly integrated on the main pressure cylinder, when the fast pressure is actuated, it is no longer necessary to return to the large cavity of the main pressure cylinder through a long pipeline and the fast pressure link inside the main valve of the multi-way valve, and a differential circuit is directly realized. Therefore, the pressure loss under fast pressure condition can be greatly reduced, and the operation speed can be improved. Moreover, since the fast pressure function is integrated on the cylinder, there is no need to set a fast pressure link on the main valve of the multi-way valve. , the structure of the main valve of the multi-way valve is simplified; when performing quick lifting operations, by blocking the inlet and outlet oil channels of the auxiliary pressure cylinder and controlling the hydraulic oil to enter the small chamber of the main pressure cylinder through the main valve of the multi-way valve, the piston rod of the main pressure cylinder is lifted, and at the same time, the auxiliary pressure cylinder is pushed to passively return. When the piston rod of the auxiliary pressure cylinder is quickly lifted, by controlling the quick return valve group, a part of the hydraulic oil in the large chamber of the auxiliary pressure cylinder enters the small chamber of the auxiliary pressure cylinder for replenishment, and the excess hydraulic oil enters the external oil tank through the pipeline, thereby realizing the quick lifting operation of the pile driver. At the same time, since the quick return valve group is directly integrated on the auxiliary pressure cylinder, this can reduce the pipeline pressure loss and improve the quick lifting efficiency.

[0029] As a result, compared to the traditional manually controlled pile driver multi-way valve, the control valve group is too dispersed, resulting in a messy piping layout, high labor intensity in operation, multiple oil leaks, and inconvenient after-sales maintenance. In addition, due to the use of a machine-added flow channel design, the pressure level is only 25MPa, which cannot meet the requirements of the development of high-pressure equipment. The hydraulic control system provided by the embodiment of the present invention can realize the integrated setting of the multi-way valve main valve and the hydraulic valve group, thereby simplifying the piping layout, reducing the labor intensity in operation, reducing energy consumption, and improving work efficiency. The system has a high pressure level, which is sufficient to meet the development requirements of high-pressure equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0031] Figure 1 A schematic diagram of a hydraulic control system provided by an embodiment of the present invention;

[0032] Figure 2 A front view of a main valve of a multi-way valve provided by an embodiment of the present invention;

[0033] Figure 3 A schematic diagram showing the principles of the lower signal control path and the upper signal control path provided by an embodiment of the present invention;

[0034] Figure 4 A schematic diagram of a portion of the hydraulic circuit principles provided by an embodiment of the present invention;

[0035] Figure 5 A schematic diagram of a fast pressure valve assembly provided by an embodiment of the present invention;

[0036] Figure 6 A schematic diagram of a two-stage control valve group of a main relief valve provided in an embodiment of the present invention;

[0037] Figure 7 A schematic diagram of a quick return valve assembly provided by an embodiment of the present invention;

[0038] Figure 8 for Figure 2 Cross-sectional view at DD in the middle;

[0039] Figure 9 for Figure 2 Cross-sectional view at EE;

[0040] Figure 10 A schematic diagram of the oil drain valve assembly provided in an embodiment of the present invention;

[0041] Figure 11 This is a connection diagram of the fast pressure valve group provided by an embodiment of the present invention.

[0042] in:

[0043] 1-Multi-way valve main valve, 2-Quick pressure valve group, 3-Quick return valve group, 4-Oil discharge valve group, 5-Cylinder, 6-Lower signal control line, 7-Upper signal control line, 8-Lower parallel line 1, 9-Lower parallel line 2, 10-Main oil return line, 11-Multi-way valve body, 12-Pile clamp valve group, 13-Main relief valve two-stage control valve group, 14-Control oil line, 15-Upper parallel line 1, 16-Upper parallel line 2, 17-Check valve 1, 18-Check valve 2, 21-Quick pressure valve body, 22-Quick pressure switching valve;

[0044] 111 - first half integral valve, 112 - second half integral valve;

[0045] 121-Pile clamp hydraulic control one-way valve;

[0046] 131 - first bypass cut-off control valve, 132 - second bypass cut-off control valve, 133 - main relief valve, 134 - first damping orifice, 135 - second damping orifice, 136 - secondary relief valve;

[0047] 301-Large cavity hydraulically controlled one-way valve, 302-Small cavity hydraulically controlled one-way valve;

[0048] 401-hydraulic controlled one-way valve 1;

[0049] 501-main pressure cylinder, 502-auxiliary pressure cylinder;

[0050] 1111-pile clamping unit, 1112-main pressure unit, 1113-oil inlet unit 1, 1114-longitudinal movement unit 2, 1115-longitudinal movement unit 1, 1116-support leg unit 4, 1117-support leg unit 3;

[0051] 1121- auxiliary pressure unit 1, 1122- auxiliary pressure unit 2, 1123- transverse movement unit 2, 1124- transverse movement unit 1, 1125- support leg unit 2, 1126- support leg unit 1, 1127- oil inlet unit 2. DETAILED DESCRIPTION

[0052] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0053] The core of the present invention is to provide a hydraulic control system that integrates control valves and hydraulic piping, thereby simplifying piping layout, reducing operating labor, lowering energy consumption, and improving work efficiency. Another core of the present invention is to provide a hydraulic static pile driver that includes the hydraulic control system.

[0054] In order to enable those skilled in the art to better understand the solutions of the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0055] refer to Figure 1The hydraulic control system provided by the embodiment of the present invention includes a multi-way valve main valve 1, a fast pressure valve group 2, a quick return valve group 3, and a cylinder 5, wherein the cylinder 5 includes a main pressure cylinder 501 and a secondary pressure cylinder 502, and the fast pressure valve group 2 is integrated on the main pressure cylinder 501 to realize the fast pressure function, so that the hydraulic oil in the small cavity of the main pressure cylinder 501 no longer needs to flow back to the large cavity of the main pressure cylinder 501 through a long pipeline, and the differential circuit is directly realized; the quick return valve group 3 is integrated on the secondary pressure cylinder 502 to realize the quick return function; the multi-way valve main valve 1 is connected to the pipeline of the fast pressure valve group 2, and the multi-way valve main valve 1 is connected to the pipeline of the quick return valve group 3.

[0056] The system also includes an oil drain valve assembly 4 and an external oil tank. The multi-way valve main valve 1 is connected to the pipeline of the quick-pressure valve assembly 2 via the oil drain valve assembly 4, which is in turn connected to the external oil tank. By controlling the oil drain valve assembly 4, the hydraulic oil in the main chamber of the main pressure cylinder 501 is directly returned to the external oil tank after passing through the oil drain valve assembly 4 during pile lifting. This improves the efficiency of the pile lifting operation and reduces the labor intensity of the operator.

[0057] It should be noted that the multi-way valve main valve 1 includes two semi-integrally cast multi-way valve structures, which are cast with QT500 material and have a pressure rating of 35MPa, and are used to realize functions such as pile driving, pile clamping, force application, walking, and lifting.

[0058] Compared with the traditional manually controlled pile driver multi-way valve, the pile driver valve, leg valve, and travel valve are three separate sets of multi-way valves, plus some valve blocks with auxiliary functions. The layout of the control valve group is too dispersed, which makes the pipeline layout messy, the operation labor intensity is high, there are many oil leakage points, after-sales maintenance is inconvenient, and it is not beautiful. In addition, due to the use of a machine-added flow channel design, the pressure level is 25MPa, which cannot meet the requirements of the high-pressure development of equipment. The hydraulic control system provided by the embodiment of the present invention can realize the integrated setting of the multi-way valve main valve and the hydraulic valve group, changing the traditional mode of three multi-way valve main valves plus a basic valve block to the mode of an integral multi-way valve, thereby simplifying the pipeline layout, reducing the operation labor intensity, reducing energy consumption and improving work efficiency. The system has a high pressure level, which is sufficient to meet the requirements of the high-pressure development of equipment, and its operating capacity is greatly improved.

[0059] Specifically, the multi-way valve main valve 1 includes a multi-way valve body 11, a pile clamp valve group 12 and a main overflow valve two-stage control valve group 13. The multi-way valve main valve 1 also includes a main return oil circuit 10. The main return oil circuit 10 is arranged inside the multi-way valve body 11 and connected to the return oil tank. The pile clamp valve group 12 and the main overflow valve two-stage control valve group 13 are integrated on the multi-way valve body 11.

[0060] refer to Figure 2 、 Figure 3 、 Figure 8 and Figure 9The multi-way valve body 11 includes a first half integral valve 111 and a second half integral valve 112. The first half integral valve 111 includes a pile clamping link 1111, a main pressure link 1112, an oil inlet link 1 1113, a longitudinal shift link 2 1114, a longitudinal shift link 1 1115, a leg quadruple link 1116, and a leg triple link 1117, and each working link serves as a hydraulic pilot control. The second half integral valve 112 includes a secondary pressure link 1 1121, a secondary pressure link 2 1122, an oil inlet link 2 1127, a transverse shift link 2 1123, a transverse shift link 1 1124, a leg quadruple link 1125, and a leg quadruple link 1 1126, and each working link serves as a hydraulic pilot control.

[0061] refer to Figure 6 The main relief valve two-stage control valve assembly 13 includes a first bypass cutoff control valve 131, a first damping orifice 134, a second bypass cutoff control valve 132, a second damping orifice 135, a secondary relief valve 136, and a main relief valve 133. The first bypass cutoff control valve 131 is connected to a first external pilot oil source via an external control oil port X1. After the first external pilot oil source is connected to the external control oil port X1, the oil acts on the first bypass cutoff control valve through the first damping orifice. The second bypass cutoff control valve 132 is connected to a second external pilot oil source via an external control oil port X2. After the second external pilot oil source is connected to the external control oil port X2, the oil acts on the second bypass cutoff control valve through the second damping orifice.

[0062] refer to Figure 6 、 Figure 4 and Figure 3 The control port of the main relief valve 133 is connected in series with the first bypass cut-off control valve 131 and the second bypass cut-off control valve 132 through the control oil circuit 14, and then connected to the main oil return circuit 10; the oil inlet of the secondary relief valve 136 is connected to the series pipeline between the first bypass cut-off control valve 131 and the second bypass cut-off control valve 132, and the oil outlet and control oil port of the secondary relief valve 136 are both connected to the main oil return circuit 10.

[0063] Further, refer to Figure 3 The hydraulic control system also includes an upper signal control path 7 connected to the first bypass cut-off control valve 131 and a lower signal control path 6 connected to the second bypass cut-off control valve 132; wherein the upper signal control path 7 is connected in series with the auxiliary pressure link 1121, the auxiliary pressure link 2 1122, the pile clamp link 1111 and the main pressure link 1112 in sequence, and finally connected with the main return oil path 10 after returning the oil; the lower signal control path 6 is connected in series with the longitudinal movement link 2 1114, the longitudinal movement link 1 1115, the support leg four-link 1116, the support leg three-link 1117, the support leg link 1126, the support leg link 2 1125, the transverse movement link 1 1124 and the transverse movement link 2 1123 in sequence, and finally connected with the main return oil path 10 after returning the oil.

[0064] In this way, after the first external pilot oil source is connected to the X1 port, it acts on the first bypass cut-off control valve 131 through the first damping hole 134. At the same time, the auxiliary pressure link 1121, the auxiliary pressure link 2 1122, the clamping pile link 1111 and the main pressure link 1112 are connected in series in sequence through the upper signal control path 7, and finally connected to the main return oil path 10 and then the oil is returned; through the above connection, when any one of the valves in the auxiliary pressure link 1121, the auxiliary pressure link 2 1122, the clamping pile link 1111 and the main pressure link 1112 is reversed, the channel back to the oil tank of the upper signal control path 7 is blocked, and the first external pilot oil source passes through the X1 port, and acts on the valve core of the first bypass cut-off control valve 131 through the first damping hole 134, pushing the valve core of the first bypass cut-off control valve 131 to reverse, thereby building up pressure in the main relief valve 133. At this time, the relief pressure of the main relief valve 133 is determined by its own set pressure.

[0065] After the second external pilot oil source is connected to the X2 port, it acts on the second bypass cut-off control valve 132 through the second damping hole 135. At the same time, the longitudinal shift second link 1114, the longitudinal shift first link 1115, the support leg quadruple link 1116, the support leg triple link 1117, the support leg first link 1126, the support leg second link 1125, the transverse shift first link 1124 and the transverse shift second link 1123 are connected in series in sequence through the lower signal control line 6, and finally connected to the main oil return line 10 and then the oil is returned; through the above connection, the longitudinal shift second link 1114, the longitudinal shift first link 1115, the support leg quadruple link 1116, the support leg triple link 1117, the support leg first link 1126, the support leg second link 1125, the transverse shift first link 1124 and the transverse shift second link 1123 are connected in series in sequence. 126, the support leg two-link 1125, the transverse movement one-link 1124 and the transverse movement two-link 1123, when any one of the valves is reversed, the channel of the lower signal control line 6 back to the oil tank is blocked, and the second external pilot oil source passes through the X2 port, and then acts on the valve core of the second bypass cut-off control valve 132 through the second damping hole 135, pushing the valve core of the second bypass cut-off control valve 132 to reverse, thereby building up pressure in the main relief valve 133. At this time, the relief pressure of the main relief valve 133 is determined by the secondary relief valve 136. It should be noted that the set pressure of the secondary relief valve 136 is lower than the set pressure of the main relief valve 133.

[0066] In this way, due to the arrangement of the main overflow valve two-stage control valve group 13 of the above-mentioned connection structure, two-stage pressure control of the pile driving machine body movement and pile driving can be achieved.

[0067] In addition, reference Figure 4The oil inlet link 1113 and the oil inlet link 2 1127 are connected to each other through the channel and then branched into the lower parallel road 1 8 and the lower parallel road 2 9. The lower parallel road 1 8 is connected in parallel to the second longitudinal movement link 1114, the first longitudinal movement link 1115, the fourth support leg link 1116 and the third support leg link 1117; the lower parallel road 2 9 is connected in parallel to the second transverse movement link 1123, the first transverse movement link 1124, the second support leg link 1125, the first support leg link 1126 and the oil inlet of the main overflow valve 133, and the oil return port of the main overflow valve 133 is connected to the main oil return road 10.

[0068] refer to Figure 4 The oil inlet link 1113 includes a pump oil inlet P1, and the oil inlet link 2 1127 includes a pump oil inlet P2. The pump oil inlet P1 is connected to the forward oil inlet of the one-way valve 2 18, and the pump oil inlet P2 is connected to the forward oil inlet of the one-way valve 17. The forward oil outlet of the one-way valve 2 18 and the forward oil outlet of the one-way valve 17 are connected through the flow channel and branched into an upper parallel path 15 and an upper parallel path 2 16; the upper parallel path 15 is connected in parallel to the main pressure link 1112 and the clamping pile link 1111; the upper parallel path 2 16 is connected in parallel to the auxiliary pressure link 1 1121 and the auxiliary pressure link 2 1122.

[0069] In this way, by providing one-way valve 17 and one-way valve 2 18, the flow path where the upper parallel path 15 and the upper parallel path 2 16 are located is isolated from the flow path where the lower parallel path 1 8 and the lower parallel path 2 9 are located. Due to the unidirectional conductivity of one-way valve 17 and one-way valve 2 18, the high pressure in the flow path where the upper parallel path 15 and the upper parallel path 2 16 are located will not impact the flow path where the lower parallel path 1 8 and the lower parallel path 2 9 are located.

[0070] refer to Figure 1 and Figure 10 The oil drain valve group 4 includes a hydraulically controlled one-way valve 401. The forward oil inlet of the hydraulically controlled one-way valve 401 is connected to the external oil tank, and the forward oil outlet of the hydraulically controlled one-way valve 401 is connected to the large cavity of the main pressure oil cylinder 501. The hydraulic oil port of the hydraulically controlled one-way valve 401 is connected to the external control source. The hydraulically controlled one-way valve 401 is opened by the external control source, and then during the pile lifting operation, the hydraulic oil in the large cavity of the main pressure oil cylinder 501 is reversed through the hydraulically controlled one-way valve 401 and directly returned to the external oil tank.

[0071] refer to Figure 1 、 Figure 5 and Figure 11, the fast pressure valve group 2 is directly integrated on the main pressure oil cylinder 501, the fast pressure valve group 2 includes a fast pressure valve body 21 and a fast pressure switching valve 22, the inside of the fast pressure valve body 21 is provided with a flow channel, the fast pressure switching valve 22 is arranged on the fast pressure valve body 21, the forward oil inlet of the fast pressure switching valve 22 is connected to the small cavity of the main pressure oil cylinder 501, the forward working oil port A22 of the fast pressure switching valve 22 is connected to the large cavity of the main pressure oil cylinder 501, the forward working oil port B22 of the fast pressure switching valve 22 is connected to the oil drain valve group 4, and the hydraulic control oil port of the fast pressure switching valve 22 is connected to the control source; when the fast pressure is actuated, the fast pressure switching valve 22 is reversed by the control source to block the passage from the small cavity of the main pressure oil cylinder 501 to the main valve 1 of the multi-way valve, so that the small cavity of the main pressure oil cylinder 501 The hydraulic oil in the main pressure cylinder 501 passes through the forward working oil port A22 of the fast pressure switching valve 22 and merges with the hydraulic oil from the main pressure link inside the multi-way valve at the entrance of the main pressure cylinder 501 large cavity, and flows directly back to the main pressure cylinder 501 large cavity; since the fast pressure valve group 2 is directly integrated on the main pressure cylinder 501, when the fast pressure is actuated, it is no longer necessary to flow back to the main pressure cylinder 501 large cavity through a long pipeline and the fast pressure link inside the multi-way valve, and a differential circuit is directly realized, which effectively prevents the problem of low efficiency of large cavity hydraulic oil replenishment during fast pressure. Therefore, the pressure loss under fast pressure conditions can be greatly reduced and the operation speed can be improved. Moreover, since the fast pressure function is integrated on the main pressure cylinder 501, the fast pressure link is no longer set on the main valve 1 of the multi-way valve, and the structure of the main valve 1 of the multi-way valve is simplified.

[0072] refer to Figure 1 and Figure 7 The quick return valve group 3 is integrated on the secondary pressure cylinder 502. The quick return valve group 3 includes a large-cavity hydraulically controlled one-way valve 301 and a small-cavity hydraulically controlled one-way valve 302. The forward oil outlet of the large-cavity hydraulically controlled one-way valve 301 is connected to the large cavity of the secondary pressure cylinder 502, and the hydraulic control oil port of the large-cavity hydraulically controlled one-way valve 301 is connected to the external control source. The forward oil inlet of the large-cavity hydraulically controlled one-way valve 301 is connected to the forward oil inlet of the small-cavity hydraulically controlled one-way valve 302 and the external oil tank, and the forward oil outlet of the small-cavity hydraulically controlled one-way valve 302 is connected to the small cavity of the secondary pressure cylinder 502.

[0073] When a quick lifting operation is required, the position of the main pressure link 1112 is changed through an external control source. At this time, the valve cores of the auxiliary pressure link 1121 and the auxiliary pressure link 2 1122 are in the middle position, blocking the inlet and outlet oil channels of the auxiliary pressure cylinder 502, so that the hydraulic oil from the oil inlet link 1113 and the oil inlet link 2 1127 pass through the main pressure link 1112 and enter the small chamber of the main pressure cylinder 501, so that the piston rod of the main pressure cylinder 501 is lifted, and at the same time, the auxiliary pressure cylinder 502 is passively returned through an external mechanical device; when the piston rod of the auxiliary pressure cylinder 502 is quickly lifted, the external mechanical device is used to push the auxiliary pressure cylinder 502 back to its original position. The control source controls the large-cavity hydraulically controlled one-way valve 301 to open, so that the hydraulic oil in the large cavity of the auxiliary pressure oil cylinder 502 passes through the large-cavity hydraulically controlled one-way valve 301 in reverse, and a part of the hydraulic oil passes through the small-cavity hydraulically controlled one-way valve 302 in the forward direction and enters the small cavity of the auxiliary pressure oil cylinder 502 for replenishment, and the excess hydraulic oil enters the external oil tank through the pipeline, thereby realizing the quick lifting operation of the pile driver; at the same time, since the large-cavity hydraulically controlled one-way valve 301 and the small-cavity hydraulically controlled one-way valve 302 are directly integrated on the auxiliary pressure oil cylinder 502, this can reduce the pipeline pressure loss and improve the quick lifting efficiency.

[0074] refer to Figure 4 The pile clamping valve group 12 includes a pile clamping hydraulically controlled one-way valve 121. The pile clamping hydraulically controlled one-way valve 121 is integrated on the multi-way valve body 11. The hydraulic oil port of the pile clamping hydraulically controlled one-way valve 121 is connected to the small chamber of the pile clamping cylinder; when pile clamping operation is required, the valve core position of the pile clamping link 1111 is changed by an external control source, so that the hydraulic oil from the oil inlet link 1113 and the oil inlet link 2 1127 pass through the pile clamping link 1111 and the pile clamping hydraulically controlled one-way valve 121 in turn and enter the upper chamber of the pile clamping cylinder to achieve pile clamping; when the pile is clamped continuously, the high pressure in the large chamber of the pile clamping cylinder can make the pile clamping hydraulically controlled one-way valve 121 tightly closed to prevent the hydraulic oil in the upper chamber of the pile clamping cylinder from leaking from the sealing gap of the valve core of the pile clamping link 1111, thereby effectively enhancing the pressure maintaining effect of the pile clamping output end; when the pile is loosened, the valve core position of the pile clamping link 1111 is changed by an external control source, so that the large chamber of the pile clamping cylinder returns oil and the small chamber enters oil.

[0075] It should be noted that, in this article, the so-called small cavity refers to the rod cavity of the oil cylinder, and the so-called large cavity refers to the rodless cavity of the oil cylinder.

[0076] The present invention provides a hydraulic static pile driver, which includes the hydraulic control system described in the above specific embodiment; other parts of the hydraulic static pile driver can refer to the existing technology and will not be elaborated in this article.

[0077] It should be noted that, in this specification, relational terms such as first and second are merely used to distinguish one entity from other entities, but do not necessarily require or imply any actual relationship or order between these entities.

[0078] The above is a detailed introduction to the hydraulic static pile driver and its hydraulic control system provided by the present invention. Specific examples are used herein to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only intended to help understand the scheme and core ideas of the present invention. It should be pointed out that, for those skilled in the art, various improvements and modifications may be made to the present invention without departing from the principles of the present invention, and such improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A hydraulic control system, characterized in that: The invention comprises a multi-way valve main valve (1), a quick pressure valve group (2), a quick return valve group (3), a main pressure oil cylinder (501) and a secondary pressure oil cylinder (502), wherein the quick pressure valve group (2) is integrated with the main pressure oil cylinder (501), the quick return valve group (3) is integrated with the secondary pressure oil cylinder (502), the multi-way valve main valve (1) is connected to the quick pressure valve group (2), and the multi-way valve main valve (1) is connected to the quick return valve group (3); The multi-way valve main valve (1) comprises a multi-way valve body (11) and a main overflow valve two-stage control valve group (13), wherein the main overflow valve two-stage control valve group (13) is integrated with the multi-way valve body (11); The multi-way valve body (11) comprises a first half integral valve (111) and a second half integral valve (112); The first half integral valve (111) comprises a pile clamping unit (1111), a main pressure unit (1112), an oil inlet unit (1113), a second longitudinal shift unit (1114), a first longitudinal shift unit (1115), a fourth support leg unit (1116), and a third support leg unit (1117). The second half integral valve (112) comprises a first auxiliary pressure unit (1121), a second auxiliary pressure unit (1122), a second oil inlet unit (1127), a second transverse movement unit (1123), a first transverse movement unit (1124), a second support leg unit (1125) and a first support leg unit (1126); The multi-way valve main valve (1) further includes a main oil return line (10) disposed inside the multi-way valve body (11) and connected to the oil return tank; The main relief valve two-stage control valve group (13) comprises a first bypass cut-off control valve (131), a first damping orifice (134), a second bypass cut-off control valve (132), a second damping orifice (135), a secondary relief valve (136) and a main relief valve (133); The first bypass cut-off control valve (131) is connected to a first external pilot oil source via an external control oil port X1. After the first external pilot oil source is connected to the external control oil port X1, the first external pilot oil source acts on the first bypass cut-off control valve (131) via the first damping hole (134); The second bypass cut-off control valve (132) is connected to a second external pilot oil source via an external control oil port X2. After the second external pilot oil source is connected to the external control oil port X2, it acts on the second bypass cut-off control valve (132) via the second damping hole (135); The control port of the main relief valve (133) is connected in series with the first bypass cut-off control valve (131) and the second bypass cut-off control valve (132) in sequence through the control oil circuit (14), and then communicates with the main oil return circuit (10); The oil inlet of the secondary relief valve (136) is in communication with the series pipeline between the first bypass cut-off control valve (131) and the second bypass cut-off control valve (132), and the oil outlet and control oil port of the secondary relief valve (136) are both in communication with the main oil return line (10); It also includes an upper signal control path (7) connected to the first bypass cut-off control valve (131) and a lower signal control path (6) connected to the second bypass cut-off control valve (132); The upper signal control circuit (7) is connected in series with the auxiliary pressure first link (1121), the auxiliary pressure second link (1122), the clamping pile link (1111) and the main pressure link (1112) and then communicates with the main oil return circuit (10); The lower signal control circuit (6) is connected in series with the longitudinal shift second unit (1114), the longitudinal shift first unit (1115), the support leg fourth unit (1116), the support leg triple unit (1117), the support leg first unit (1126), the support leg second unit (1125), the transverse shift first unit (1124) and the transverse shift second unit (1123) and then communicates with the main oil return circuit (10).

2. The hydraulic control system according to claim 1, wherein: The oil inlet link 1 (1113) and the oil inlet link 2 (1127) are connected through a channel and then branched into a lower parallel path 1 (8) and a lower parallel path 2 (9). The lower parallel path 1 (8) is connected in parallel to the longitudinal shift link 2 (1114), the longitudinal shift link 1 (1115), the support leg quadruple link (1116) and the support leg triple link (1117). The lower parallel path 2 (9) is connected in parallel to the transverse shift link 2 (1123), the transverse shift link 1 (1124), the support leg 2 (1125), the support leg 1 (1126) and the oil inlet of the main overflow valve (133). The oil return port of the main overflow valve (133) is connected to the main oil return path (10). The oil inlet link 1 (1113) includes a pump oil inlet P1, and the oil inlet link 2 (1127) includes a pump oil inlet P2. The pump oil inlet P1 is connected to the forward oil inlet of the one-way valve 2 (18), and the pump oil inlet P2 is connected to the forward oil inlet of the one-way valve 1 (17). The forward oil outlet of the one-way valve 2 (18) and the forward oil outlet of the one-way valve 1 (17) are connected through a flow channel and then branched into an upper parallel path 1 (15) and an upper parallel path 2 (16). The upper parallel path 1 (15) is connected in parallel to the main pressure link (1112) and the clamping pile link (1111), and the upper parallel path 2 (16) is connected in parallel to the auxiliary pressure link 1 (1121) and the auxiliary pressure link 2 (1122).

3. The hydraulic control system according to any one of claims 1 to 2, characterized in that: The fast pressure valve group (2) includes a fast pressure valve body (21) and a fast pressure switching valve (22). A flow channel is provided inside the fast pressure valve body (21). The fast pressure switching valve (22) is provided on the fast pressure valve body (21). The forward oil inlet of the fast pressure switching valve (22) is connected to the small cavity of the main pressure oil cylinder (501), the forward working oil port A22 of the fast pressure switching valve (22) is connected to the large cavity of the main pressure oil cylinder (501), the forward working oil port B22 of the fast pressure switching valve (22) is connected to the multi-way valve main valve (1), and the hydraulic control oil port of the fast pressure switching valve (22) is connected to an external control source.

4. The hydraulic control system according to any one of claims 1 to 2, characterized in that: The quick return valve group (3) comprises a large-cavity hydraulically controlled one-way valve (301) and a small-cavity hydraulically controlled one-way valve (302); the forward oil outlet of the large-cavity hydraulically controlled one-way valve (301) is in communication with the large cavity of the secondary pressure oil cylinder (502); the hydraulic oil port of the large-cavity hydraulically controlled one-way valve (301) is connected to an external control source; the forward oil inlet of the large-cavity hydraulically controlled one-way valve (301) is in communication with the forward oil inlet of the small-cavity hydraulically controlled one-way valve (302) and an external oil tank; and the forward oil outlet of the small-cavity hydraulically controlled one-way valve (302) is in communication with the small cavity of the secondary pressure oil cylinder (502).

5. The hydraulic control system according to any one of claims 1 to 2, characterized in that: It also includes an oil drain valve group (4), the multi-way valve main valve (1) is connected to the quick pressure valve group (2) through the oil drain valve group (4), and the oil drain valve group (4) is connected to an external oil tank; The oil discharge valve group (4) includes a hydraulically controlled one-way valve (401), the forward oil inlet of the hydraulically controlled one-way valve (401) is connected to the external oil tank, the forward oil outlet of the hydraulically controlled one-way valve (401) is connected to the large cavity of the main pressure oil cylinder (501), and the hydraulically controlled oil port of the hydraulically controlled one-way valve (401) is connected to an external control source; the hydraulically controlled one-way valve (401) is opened by the external control source to enable the hydraulic oil in the large cavity of the main pressure oil cylinder (501) to flow back to the external oil tank after passing through the hydraulically controlled one-way valve (401) during pile lifting operation.

6. A hydraulic static pile driver, characterized in that: Comprising the hydraulic control system according to any one of claims 1 to 5.

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