A walking type self-moving tail bridge raising cylinder control system

Abstract

The present application discloses a control system for raising the oil cylinder of the tail bridge of a walking self-moving machine, including a hydraulic pump station, an electro-hydraulic proportional multi-way valve group, and several bridge units connected by hydraulic pipelines, each of which is provided with two raising oil cylinders, and also includes: a manual proportional multi-way valve group, which is provided with several manual proportional multi-way valves corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve are respectively connected to the output end and the return oil tank of the hydraulic pump station; each of the bridge units also includes two composite control valve groups, each of which is simultaneously connected to the corresponding raising oil cylinder, the manual proportional multi-way valve and the A port and the B port, and the A port and the B port of the electro-hydraulic proportional multi-way valve group. The present application improves the operating stability of the tail system of the walking self-moving machine, including a dual operating system, one for use and one for backup, taking into account both simultaneous control and separate control modes, greatly improving the efficiency of troubleshooting and reducing maintenance costs.

Description

Technical Field

[0001] The present application relates to the technical field of engineering machinery and equipment, and in particular, to a step-type self-moving tail bridge raising cylinder control system. Background Art

[0002] The existing walking self-moving tail includes a tail body, a walking self-moving device and a power device. The walking self-moving device includes a plurality of lifting mechanisms, a wheel frame, a running wheel, a push cylinder and a movable ground rail installed on both sides of the tail body. The walking self-moving tail can move in two directions, level and adjust the body, and move with the transfer equipment through the power device. During coal mine construction, the walking self-moving tail can effectively reduce labor intensity and labor costs and greatly improve the efficiency of working face excavation.

[0003] At present, the lifting cylinders of the tail bridge lifting mechanism of the walking self-propelled machine are all controlled in parallel by the same multi-way valve, that is, after the action command is issued, all the lifting cylinders will act in sequence from light load to heavy load according to different loads. Finally, after all the lifting cylinders have moved to their full potential, the action command is stopped. In other words, the current control method of the lifting cylinders of the tail of the walking self-propelled machine adopts the method of total control of all cylinders acting simultaneously. This control method has the following shortcomings:

[0004] First, when the working surface is uneven, it is necessary to adjust the height of a single bridge, and it is impossible to control a single lifting cylinder separately;

[0005] Second, when the hydraulic control system of the tail lifting cylinder of the walking self-propelled machine fails, other cylinders cannot be blocked, which increases the difficulty and time of troubleshooting;

[0006] Third, the control system controls a large number of actuators at the same time, which affects the continuous working stability of the walking self-moving tail. Summary of the invention

[0007] The embodiment of the present application provides a step-type self-moving tail bridge raising cylinder control system to solve the technical problems that the existing step-type self-moving tail bridge lifting mechanism raising cylinder control system cannot be controlled independently, is difficult to troubleshoot, and has poor stability.

[0008] The technical solutions adopted in this application are as follows:

[0009] A step-type self-moving tail bridge raising cylinder control system includes a hydraulic pump station, an electro-hydraulic proportional multi-way valve group, and a plurality of bridge units connected by hydraulic pipelines, each bridge unit is provided with two raising cylinders, and also includes:

[0010] A manual proportional multi-way valve group is provided with a number of manual proportional multi-way valves corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve are respectively connected to the output end of the hydraulic pump station and the return oil tank;

[0011] Each of the bridge units also includes two compound control valve groups, each of which is simultaneously connected to the corresponding lifting cylinder, the manual proportional multi-way valve and the A and B ports, and the A and B ports of the electro-hydraulic proportional multi-way valve group, and is used to achieve individual action control of the lifting cylinder when the corresponding manual proportional multi-way valve is switched; and, when the electro-hydraulic proportional multi-way valve group is switched, achieve simultaneous action control of all the lifting cylinders at the tail of the walking type self-propelled machine.

[0012] Further, the compound control valve group includes a second two-way balancing valve and a third two-way balancing valve, the V1 port and V2 port of the second two-way balancing valve are respectively connected to the A port and B port of the corresponding manual proportional multi-way valve, and the C1 port and C2 port of the second two-way balancing valve are respectively connected to the rodless chamber and rod chamber of the corresponding lifting cylinder; the V1 port and V2 port of the third two-way balancing valve are respectively connected to the A port and B port of the electro-hydraulic controlled proportional multi-way valve group, and the C1 port and C2 port of the third two-way balancing valve are respectively connected to the rodless chamber and rod chamber of the same lifting cylinder.

[0013] Furthermore, the compound control valve group includes a second two-way hydraulic lock and a third two-way hydraulic lock, the V1 port and V2 port of the second two-way hydraulic lock are respectively connected to the A port and B port of the corresponding manual proportional multi-way valve, and the C1 port and C2 port of the second two-way hydraulic lock are respectively connected to the rodless chamber and rod chamber of the corresponding lifting cylinder; the V1 port and V2 port of the third two-way hydraulic lock are respectively connected to the A port and B port of the electro-hydraulic proportional multi-way valve group, and the C1 port and C2 port of the third two-way hydraulic lock are respectively connected to the rodless chamber and rod chamber of the same lifting cylinder.

[0014] Further, the compound control valve group includes a first shuttle valve, a second shuttle valve, and a first two-way balancing valve. The C1 port and C2 port of the first two-way balancing valve are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder. The P1 port of the first shuttle valve is connected to the B port of the electro-hydraulic proportional multi-way valve group. The P2 port of the first shuttle valve is connected to the A port of the corresponding manual proportional multi-way valve. The A port of the first shuttle valve is connected to the V1 port of the first two-way balancing valve. The P1 port of the second shuttle valve is connected to the A port of the electro-hydraulic proportional multi-way valve group. The P2 port of the second shuttle valve is connected to the B port of the corresponding manual proportional multi-way valve. The A port of the second shuttle valve is connected to the V2 port of the first two-way balancing valve.

[0015] Further, the compound control valve group includes a first shuttle valve, a second shuttle valve, and a first two-way hydraulic lock. The C1 port and C2 port of the first two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder, the P1 port of the first shuttle valve is connected to the B port of the electro-hydraulic proportional multi-way valve group, the P2 port of the first shuttle valve is connected to the A port of the corresponding manual proportional multi-way valve, and the A port of the first shuttle valve is connected to the V1 port of the first two-way hydraulic lock; the P1 port of the second shuttle valve is connected to the A port of the electro-hydraulic proportional multi-way valve group, the P2 port of the second shuttle valve is connected to the B port of the corresponding manual proportional multi-way valve, and the A port of the second shuttle valve is connected to the V2 port of the first two-way hydraulic lock.

[0016] Furthermore, a valve core initial position control device is connected to the pipeline between the A port and the B port of the electro-hydraulic controlled proportional multi-way valve group and the first shuttle valve and the second shuttle valve, so that the valve cores of the first shuttle valve and the second shuttle valve move to the side of the P2 port when the walking self-moving tail is in the standby state.

[0017] Further, the valve core initial position control device includes a hydraulic oil supply port, a first one-way valve, a second one-way valve, a third one-way valve, a fourth one-way valve, a first back-pressure valve, and a second back-pressure valve. The P ports of the third one-way valve and the fourth one-way valve are connected to the hydraulic oil supply port, the P ports of the first one-way valve and the second one-way valve are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group, the A port of the first one-way valve and the A port of the fourth one-way valve are both connected to the P1 port of the second shuttle valve; the A port of the second one-way valve and the A port of the third one-way valve are respectively connected to the P1 port of the first shuttle valve; the P ports of the first back-pressure valve and the second back-pressure valve are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group, and the A ports of the first back-pressure valve and the second back-pressure valve are respectively connected to the P1 ports of the second shuttle valve and the first shuttle valve.

[0018] Furthermore, the first back-pressure valve and the second back-pressure valve are back-pressure check valves, and the back-pressure check valves include a check valve and a spring arranged in the check valve, and the spring provides a certain elastic force to push the check valve against the P port of the check valve to put the check valve in a cut-off state;

[0019] or,

[0020] The first back pressure valve and the second back pressure valve are sequential valves with set opening pressure values;

[0021] or,

[0022] The first back-pressure valve and the second back-pressure valve are overflow valves with set opening pressure values.

[0023] Furthermore, it also includes a merging control valve group and a merging block, one of the input ends of the merging block is connected to the A port and the B port of the first electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group, and the output end is connected to each compound control valve group; the input end of the merging control valve group is connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group, and the output end is connected to the other input end of the merging block, and the merging control valve group controls the flow control of all the lifting cylinders at the same time through two hydraulically controlled one-way valves to achieve first and second gear speed regulation.

[0024] Further, the confluence control valve group includes a fourth two-way hydraulically controlled lock, the C1 port and the C2 port of the fourth two-way hydraulically controlled lock are respectively connected to the input end of the confluence block, and the V1 port and the V2 port of the fourth two-way hydraulically controlled lock are respectively connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group;

[0025] or,

[0026] The confluence control valve group includes a fourth two-way balancing valve, the C1 port and the C2 port of the fourth two-way balancing valve are respectively connected to the input end of the confluence block, and the V1 port and the V2 port of the fourth two-way balancing valve are respectively connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group.

[0027] Compared with the prior art, this application has the following beneficial effects:

[0028] The present application provides a control system for raising the oil cylinder of the bridge at the tail of a walking type self-moving machine, comprising a hydraulic pump station, an electro-hydraulic proportional multi-way valve group, and a plurality of bridge units connected by hydraulic pipelines, each of which is provided with two raising oil cylinders, and also comprising: a manual proportional multi-way valve group, which is provided with a plurality of manual proportional multi-way valves corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve are respectively connected to the output end and the return oil tank of the hydraulic pump station; each of the bridge units also comprises two compound control valve groups, each of which is simultaneously connected to the corresponding raising oil cylinder, the manual proportional multi-way valve and the A port and the B port, and the A port and the B port of the electro-hydraulic proportional multi-way valve group, and is used for realizing the individual action control of the raising oil cylinder when the corresponding manual proportional multi-way valve is switched; and, when the electro-hydraulic proportional multi-way valve group is switched, realizing the simultaneous action control of all the raising oil cylinders at the tail of the walking type self-moving machine. The present application realizes infinite adjustment of the vertical height of a single bridge by setting a manual proportional multi-way valve group and a compound control valve group on the basis of the original synchronous control. When the working surface is undulating, it can not only control simultaneously but also adjust the height of a single bridge individually, thereby improving the adaptability of the equipment. The present application shortens the troubleshooting time. Since a single lifting cylinder can be controlled individually, when a fault occurs, the source of the fault can be found more quickly. Compared with the original design scheme that requires sealing the lifting cylinders one by one, which consumes a lot of manpower and material resources, the troubleshooting efficiency is greatly improved and the maintenance costs such as manpower and material resources are reduced. The present application improves the operating stability of the step-type self-moving tail system, with dual operating systems, one for use and one for backup, taking into account both simultaneous control and individual control modes, effectively ensuring the stability and reliability of equipment operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] The drawings constituting a part of the present application are used to provide a further understanding of the present application. The illustrative embodiments and descriptions of the present application are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0030] Figure 1 It is a partial schematic diagram of the principle of the step-type self-moving tail bridge raising cylinder control system of the preferred embodiment of the present application.

[0031] Figure 2 It is a schematic diagram of the principles of the remaining parts of the step-type self-moving tail bridge raising cylinder control system of the preferred embodiment of the present application.

[0032] Figure 3 It is a schematic diagram of the structural principle of the composite control valve group of the preferred embodiment of the present application.

[0033] Figure 4 It is a partial principle schematic diagram of a step-type self-moving tail bridge raising cylinder control system of another preferred embodiment of the present application.

[0034] Figure 5 It is a schematic diagram of the principles of the remaining parts of the step-type self-moving tail bridge raising cylinder control system of another preferred embodiment of the present application.

[0035] In the figure:

[0036] 1. Hydraulic pump station; 2. Electro-hydraulic proportional multi-way valve group; 3. Confluence control valve group; 4. Confluence block; 5. Valve core initial position control device; 5.1. First one-way valve; 5.2. Second one-way valve; 5.3. Third one-way valve; 5.4. Fourth one-way valve; 6.1. First back pressure valve; 6.2. Second back pressure valve; 7. Hydraulic oil supply port; 8. Manual proportional multi-way valve group; 8.1. Manual proportional multi-way valve; 9.1. First shuttle valve; 9.2. Second shuttle valve; 10. First two-way balancing valve; 11. Lifting cylinder; 13. Second two-way balancing valve; 14. Third two-way balancing valve. DETAILED DESCRIPTION

[0037] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0038] Reference Figure 1 and Figure 2 The preferred embodiment of the present application provides a step-type self-propelled tail bridge lifting cylinder control system, including a hydraulic pump station 1, an electro-hydraulic proportional multi-way valve group 2, and a plurality of bridge units connected by hydraulic pipelines, each bridge unit is provided with two lifting cylinders 11, and also includes:

[0039] The manual proportional multi-way valve group 8 is provided with a number of manual proportional multi-way valves 8.1 corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve 8.1 are respectively connected to the output end and the return oil tank of the hydraulic pump station 1;

[0040] Each of the bridge units also includes two compound control valve groups, each of which is simultaneously connected to the corresponding lifting cylinder 11, the manual proportional multi-way valve 8.1 and the A port and the B port, and the A port and the B port of the electro-hydraulic proportional multi-way valve group 2, and is used to realize the individual action control of the lifting cylinder 11 when the corresponding manual proportional multi-way valve 8.1 is switched; and when the electro-hydraulic proportional multi-way valve group 2 is switched, it is used to realize the simultaneous action control of all the lifting cylinders 11 at the tail of the walking type self-propelled machine.

[0041] The present embodiment provides a control system for raising the cylinder of the bridge at the tail of a walking-type self-moving machine, comprising a hydraulic pump station, an electro-hydraulic proportional multi-way valve group, and a plurality of bridge units connected by hydraulic pipelines, each of which is provided with two raising cylinders, and also comprising: a manual proportional multi-way valve group, which is provided with a plurality of manual proportional multi-way valves corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve are respectively connected to the output end and the return oil tank of the hydraulic pump station; each of the bridge units also comprises two compound control valve groups, each of which is simultaneously connected to the corresponding raising cylinder, the manual proportional multi-way valve and the A port and the B port, and the A port and the B port of the electro-hydraulic proportional multi-way valve group, for realizing the individual action control of the raising cylinder when the corresponding manual proportional multi-way valve performs the switching action; and, when the electro-hydraulic proportional multi-way valve group performs the switching action, realizing the simultaneous action control of all the raising cylinders at the tail of the walking-type self-moving machine. This embodiment realizes the stepless adjustment of the vertical height of a single bridge by setting a manual proportional multi-way valve group and a compound control valve group on the basis of the original synchronous control. When the working surface is undulating, it can not only control simultaneously, but also adjust the height of a single bridge individually, thereby improving the adaptability of the equipment. This embodiment shortens the troubleshooting time. Since a single lifting cylinder can be controlled individually, when a fault occurs, the source of the fault can be found more quickly. Compared with the original design scheme that requires sealing the lifting cylinders one by one, which consumes a lot of manpower and material resources, this greatly improves the troubleshooting efficiency and reduces the maintenance costs such as manpower and material resources. This embodiment improves the operating stability of the step-type self-moving tail system, dual operating systems, one for use and one for backup, taking into account both simultaneous control and individual control modes, effectively ensuring the stability and reliability of equipment operation.

[0042] like Figure 1 and Figure 2 As shown, in a preferred embodiment of the present application, the compound control valve group includes a first shuttle valve 9.1, a second shuttle valve 9.2, and a first two-way balancing valve 10, the C1 port and C2 port of the first two-way balancing valve 10 are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder 11, the P1 port of the first shuttle valve 9.1 is connected to the B port of the electro-hydraulic proportional multi-way valve group 2, the P2 port of the first shuttle valve 9.1 is connected to the A port of the corresponding manual proportional multi-way valve 8.1, and the A port of the first shuttle valve 9.1 is connected to the V1 port of the first two-way balancing valve 10; the P1 port of the second shuttle valve 9.2 is connected to the A port of the electro-hydraulic proportional multi-way valve group 2, the P2 port of the second shuttle valve 9.2 is connected to the B port of the corresponding manual proportional multi-way valve 8.1, and the A port of the second shuttle valve 9.2 is connected to the V2 port of the first two-way balancing valve 10.

[0043] like Figure 1As shown, in a preferred embodiment of the present application, the compound control valve group includes a first shuttle valve 9.1, a second shuttle valve 9.2, and a first two-way hydraulic lock. The C1 port and C2 port of the first two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder 11, the P1 port of the first shuttle valve 9.1 is connected to the B port of the electro-hydraulic proportional multi-way valve group 2, the P2 port of the first shuttle valve 9.1 is connected to the A port of the corresponding manual proportional multi-way valve 8.1, and the A port of the first shuttle valve 9.1 is connected to the V1 port of the first two-way hydraulic lock; the P1 port of the second shuttle valve 9.2 is connected to the A port of the electro-hydraulic proportional multi-way valve group 2, the P2 port of the second shuttle valve 9.2 is connected to the B port of the corresponding manual proportional multi-way valve 8.1, and the A port of the second shuttle valve 9.2 is connected to the V2 port of the first two-way hydraulic lock.

[0044] In a preferred embodiment of the present application, a valve core initial position control device 5 is also connected to the pipeline between the A port and the B port of the electro-hydraulic controlled proportional multi-way valve group 2 and the first shuttle valve 9.1 and the second shuttle valve 9.2, which moves the valve cores of the first shuttle valve 9.1 and the second shuttle valve 9.2 to the side of the P2 port when the walking self-propelled tail is in a standby state, so that in the standby state, the valve cores of the first shuttle valve 9.1 and the second shuttle valve 9.2 are at the P2 port position on the right side, ensuring that the subsequent hydraulic oil can flow into the preset pipeline through the first shuttle valve 9.1 and the second shuttle valve 9.2.

[0045] Specifically, Figure 2As shown, in a preferred embodiment of the present application, the valve core initial position control device 5 includes a hydraulic oil supply port, a first one-way valve 5.1, a second one-way valve 5.2, a third one-way valve 5.3, a fourth one-way valve 5.4, a first back pressure valve 6.1, and a second back pressure valve 6.2. The P ports of the third one-way valve 5.3 and the fourth one-way valve 5.4 are both connected to the hydraulic oil supply port, the P ports of the first one-way valve 5.1 and the second one-way valve 5.2 are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group 2, and the A port of the first one-way valve 5.1 is connected to the fourth one-way valve 5.4. The A port of the second check valve 5.2 is connected to the P1 port of the second shuttle valve 9.2; the A port of the second check valve 5.2 is connected to the A port of the third check valve 5.3 and the P1 port of the first shuttle valve 9.1; the P ports of the first back pressure valve 6.1 and the second back pressure valve 6.2 are connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group 2 respectively, and the A ports of the first back pressure valve 6.1 and the second back pressure valve 6.2 are connected to the P1 ports of the second shuttle valve 9.2 and the first shuttle valve 9.1 respectively. The hydraulic oil supply port does not require too much pressure, so an ordinary gear pump can be used to output the hydraulic oil. The first back pressure valve 6.1 and the second back pressure valve 6.2 can provide a certain back pressure, so that in the standby state, the hydraulic oil in the pipeline between the output end of the gear pump and the first shuttle valve 9.1 and the second shuttle valve 9.2 maintains a suitable pressure, so that the valve cores of the first shuttle valve 9.1 and the second shuttle valve 9.2 are at the P2 port position on the right.

[0046] Alternatively, if Figure 2 As shown, the first back-pressure valve 6.1 and the second back-pressure valve 6.2 are back-pressure one-way valves, which include a one-way valve and a spring arranged inside the one-way valve. The spring provides a certain elastic force to push the one-way valve against the P port of the one-way valve to put the one-way valve in a cut-off state.

[0047] Optionally, in a preferred embodiment of the present application, the first back-pressure valve 6.1 and the second back-pressure valve 6.2 are sequential valves with set opening pressure values.

[0048] Optionally, in a preferred embodiment of the present application, the first back-pressure valve 6.1 and the second back-pressure valve 6.2 are overflow valves with set opening pressure values.

[0049] like Figure 3As shown, in a preferred embodiment of the present application, the compound control valve group includes a second two-way balancing valve 13 and a third two-way balancing valve 14, the V1 port and V2 port of the second two-way balancing valve 13 are respectively connected to the A port and B port of the corresponding manual proportional multi-way valve 8.1, and the C1 port and C2 port of the second two-way balancing valve 13 are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder 11; the V1 port and V2 port of the third two-way balancing valve 14 are respectively connected to the A port and B port of the electro-hydraulic proportional multi-way valve group 2, and the C1 port and C2 port of the third two-way balancing valve 14 are respectively connected to the rodless chamber and the rod chamber of the same lifting cylinder 11.

[0050] In another preferred embodiment of the present application, the compound control valve group includes a second two-way hydraulic lock and a third two-way hydraulic lock, the V1 port and V2 port of the second two-way hydraulic lock are respectively connected to the A port and B port of the corresponding manual proportional multi-way valve 8.1, and the C1 port and C2 port of the second two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder 11; the V1 port and V2 port of the third two-way hydraulic lock are respectively connected to the A port and B port of the electro-hydraulic proportional multi-way valve group 2, and the C1 port and C2 port of the third two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the same lifting cylinder 11. This embodiment uses a two-way hydraulic lock to replace the two-way balancing valve to perform similar functions.

[0051] like Figure 2 and Figure 4 As shown, in a preferred embodiment of the present application, the control system further includes a merging control valve group 3 and a merging block 4, one of the input ends of the merging block 4 is connected to the A port and the B port of the first electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group 2, and the output end is connected to each compound control valve group; the input end of the merging control valve group 3 is connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group 2, and the output end is connected to the other input end of the merging block 4, and the merging control valve group 3 controls all the lifting cylinders through two hydraulically controlled one-way valves at the same time to perform flow control to achieve first and second gear speed regulation.

[0052] The function of the merging control valve group 3 of this embodiment is to realize the first and second speed adjustment of all the lifting cylinders at the same time, realize the external merging of the second and third joint valves of the middle Y-shaped functional multi-way valve, meet the flow demand, and realize the first and second speed adjustment. The function of the merging block 3 is to realize the convenience of installation of the merging pipeline outside the valve and reduce the number of pipelines and joints used.

[0053] Specifically, Figure 2 and Figure 4As shown, the confluence control valve group 3 includes a fourth two-way hydraulically controlled lock, and the C1 port and C2 port of the fourth two-way hydraulically controlled lock are respectively connected to the input end of the confluence block 4, and the V1 port and V2 port of the fourth two-way hydraulically controlled lock are respectively connected to the A port and B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic controlled proportional multi-way valve group 2.

[0054] The confluence control valve group 3 of this embodiment realizes the first and second gear speed adjustment of simultaneously controlling all the lifting cylinders through a two-way hydraulic control lock, realizes the external confluence of the second and third valves of the mid-position Y-type functional multi-way valve, meets the flow demand, and thus realizes the first and second gear speed adjustment.

[0055] In a preferred embodiment of the present application, the confluence control valve group 3 includes a fourth two-way balancing valve, and the C1 port and C2 port of the fourth two-way balancing valve are respectively connected to the input end of the confluence block 4, and the V1 port and V2 port of the fourth two-way balancing valve are respectively connected to the A port and B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group 2.

[0056] Different from the above-mentioned embodiment, the confluence control valve group 3 of this embodiment realizes the first and second gear speed regulation of simultaneously controlling all the lifting cylinders through a two-way balancing valve, realizes the external confluence of the second and third valves of the mid-position Y-type functional multi-way valve, meets the flow demand, and thus realizes the first and second gear speed regulation.

[0057] Below Figure 1 and Figure 2 The working principle of the cylinder control system is described in detail as shown in the figure:

[0058] The lifting cylinder control system can realize two modes of simultaneous action control and individual action control of the lifting cylinders. The main working principle is as follows:

[0059] When the oil cylinder 11 is raised to extend in the simultaneous action control mode, the oil flows out through the hydraulic pump station 1 and enters the inside of the electro-hydraulic proportional multi-way valve group 2. When the second and third units of the electro-hydraulic proportional multi-way valve group 2 are working in the lower position, the oil passes through the B2 port and B3 port of the electro-hydraulic proportional multi-way valve group 2 respectively. The oil at the B3 port enters through the V2 port of the confluence control valve group 3 and flows out from the C2 port, and finally merges with the oil at the B2 port inside the confluence block 4. After the confluence, the hydraulic pressure is divided into two paths, one path enters the second back pressure valve 6.2. Since the second back pressure valve 6.2 is closed in reverse, the oil is sealed here. The second path flows through the second check valve 5.2 and enters the outlet of the third check valve 5.3. Since the check valve is closed in reverse, the oil is sealed here. One path passes through the main pipeline and is connected to the confluence block 4. The left P1 port of the first shuttle valve 9.1 enters the V1 port of all the first two-way balancing valves 10, and the oil flows into the rodless chamber of the lifting cylinder 11 through the V1 port. At the same time, the pilot oil flows into the V2 port, so that the oil flows from the rod chamber of the lifting cylinder 11 to the V2 port of the first two-way balancing valve 10, and then flows into the A port in the middle of the second shuttle valve 9.2, and enters the return oil chamber of the confluence block 4 through the left P1 port of the second shuttle valve 9.2. The oil enters the A3 port of the third joint of the electro-hydraulic proportional multi-way valve group 2 from the return oil chamber through the C1 port of the confluence control valve group 3, and the second way directly flows into the A2 port of the second joint of the electro-hydraulic proportional multi-way valve group 2, and finally enters the oil tank through the return oil. The principle of the simultaneous extension action of another lifting cylinder 11 located in the same bridge unit is the same.

[0060] When the oil cylinder 11 is raised and retracted in the simultaneous action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the electro-hydraulic proportional multi-way valve group 2. The second and third units of the electro-hydraulic proportional multi-way valve group 2 work in the upper position, and the oil passes through the A2 port and A3 port of the electro-hydraulic proportional multi-way valve group 2 respectively. The oil at the A3 port enters through the V1 port of the confluence control valve group 3 and flows out from the C1 port, and finally merges with the oil at the A2 port inside the confluence block 4. After the confluence, the hydraulic pressure is divided into two paths, one path enters the first back pressure valve 6.1. Since the first back pressure valve 6.1 is closed in reverse, the oil is sealed here. After the second path flows through the first non-return valve 5.1, one path enters the fourth non-return valve 5.4. Since the non-return valve is closed in reverse, the oil is sealed here. The other path passes through the main path. , enters the V2 ports of all the first two-way balancing valves 10 from the left P1 ports of all the second shuttle valves 9.2, and the oil flows into the rod chambers of all the lifting cylinders 11 through the V2 ports. At the same time, the pilot oil flows into the V1 port, so that the oil flows from the rodless chamber of the lifting cylinder 11 to the V1 port balancing valve of the first two-way balancing valve 10, and then enters the return oil chamber of the confluence block 4 through the left P1 port of the first shuttle valve 9.1. The oil enters the B3 port of the third joint of the electro-hydraulic proportional multi-way valve group 2 through the C2 port of the confluence control valve group 3 from the return oil chamber, and the second way directly flows into the B2 port of the second joint of the electro-hydraulic proportional multi-way valve group 2, and finally enters the oil tank through the return oil. The principle of the simultaneous retraction of another lifting cylinder 11 located in the same bridge unit is the same.

[0061] When the lifting cylinder 11 performs the extension action in the single action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the manually operated multi-way valve group 8. When the corresponding manual proportional multi-way valve 8.1 in the manually operated multi-way valve group 8 is in the lower position, the oil enters the V1 port of the first two-way balance valve 10 through the A1 port of the manual proportional multi-way valve 8.1 and the right side P2 port of the first shuttle valve 9.1 in turn, and the oil flows into the rodless cavity of the lifting cylinder 11 through the V1 port. At the same time, a pilot oil flows into the V2 port, so that the oil in the rod cavity of the lifting cylinder 11 enters the return oil cavity of the confluence block 4 through the V2 port of the first two-way balance valve 10 and the left side P1 port of the second shuttle valve 9.2 in turn, and the oil directly flows into the A2 port of the second joint of the electro-hydraulic proportional multi-way valve group 2 and finally enters the oil tank through the return oil. The principle of the other lifting cylinder 11 located in the same bridge unit performing a single extension action is the same.

[0062] When the lifting cylinder retracts in the single action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the manually operated multi-way valve group 8. When the corresponding manual proportional multi-way valve 8.1 in the manually operated multi-way valve group 8 is in the upper position, the oil enters the V2 port of the first two-way balancing valve 10 through the B1 port of the manually operated multi-way valve 8.1 and the right P2 port of the second shuttle valve 9.2 in turn, and the oil flows into the rod chamber of the lifting cylinder 11 through the V2 port. At the same time, a pilot oil flows into the V1 port, so that the oil in the rodless chamber of the lifting cylinder 11 enters the return oil chamber of the confluence block 4 through the V1 port of the first two-way balancing valve 10 and the left P1 port of the first shuttle valve 9.1 in turn, and the oil directly flows into the B2 port of the second joint of the electro-hydraulic proportional multi-way valve group 2 and finally enters the oil tank through the return oil. The principle of the other lifting cylinder 11 located in the same bridge unit performing a single retraction action is the same.

[0063] When the whole system is in standby state, in order to ensure that the first shuttle valve 9.1 and the second shuttle valve 9.2 are in the right position to work and prevent the throttling of the large flow return oil in the simultaneous action mode, the hydraulic oil supply port 7 uses a gear pump to output the hydraulic oil and enters the corresponding pipeline through the third check valve 5.3 and the fourth check valve 5.4 respectively. Since the first check valve 5.1 and the second check valve 5.2 are reversely locked, the oil can only reach the left P1 port of the first shuttle valve 9.1 and the second shuttle valve 9.2 through the main oil circuit, and then enter the V1 and V2 ports of the first two-way balance valve 10. Since the setting value of the balance valve is much greater than the oil replenishment pressure value, the first two-way balance valve 10 cannot be opened, and the oil is locked here. The second path overcomes the springs of the first back pressure valve 6.1 and the second back pressure valve 6.2, and returns to the oil tank through the middle position of the electro-hydraulic proportional multi-way valve group 2. At this time, the first shuttle valve 9.1 and the second shuttle valve 9.2 are both in the right position holding state.

[0064] Below Figures 3 to 5 The working principle of the cylinder control system is described in detail as shown in:

[0065] The lifting cylinder control system can realize two modes of simultaneous action control and individual action control of the lifting cylinders. The main working principle is as follows:

[0066] When the lifting cylinder 11 retracts in the single action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the manually operated multi-way valve group 8. When the corresponding manual proportional multi-way valve 8.1 in the manually operated multi-way valve group 8 is in the upper position, the oil enters the V2 port of the second two-way balancing valve 13 through the B1 port of the manually operated multi-way valve 8.1 in turn, and then flows into the rod chamber of the lifting cylinder 11 through the C2 port. At the same time, the oil in the rodless chamber of the lifting cylinder 11 flows back to the A1 port of the manual proportional multi-way valve 8.1 through the C1 port and V1 port of the second two-way balancing valve 13 in turn, circulates inside the valve body, and returns to the hydraulic oil tank to realize the retraction action of the lifting cylinder 11. The second two-way balancing valve 13 can realize the oil return control of the rodless chamber of the lifting cylinder 11 to prevent speed loss. The principle of the other lifting cylinder 11 located in the same bridge unit performing a single retraction action is the same.

[0067] When the lifting cylinder 11 is extended in the single action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the manually operated multi-way valve group 8. When the corresponding manual proportional multi-way valve 8.1 in the manually operated multi-way valve group 8 is in the upper working position, the oil enters the V1 port of the second two-way balancing valve 13 through the A1 port of the manually operated multi-way valve 8.1 in turn, and then flows into the rodless chamber of the lifting cylinder 11 through the C1 port. At the same time, the oil in the rod chamber of the lifting cylinder 11 flows back to the B1 port of the manual proportional multi-way valve 8.1 through the C2 port and V2 port of the second two-way balancing valve 13 in turn, circulates inside the valve body, and returns to the hydraulic oil tank to realize the extension action of the lifting cylinder 11. The second two-way balancing valve 13 can realize the oil return control of the rod chamber of the lifting cylinder 11 to prevent speed loss. The principle of the other lifting cylinder 11 located in the same bridge unit performing a single extension action is the same.

[0068] When the oil cylinder 11 is raised and retracted in the simultaneous action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the electro-hydraulic proportional multi-way valve group 2. The second electro-hydraulic proportional multi-way valve and the third electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2 work in the upper position. At this time, one line of oil enters the inlet of the confluence block 4 from the B2 port of the second electro-hydraulic proportional multi-way valve, and the other line of oil enters the interior of the confluence control valve group 3 from the B3 port of the third electro-hydraulic proportional multi-way valve. After the two lines of oil merge in the confluence block 4, they flow through the oil circuit to the V2 port of the third two-way balancing valve 14 of all the compound control valve groups, and then pass through the third two-way balancing valve 14. The C2 port flows into the rod chamber of the lifting cylinder 11, and at the same time, the oil in the rodless chamber of the lifting cylinder 11 flows into the merging block 4 through the C1 port and the V1 port of the third two-way balancing valve 14 in turn. Then, the oil is divided into two paths. One path passes through the A2 port of the second electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2, circulates inside the valve body, and returns to the hydraulic oil tank. The other path passes through the opened hydraulic one-way valve in the merging control valve group 3, enters the A3 port of the third electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2, circulates inside the valve body, and returns to the hydraulic oil tank, thereby realizing the retraction action of the lifting cylinder 11. The retraction action mechanism of all lifting cylinders 11 is the same.

[0069] When the oil cylinder 11 is extended in the simultaneous action control mode, the oil flows out through the hydraulic pump station 1 and enters the interior of the electro-hydraulic proportional multi-way valve group 2. The second electro-hydraulic proportional multi-way valve and the third electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2 work in the lower position. At this time, one oil path enters the inlet of the confluence block 4 from the A2 port of the second electro-hydraulic proportional multi-way valve, and the other oil path enters the interior of the confluence control valve group 3 from the A3 port of the third electro-hydraulic proportional multi-way valve. After the two oil paths merge in the confluence block 4, they flow through the oil circuit to the V1 port of the third two-way balancing valve 14 of all the compound control valve groups, and then flow through the third two-way balancing valve 14. The C1 port flows into the rodless chamber of the lifting cylinder 11, and at the same time, the oil in the rod chamber of the lifting cylinder 11 flows into the confluence block 4 through the C2 port and the V2 port of the third two-way balancing valve 14 in turn. Then, the oil is divided into two paths. One path passes through the B2 port of the second electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2, circulates through the valve body, and returns to the hydraulic oil tank. The other path passes through the opened hydraulic one-way valve in the confluence control valve group 3, enters the B3 port of the third electro-hydraulic proportional multi-way valve of the electro-hydraulic proportional multi-way valve group 2, circulates through the valve body, and returns to the hydraulic oil tank, thereby realizing the extension action of the lifting cylinder 11. The extension action mechanism of all lifting cylinders 11 is the same.

[0070] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application should be included in the protection scope of the present application.

Claims

1. A walking type self-moving tail bridge lifting cylinder control system, comprising a hydraulic pump station (1), an electro-hydraulic proportional multi-way valve group (2), and a plurality of bridge units connected by hydraulic pipelines, each bridge unit being provided with two lifting cylinders (11), characterized in that: Also includes: A manual proportional multi-way valve group (8) is provided with a number of manual proportional multi-way valves (8.1) corresponding to the number of the bridge units, and the P port and T port of each manual proportional multi-way valve (8.1) are respectively connected to the output end and the oil return tank of the hydraulic pump station (1); Each of the bridge units also includes two compound control valve groups, each of which is simultaneously connected to the corresponding lifting cylinder (11), the manual proportional multi-way valve (8.1) and the A port and the B port, and the A port and the B port of the electro-hydraulic proportional multi-way valve group (2), and is used to realize the individual action control of the lifting cylinder (11) when the corresponding manual proportional multi-way valve (8.1) is switched; and to realize the simultaneous action control of all the lifting cylinders (11) at the tail of the walking self-propelled machine when the electro-hydraulic proportional multi-way valve group (2) is switched.

2. The walking type self-moving tail bridge raising cylinder control system according to claim 1 is characterized in that: The composite control valve group comprises a second two-way balancing valve (13) and a third two-way balancing valve (14); the V1 port and the V2 port of the second two-way balancing valve (13) are respectively connected to the A port and the B port of the corresponding manual proportional multi-way valve (8.1); the C1 port and the C2 port of the second two-way balancing valve (13) are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder (11); the V1 port and the V2 port of the third two-way balancing valve (14) are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group (2); the C1 port and the C2 port of the third two-way balancing valve (14) are respectively connected to the rodless chamber and the rod chamber of the same lifting cylinder (11).

3. The walking type self-moving tail bridge raising cylinder control system according to claim 1 is characterized in that: The composite control valve group includes a second two-way hydraulic lock and a third two-way hydraulic lock. The V1 port and V2 port of the second two-way hydraulic lock are respectively connected to the A port and B port of the corresponding manual proportional multi-way valve (8.1), and the C1 port and C2 port of the second two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder (11); the V1 port and V2 port of the third two-way hydraulic lock are respectively connected to the A port and B port of the electro-hydraulic proportional multi-way valve group (2), and the C1 port and C2 port of the third two-way hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the same lifting cylinder (11).

4. The walking type self-moving tail bridge raising cylinder control system according to claim 1 is characterized in that: The composite control valve group comprises a first shuttle valve (9.1), a second shuttle valve (9.2), and a first two-way balancing valve (10); the C1 port and the C2 port of the first two-way balancing valve (10) are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder (11); the P1 port of the first shuttle valve (9.1) is connected to the B port of the electro-hydraulic proportional multi-way valve group (2); the P2 port of the first shuttle valve (9.1) is connected to the A port of the corresponding manual proportional multi-way valve (8.1); the A port of the first shuttle valve (9.1) is connected to the V1 port of the first two-way balancing valve (10); the P1 port of the second shuttle valve (9.2) is connected to the A port of the electro-hydraulic proportional multi-way valve group (2); the P2 port of the second shuttle valve (9.2) is connected to the B port of the corresponding manual proportional multi-way valve (8.1); and the A port of the second shuttle valve (9.2) is connected to the V2 port of the first two-way balancing valve (10).

5. The walking type self-moving tail bridge raising cylinder control system according to claim 1 is characterized in that: The composite control valve group comprises a first shuttle valve (9.1), a second shuttle valve (9.2), and a first bidirectional hydraulic lock. The C1 port and C2 port of the first bidirectional hydraulic lock are respectively connected to the rodless chamber and the rod chamber of the corresponding lifting cylinder (11); the P1 port of the first shuttle valve (9.1) is connected to the B port of the electro-hydraulic proportional multi-way valve group (2); the P2 port of the first shuttle valve (9.1) is connected to the A port of the corresponding manual proportional multi-way valve (8.1); the A port of the first shuttle valve (9.1) is connected to the V1 port of the first bidirectional hydraulic lock; the P1 port of the second shuttle valve (9.2) is connected to the A port of the electro-hydraulic proportional multi-way valve group (2); the P2 port of the second shuttle valve (9.2) is connected to the B port of the corresponding manual proportional multi-way valve (8.1); the A port of the second shuttle valve (9.2) is connected to the V2 port of the first bidirectional hydraulic lock.

6. The step-type self-moving tail bridge raising cylinder control system according to claim 4 or 5 is characterized in that: A valve core initial position control device (5) is also connected to the pipeline between the A port and the B port of the electro-hydraulic controlled proportional multi-way valve group (2) and the first shuttle valve (9.1) and the second shuttle valve (9.2) so as to move the valve cores of the first shuttle valve (9.1) and the second shuttle valve (9.2) to the side of the P2 port when the walking self-propelled tail is in a standby state.

7. The walking type self-moving tail bridge raising cylinder control system according to claim 6 is characterized in that: The valve core initial position control device (5) comprises a hydraulic oil supply port (7), a first one-way valve (5.1), a second one-way valve (5.2), a third one-way valve (5.3), a fourth one-way valve (5.4), a first back pressure valve (6.1), and a second back pressure valve (6.2). The P ports of the third one-way valve (5.3) and the fourth one-way valve (5.4) are both connected to the hydraulic oil supply port (7). The P ports of the first one-way valve (5.1) and the second one-way valve (5.2) are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group (2). The first one-way valve (5.1) and the second one-way valve (5.2) are respectively connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group (2). The A port of the first back-pressure valve (6.1) and the A port of the second back-pressure valve (6.2) are connected to the P1 port of the second shuttle valve (9.2); the A port of the second back-pressure valve (5.2) and the A port of the third back-pressure valve (5.3) are connected to the P1 port of the first shuttle valve (9.1); the P ports of the first back-pressure valve (6.1) and the second back-pressure valve (6.2) are connected to the A port and the B port of the electro-hydraulic proportional multi-way valve group (2), respectively, and the A ports of the first back-pressure valve (6.1) and the second back-pressure valve (6.2) are connected to the P1 ports of the second shuttle valve (9.2) and the first shuttle valve (9.1), respectively.

8. The walking type self-moving tail bridge raising cylinder control system according to claim 7 is characterized in that: The first back pressure valve (6.1) and the second back pressure valve (6.2) are back pressure check valves, the back pressure check valves comprising a check valve and a spring arranged inside the check valve, the spring providing a certain elastic force to push the check valve against the P port of the check valve so that the check valve is in a cut-off state; or, The first back pressure valve (6.1) and the second back pressure valve (6.2) are sequential valves with set opening pressure values; or, The first back pressure valve (6.1) and the second back pressure valve (6.2) are overflow valves with set opening pressure values.

9. The walking type self-moving tail bridge raising cylinder control system according to claim 1 is characterized in that: It also comprises a merging control valve group (3) and a merging block (4); one of the input ends of the merging block (4) is connected to the A port and the B port of the first electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group (2), and the output end is connected to each composite control valve group; the input end of the merging control valve group (3) is connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group (2), and the output end is connected to the other input end of the merging block (4); the merging control valve group (3) controls all the lifting cylinders through two hydraulically controlled one-way valves to simultaneously control the flow rate and realize first and second gear speed regulation.

10. The walking type self-moving tail bridge raising cylinder control system according to claim 9 is characterized in that: The confluence control valve group (3) comprises a fourth two-way hydraulically controlled lock, wherein the C1 port and the C2 port of the fourth two-way hydraulically controlled lock are respectively connected to the input end of the confluence block (4), and the V1 port and the V2 port of the fourth two-way hydraulically controlled lock are respectively connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group (2); or, The confluence control valve group (3) comprises a fourth two-way balancing valve, wherein the C1 port and the C2 port of the fourth two-way balancing valve are respectively connected to the input end of the confluence block (4), and the V1 port and the V2 port of the fourth two-way balancing valve are respectively connected to the A port and the B port of the second electro-hydraulic proportional multi-way valve in the electro-hydraulic proportional multi-way valve group (2).

Images