Hydraulic system for slotted lattice girder trolley, slotted lattice girder trolley

Abstract

The application discloses a hydraulic system of a slotted lattice girder trolley and the slotted lattice girder trolley, and the hydraulic system provides a working oil source for a plurality of hydraulic driving elements of the slotted lattice girder trolley through two main pumps and four multi-way valves, can realize a single connection or combined double joint and oil supply connection mode, and is high in integration degree and low in cost. In addition, since a large arm pitching oil cylinder and a milling and digging head rotary motor are in a long-time and large-flow working state, the application simultaneously supplies oil to the large arm pitching oil cylinder and the milling and digging head rotary motor through the two main pumps, so that the system hydraulic power loss is less during working, and the two-pump confluence can avoid the problem that the function of an executing element is affected due to insufficient flow.

Description

Technical Field

[0001] This invention relates to the field of slotted lattice beam trolley technology, and in particular, to a hydraulic system for a slotted lattice beam trolley. Furthermore, it also relates to a slotted lattice beam trolley employing the aforementioned hydraulic system. Background Technology

[0002] The slotting lattice beam integrated operation trolley, as an important component of the supporting equipment for precast lattice beam slope protection construction, can excavate trenches on flat slopes, remove debris during or after trench excavation, and also grab and install precast lattice beams, greatly improving the efficiency of slope protection construction and shortening the construction cycle. During construction, the slotting lattice beam trolley needs to perform multiple actions, including walking, boom pitching, boom secondary / tertiary extension, chassis rotation, milling head rotation, sliding trolley extension and retraction, milling head advance, forearm secondary / tertiary extension and retraction, outrigger extension and retraction, boom support extension and retraction, and forearm rotation. Each action is powered by a corresponding hydraulic drive component. However, current slotting lattice beam trolleys generally use multiple hydraulic systems to control different hydraulic drive components separately; for example, the walking system has a separate hydraulic system, the boom system has a separate hydraulic system, and the forearm system has a separate hydraulic system. The overall hydraulic system of the vehicle is overly complex, has low integration, and high configuration costs. Summary of the Invention

[0003] This invention provides a hydraulic system for a slotted lattice beam trolley and a slotted lattice beam trolley, to solve the technical problems of complex hydraulic systems and high configuration costs of existing slotted lattice beam trolleys.

[0004] According to one aspect of the present invention, a hydraulic system for a slotted lattice beam trolley is provided, comprising a first main pump, a second main pump, a first multi-way valve, a second multi-way valve, a third multi-way valve, and a fourth multi-way valve. The first and second main pumps are connected in series. The first main pump is connected to the first and third multi-way valves respectively. The second main pump is connected to the second and fourth multi-way valves respectively. The first multi-way valve is connected to the left travel motor, the boom pitch cylinder, the boom secondary telescopic cylinder, and the boom tertiary telescopic cylinder respectively. The second multi-way valve is connected to the boom pitch cylinder, the chassis slewing motor, and the right travel motor respectively. The third multi-way valve is connected to the milling head slewing motor, the sliding trolley telescopic cylinder, the milling head advance cylinder, the forearm secondary telescopic cylinder, and the forearm tertiary telescopic cylinder respectively. The fourth multi-way valve is connected to the milling head slewing motor, the slotting outrigger telescopic cylinder, the boom support telescopic cylinder, and the forearm slewing motor respectively.

[0005] Furthermore, it also includes a pilot oil pump, a first pilot proportional pressure reducing valve group, a second pilot proportional pressure reducing valve group, and an electronic control module. The pilot oil pump is connected to the first pilot proportional pressure reducing valve group and the second pilot proportional pressure reducing valve group. The first pilot proportional pressure reducing valve group is connected to each of the first multi-way valve and the third multi-way valve. The second pilot proportional pressure reducing valve group is connected to each of the second multi-way valve and the fourth multi-way valve. The electronic control module is electrically connected to the first pilot proportional pressure reducing valve group and the second pilot proportional pressure reducing valve group respectively, and is used to control the outlet pressure of the two pilot proportional pressure reducing valve groups, thereby controlling the valve opening of each link of each multi-way valve.

[0006] Furthermore, it also includes a first pilot proportional pressure reducing valve and a second pilot proportional pressure reducing valve electrically connected to the electronic control module. The first pilot proportional pressure reducing valve is connected to the first main pump, and the second pilot proportional pressure reducing valve is connected to the second main pump. The electronic control module is also used to control the displacement of the two main pumps respectively through the two pilot proportional pressure reducing valves.

[0007] Furthermore, both the first and second main pumps are constant power pumps, and the two main pumps are subject to cross total power control.

[0008] Furthermore, the electronic control module is controlled by a remote control handle. By converting the input angle of the remote control handle into an electrical control signal, the outlet pressure of the pilot proportional pressure reducing valve assembly is controlled.

[0009] Furthermore, the first and second main pumps adopt positive flow control, which controls the working pressure and flow of the entire hydraulic system by adjusting the output flow of the first and second main pumps.

[0010] Furthermore, it also includes a travel pilot directional valve, and the pilot oil pump is also connected to the travel pilot directional valve.

[0011] Furthermore, it also includes a mode-piloted directional valve, and the pilot oil pump is also connected to the mode-piloted directional valve.

[0012] Furthermore, it also includes a high-low speed switching valve, and the pilot oil pump is also connected to the high-low speed switching valve.

[0013] In addition, the present invention also provides a slotted lattice beam trolley, which employs the hydraulic system described above.

[0014] The present invention has the following effects:

[0015] The hydraulic system of the slotted lattice beam trolley of this invention provides working oil to multiple hydraulic drive components of the trolley through two main pumps and four multi-way valves. It can achieve single-unit or combined dual-unit oil supply connection, resulting in high integration and low cost. Furthermore, since the boom pitch cylinder and milling head slewing motor operate under long-term, high-flow conditions, this invention uses two main pumps to simultaneously supply oil to both, minimizing hydraulic power loss during operation. Simultaneously, the combined flow of the two pumps avoids problems caused by insufficient flow affecting the function of the actuators.

[0016] In addition, the slotted lattice beam trolley of the present invention also has the above-mentioned advantages.

[0017] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0018] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0019] Figure 1 This is a schematic diagram of the hydraulic principle of the hydraulic system for a slotted lattice beam trolley according to a preferred embodiment of the present invention.

[0020] Explanation of reference numerals in the attached figures

[0021] 1. First main pump; 2. Second main pump; 3. Pilot oil pump; 4. First multi-way valve; 5. Second multi-way valve; 6. Third multi-way valve; 7. Fourth multi-way valve; 8. First pilot proportional pressure reducing valve assembly; 9. Second pilot proportional pressure reducing valve assembly; 10. Electronic control module; 11. First pilot proportional pressure reducing valve; 12. Second pilot proportional pressure reducing valve; 13. Travel pilot directional valve; 14. Mode pilot directional valve; 15. High / low speed switching valve; 101. Left travel motor; 02. Boom pitch cylinder; 103. Boom two-stage telescopic cylinder; 104. Boom three-stage telescopic cylinder; 105. Chassis slewing motor; 106. Right travel motor; 107. Milling head slewing motor; 108. Sliding trolley telescopic cylinder; 109. Milling head advance cylinder; 110. Forearm two-stage telescopic cylinder; 111. Forearm three-stage telescopic cylinder; 112. Milling outrigger telescopic cylinder; 113. Boom support telescopic cylinder; 114. Forearm slewing motor. Detailed Implementation

[0022] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0023] Understandable, such as Figure 1 As shown, a preferred embodiment of the present invention provides a hydraulic system for a slotted lattice beam trolley, including a first main pump 1, a second main pump 2, a first multi-way valve 4, a second multi-way valve 5, a third multi-way valve 6, and a fourth multi-way valve 7. The first main pump 1 and the second main pump 2 are connected in series, forming a double pump to provide the main oil source. The first main pump 1 is connected to the first multi-way valve 4 and the third multi-way valve 6, respectively. The second main pump 2 is connected to the second multi-way valve 5 and the fourth multi-way valve 7, respectively. The first multi-way valve 4 is connected to the left travel motor 101, the boom pitch cylinder 102, and the boom second multi-way valve 7, respectively. The first-stage telescopic cylinder 103 and the third-stage telescopic cylinder 104 of the boom are connected. The second multi-way valve 5 is connected to the boom pitch cylinder 102, the frame slewing motor 105, and the right travel motor 106. The third multi-way valve 6 is connected to the milling head slewing motor 107, the sliding trolley telescopic cylinder 108, the milling head push cylinder 109, the second-stage telescopic cylinder 110 of the forearm, and the third-stage telescopic cylinder 111 of the forearm. The fourth multi-way valve 7 is connected to the milling head slewing motor 107, the milling outrigger telescopic cylinder 112, the boom support telescopic cylinder 113, and the forearm slewing motor 114. By supplying pressurized oil to multiple hydraulic components of the slotted lattice beam trolley through a dual pump and four multi-way valves, the trolley can perform normal movements such as travel, boom pitch, boom second / third stage extension, frame rotation, milling head rotation, sliding trolley extension and retraction, milling head advance, forearm second / third stage extension and retraction, outrigger extension and retraction, boom support extension and retraction, and forearm rotation. While ensuring functionality, this significantly improves the integration of the hydraulic system, reduces costs, and enhances work efficiency and operational convenience. Furthermore, considering that the boom pitch cylinder 102 and the milling head rotation motor 107 operate under prolonged, high-flow conditions, this invention employs dual pumps to supply oil simultaneously. This minimizes hydraulic power loss during operation, and the combined dual-pump oil supply also avoids issues such as insufficient flow affecting the performance of the actuators.

[0024] It is understood that the hydraulic system of the slotted lattice beam trolley in this embodiment provides working oil to multiple hydraulic drive components of the slotted lattice beam trolley through two main pumps and four multi-way valves. This allows for single-unit or combined dual-unit oil supply connections, resulting in a high degree of integration and low cost. Furthermore, since the boom pitch cylinder 102 and the milling head rotary motor 107 operate under long-term, high-flow conditions, this invention uses two main pumps to simultaneously supply oil to both the boom pitch cylinder 102 and the milling head rotary motor 107. This minimizes hydraulic power loss during operation, and the combined flow of the two pumps avoids issues such as insufficient flow affecting the function of the actuators.

[0025] Optionally, the hydraulic system further includes a pilot oil pump 3, a first pilot proportional pressure reducing valve group 8, a second pilot proportional pressure reducing valve group 9, and an electronic control module 10. The pilot oil pump 3 is preferably a constant pressure pump. The pilot oil pump 3 is connected to the first pilot proportional pressure reducing valve group 8 and the second pilot proportional pressure reducing valve group 9. The first pilot proportional pressure reducing valve group 8 is connected to each of the first multi-way valve 4 and the third multi-way valve 6. The second pilot proportional pressure reducing valve group 9 is connected to each of the second multi-way valve 5 and the fourth multi-way valve 7. The electronic control module 10 is electrically connected to the first pilot proportional pressure reducing valve group 8 and the second pilot proportional pressure reducing valve group 9, respectively, to control the outlet pressure of the two pilot proportional pressure reducing valve groups, thereby controlling the valve opening degree of each port of each multi-way valve. The electronic control module 10 is controlled by a remote control handle, converting the input angle of the remote control handle into an electrical control signal to control the outlet pressure of the pilot proportional pressure reducing valve groups. Of course, in other embodiments of the present invention, the electronic control module 10 can be controlled by a PLC. It is understood that the electronic control module 10 converts the input angle of the remote control handle into an electrical signal, which directly affects the outlet pressure of the first pilot proportional pressure reducing valve group 8. The outlet pressure of the first pilot proportional pressure reducing valve group 8 directly affects the valve opening degree of each section of the first multi-way valve 4 and the third multi-way valve 6, thereby enabling the input angle of the remote control handle to control the speed of each section of the first multi-way valve 4 and the third multi-way valve 6. Similarly, the electronic control module 10 converts the input angle of the remote control handle into an electrical signal, which directly affects the outlet pressure of the second pilot proportional pressure reducing valve group 9. The outlet pressure of the second pilot proportional pressure reducing valve group 9 directly affects the valve opening degree of each section of the second multi-way valve 5 and the fourth multi-way valve 7, thereby enabling the input angle of the remote control handle to control the speed of each section of the second multi-way valve 5 and the fourth multi-way valve 7. It is understood that in the hydraulic system of the present invention, the use of a combined dual pump and pilot pump 3 for oil supply is more cost-effective and requires less space for assembly compared to a triple pump. Furthermore, by controlling the multi-way valves through two sets of pilot proportional pressure reducing valve groups to achieve the reciprocating motion of each cylinder and motor, the required flow rate can be adjusted according to the load, reducing power loss, improving the control accuracy of each action, and enhancing the control response speed of each action.

[0026] In addition, the hydraulic system also includes a first pilot proportional pressure reducing valve 11 and a second pilot proportional pressure reducing valve 12 electrically connected to the electronic control module 10. The first pilot proportional pressure reducing valve 11 is connected to the first main pump 1, and the second pilot proportional pressure reducing valve 12 is connected to the second main pump 2. The electronic control module 10 is also used to control the displacement of the two main pumps respectively through the two pilot proportional pressure reducing valves. It can be understood that the electronic control module 10 converts the input angle of the remote control handle into an electrical signal and transmits it to the first pilot proportional pressure reducing valve 11 and the second pilot proportional pressure reducing valve 12 simultaneously, thereby realizing the proportional adjustment of the displacement of the two pumps by the input angle of the remote control handle, and achieving real-time matching between the pump output flow and the flow required by the working mechanism.

[0027] Optionally, both the first main pump 1 and the second main pump 2 are constant power pumps, and the two main pumps adopt cross total power control. Under certain conditions, the two pumps can absorb 100% of the diesel engine efficiency, improve the working capacity of the travel motor, and the left travel motor 101 is supplied with oil by the first main pump 1 and the right travel motor 106 is supplied with oil by the second main pump 2. When the loads of the left and right travel motors are inconsistent, the travel speed can still be kept consistent.

[0028] In addition, the first main pump 1 and the second main pump 2 adopt positive flow control. The working pressure and flow of the entire hydraulic system are controlled by adjusting the output flow of the first main pump 1 and the second main pump 2. Two pilot proportional pressure reducing valve groups are used instead of the shuttle valve group of the general positive flow control system. This gives the lattice beam, which requires high-precision positioning and slotting, and the action of grabbing and placing the lattice beam, the advantages of faster response speed, better control accuracy and stronger working stability.

[0029] Optionally, the hydraulic system further includes a travel pilot directional valve 13, and the pilot oil pump 3 is also connected to the travel pilot directional valve 13. After the travel pilot directional valve 13 is switched, the control oil ports of the first multi-way valve 4 and the second multi-way valve 5 can be directly acted upon by adjusting the operating handle in the cab, thereby realizing local control of the working status of the left travel motor 101 and the right travel motor 106.

[0030] Optionally, the hydraulic system further includes a mode-piloted directional valve 14, and the pilot oil pump 3 is also connected to the mode-piloted directional valve 14. The mode-piloted directional valve 14 is connected to a first pilot proportional pressure reducing valve group 8 and a second pilot proportional pressure reducing valve group 9, and the mode-piloted directional valve 14 determines whether the first pilot proportional pressure reducing valve group 8 and the second pilot proportional pressure reducing valve group 9 can operate.

[0031] Optionally, the hydraulic system further includes a high-low speed switching valve 15, and the pilot oil pump 3 is also connected to the high-low speed switching valve 15. The high-low speed switching valve 15 is connected to the left travel motor 101 and the right travel motor 106, which enables the left travel motor 101 and the right travel motor 106 to operate at high speed.

[0032] In addition, another embodiment of the present invention provides a slotted lattice beam trolley, preferably employing the hydraulic system described above.

[0033] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A hydraulic system for a slotted lattice beam trolley, characterized in that, The system includes a first main pump (1), a second main pump (2), a first multi-way valve (4), a second multi-way valve (5), a third multi-way valve (6), and a fourth multi-way valve (7). The first main pump (1) and the second main pump (2) are connected in series. The first main pump (1) is connected to the first multi-way valve (4) and the third multi-way valve (6) respectively. The second main pump (2) is connected to the second multi-way valve (5) and the fourth multi-way valve (7) respectively. The first multi-way valve (4) is connected to the left travel motor (101), the boom pitch cylinder (102), the boom secondary telescopic cylinder (103), and the boom tertiary telescopic cylinder (104) respectively. The second multi-way valve (5) is connected to the boom pitch cylinder (102), the frame slewing motor (105), and the right travel motor (106) respectively. The third multi-way valve (6) is connected to the milling head slewing motor (107), the sliding trolley telescopic cylinder (108), the milling head push cylinder (109), the forearm secondary telescopic cylinder (110), and the forearm tertiary telescopic cylinder (111) respectively. The fourth multi-way valve (7) is connected to the milling head slewing motor (107), the milling outrigger telescopic cylinder (112), the boom support telescopic cylinder (113), and the forearm slewing motor (114) respectively.

2. The hydraulic system for a slotted lattice beam trolley as described in claim 1, characterized in that, It also includes a pilot oil pump (3), a first pilot proportional pressure reducing valve group (8), a second pilot proportional pressure reducing valve group (9), and an electronic control module (10). The pilot oil pump (3) is connected to the first pilot proportional pressure reducing valve group (8) and the second pilot proportional pressure reducing valve group (9). The first pilot proportional pressure reducing valve group (8) is connected to each of the first multi-way valve (4) and the third multi-way valve (6). The second pilot proportional pressure reducing valve group (9) is connected to each of the second multi-way valve (5) and the fourth multi-way valve (7). The electronic control module (10) is electrically connected to the first pilot proportional pressure reducing valve group (8) and the second pilot proportional pressure reducing valve group (9) respectively, and is used to control the outlet pressure of the two pilot proportional pressure reducing valve groups, thereby controlling the valve opening of each multi-way valve in each section.

3. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, It also includes a first pilot proportional pressure reducing valve (11) and a second pilot proportional pressure reducing valve (12) electrically connected to the electronic control module (10). The first pilot proportional pressure reducing valve (11) is connected to the first main pump (1), and the second pilot proportional pressure reducing valve (12) is connected to the second main pump (2). The electronic control module (10) is also used to control the displacement of the two main pumps respectively through the two pilot proportional pressure reducing valves.

4. The hydraulic system for a slotted lattice beam trolley as described in claim 3, characterized in that, Both the first main pump (1) and the second main pump (2) are constant power pumps, and the two main pumps adopt cross total power control.

5. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, The electronic control module (10) is controlled by a remote control handle. It controls the outlet pressure of the pilot proportional pressure reducing valve group by converting the input angle of the remote control handle into an electrical control signal.

6. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, The first main pump (1) and the second main pump (2) adopt positive flow control, and the working pressure and flow of the entire hydraulic system are controlled by adjusting the output flow of the first main pump (1) and the second main pump (2).

7. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, It also includes a travel pilot directional valve (13), and the pilot oil pump (3) is also connected to the travel pilot directional valve (13).

8. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, It also includes a mode pilot directional valve (14), and the pilot oil pump (3) is also connected to the mode pilot directional valve (14).

9. The hydraulic system for a slotted lattice beam trolley as described in claim 2, characterized in that, It also includes a high-low speed switching valve (15), and the pilot oil pump (3) is also connected to the high-low speed switching valve (15).

10. A slotted lattice beam trolley, characterized in that, The hydraulic system described in any one of claims 1 to 9 is employed.

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