Hydraulic control system and crank arm vehicle

Abstract

The utility model relates to the technical field of overhead working vehicles, in particular to a hydraulic control system and a crank arm vehicle. The hydraulic control system comprises a first main path, a second main path, a first subsystem, a second subsystem and a pressure compensation type proportional valve, wherein one end of the first main path is provided with a main oil inlet; one end of the second main path is provided with a main oil return port; the first subsystem comprises a first hydraulic oil cylinder and a first electromagnetic valve, the first electromagnetic valve is used for switching a flow path of the first subsystem, and the first main path and the second main path communicate with the first hydraulic oil cylinder through the first electromagnetic valve; the second subsystem comprises a second hydraulic oil cylinder and a second electromagnetic valve; the second electromagnetic valve is used for switching a flow path of the second subsystem; the first main path and the second main path are communicated with the second hydraulic oil cylinder through the second electromagnetic valve; the pressure compensation type proportional valve is arranged on the first main path, communicates with the first subsystem and the second subsystem and is used for adjusting the flow of hydraulic oil entering the first subsystem and the second subsystem.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of aerial work vehicles, and particularly relates to a hydraulic control system and a luffing boom truck. BACKGROUND

[0002] The luffing boom truck mainly comprises a hydraulic control system, a slewing platform and a jib. The hydraulic control system is supplied with oil by a pump body, and the oil is divided into two paths after passing through a check valve. One path reaches the jib through a proportional valve, controls the rising and falling of the jib, and can adjust the action speed of the jib. The other path reaches the slewing platform to realize the rotation of the slewing platform, but the rotation speed of the slewing platform cannot be adjusted. Moreover, the oil supplied by the pump body of the hydraulic control system is divided into two paths, and the oil path design is complex after being integrated with other actions, and the cost is relatively high. CONTENT OF THE UTILITY MODEL

[0003] The present application provides a hydraulic control system and a luffing boom truck, which simplifies the hydraulic control system and makes the oil path design simpler.

[0004] In order to achieve the above purpose, the main technical scheme adopted by the present application comprises:

[0005] In a first aspect, the present application provides a hydraulic control system, comprising a first main path, a second main path, a first subsystem, a second subsystem and a pressure compensation proportional valve. One end of the first main path is configured as a total oil inlet. One end of the second main path is configured as a total oil return port. The first subsystem comprises a first hydraulic cylinder and a first electromagnetic valve connected to each other. The first electromagnetic valve is used to switch the flow path of the first subsystem. The first main path and the second main path are both in communication with the first hydraulic cylinder through the first electromagnetic valve. The second subsystem comprises a second hydraulic cylinder and a second electromagnetic valve connected to each other. The second electromagnetic valve is used to switch the flow path of the second subsystem. The first main path and the second main path are both in communication with the second hydraulic cylinder through the second electromagnetic valve. The pressure compensation proportional valve is arranged in the first main path. The pressure compensation proportional valve is in communication with the first subsystem and the second subsystem respectively. The pressure compensation proportional valve is used to adjust the flow of hydraulic oil entering the first subsystem and the second subsystem.

[0006] The hydraulic control system provided by the embodiments of the present application has a pressure compensation type proportional valve arranged in the first main path, hydraulic oil from the total oil inlet passes through the pressure compensation type proportional valve, and then the hydraulic oil enters the first hydraulic system through the first electromagnetic valve or enters the second hydraulic system through the second electromagnetic valve. No matter the action of the load connected with the first hydraulic cylinder or the action of the load connected with the second hydraulic cylinder, the hydraulic oil from the first main path directly acts, thereby simplifying the oil path design of the hydraulic control system. In addition, the pressure compensation type proportional valve can adjust the flow of the hydraulic oil entering the first hydraulic cylinder and the flow of the hydraulic oil entering the second hydraulic cylinder, so that the speed of the load connected with the hydraulic control system can be adjusted.

[0007] Optionally, the pressure compensation type proportional valve comprises a proportional adjusting part, an inlet of the proportional adjusting part is in communication with the total oil inlet, and outlets of the proportional adjusting part are in communication with the first subsystem and the second subsystem respectively.

[0008] In the above scheme, when the action speed of the load connected with the first hydraulic cylinder or the load connected with the second hydraulic cylinder needs to be adjusted, the hydraulic oil entering the first hydraulic cylinder or the second hydraulic cylinder is adjusted through the proportional adjusting part, so that the action speed of the load connected with the first hydraulic cylinder or the load connected with the second hydraulic cylinder is adjusted.

[0009] Optionally, the pressure compensation type proportional valve further comprises a pressure compensation part, the pressure compensation part comprises a first inlet and a first outlet, the first inlet is in communication with the total oil inlet, and the first outlet is in communication with the second main path.

[0010] In the above scheme, when the flow of the hydraulic oil flowing out of the total oil inlet is greater than the hydraulic oil required by the first hydraulic cylinder or the second hydraulic cylinder, or the load connected with the first hydraulic cylinder or the load connected with the second hydraulic cylinder does not need to act, the hydraulic oil can enter the compensation cavity of the pressure compensation part through the first inlet, so as to flow out from the first outlet to the second main path and then flow out from the total oil return port, thereby realizing the pressure relief of the hydraulic oil in the first main path.

[0011] Optionally, the pressure compensation part further comprises a second inlet and a second outlet, the second inlet is in communication with the outlet of the proportional adjusting part, and the second outlet is in communication with the first subsystem and the second subsystem respectively.

[0012] In the above scheme, the pressure compensation type proportional valve integrates the proportional adjusting part and the pressure compensation part, can simultaneously realize the adjustment of the flow of the hydraulic oil in the pipeline and the pressure relief of the pipeline, simplifies the oil path of the hydraulic control system, and makes the oil path design simpler.

[0013] Optionally, the hydraulic control system further comprises a fifth branch, one end of the fifth branch being in communication with the total oil inlet, the other end of the fifth branch being in communication with the first subsystem, and a first damper being arranged on the fifth branch.

[0014] In the above scheme, the hydraulic oil of the total oil inlet can enter the first hydraulic oil cylinder through the first damper, the action of the load connected with the first hydraulic oil cylinder is controlled, and the first damper buffers the hydraulic oil entering the first hydraulic oil cylinder, so that the driving action of the first hydraulic oil cylinder is more stable.

[0015] Optionally, the first subsystem further comprises a first branch, the first branch connecting the first electromagnetic valve (3021) and the pressure compensation type proportional valve (400); the hydraulic control system further comprises a second damper (304), the second damper (304) being arranged on the first branch, and the second damper being located between the one end of the fifth branch connected with the first branch and the first electromagnetic valve.

[0016] In the above scheme, the second damper is arranged on the first branch, and buffers the hydraulic oil entering the first electromagnetic valve and the first hydraulic oil cylinder through the pressure compensation type proportional valve and the first damper, so that the driving action of the first hydraulic oil cylinder is more stable.

[0017] Optionally, the aperture of the second damper is larger than the aperture of the first damper.

[0018] In the above scheme, the second damper mainly buffers the hydraulic oil passing through the pressure compensation type proportional valve, so as to ensure that the load operation has sufficient hydraulic oil flow and pressure, thereby improving the stability of the entire hydraulic control system.

[0019] Optionally, the hydraulic control system further comprises a sixth branch, one end of the sixth branch being in communication with the first subsystem and the second subsystem respectively, the other end of the sixth branch being in communication with the second main branch, and a pressure compensation flow valve being arranged on the sixth branch.

[0020] In the above scheme, the pressure compensation flow valve can keep the flow of the hydraulic oil in the entire hydraulic control system stable, thereby improving the stability of the entire hydraulic control system.

[0021] Optionally, the hydraulic control system further comprises a seventh branch, one end of the seventh branch being connected to the first main branch and located between the total oil inlet and the pressure compensation type proportional valve, the other end of the seventh branch being in communication with the second main branch, and an overflow valve being arranged on the seventh branch.

[0022] In the above scheme, the overflow valve is used to limit the maximum pressure in the hydraulic control system. When the pressure in the hydraulic control system exceeds the predetermined pressure of the overflow valve, the overflow valve opens to discharge excess oil to the second main circuit, so that the pressure of the hydraulic control system is stabilized below the predetermined pressure, reducing the probability of damage to components or safety accidents of the hydraulic control system due to excessive pressure, and improving the stability of the hydraulic control system.

[0023] Optionally, a first one-way valve is further arranged on the second main circuit, and the first one-way valve is located at one end of the total oil return port and the seventh branch connected with the second main circuit.

[0024] In the above scheme, in the hydraulic control system, the first one-way valve is arranged to increase the oil return back pressure, so that the oil return resistance of the first hydraulic oil cylinder or the second hydraulic oil cylinder is increased, the hydraulic oil flows more smoothly, thereby effectively reducing the occurrence of crawling phenomenon and improving the stability of load action.

[0025] In a second aspect, the embodiments of the present application provide a curved arm vehicle, comprising the hydraulic control system, the platform and the boom of any one of the above embodiments, the platform is connected with the first hydraulic oil cylinder, and the boom is connected with the second hydraulic oil cylinder.

[0026] In the above scheme, when the platform needs to rotate, the hydraulic oil of the total oil inlet of the hydraulic control system enters the first hydraulic oil cylinder through the first electromagnetic valve, so that the first hydraulic oil cylinder controls the rotation of the platform, and the rotation speed of the platform can be adjusted through the pressure compensation type proportional valve; when the boom needs to act, the hydraulic oil of the total oil inlet enters the second hydraulic oil cylinder through the second electromagnetic valve, so that the second hydraulic oil cylinder controls the lifting or lowering action of the boom, and the speed of the boom action can be adjusted through the pressure compensation type proportional valve. BRIEF DESCRIPTION OF DRAWINGS

[0027] In order to more clearly illustrate the specific embodiments of the present application or the technical solutions in the prior art, the drawings needed in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor.

[0028] Figure 1 a schematic diagram of the hydraulic control system in one embodiment of the present application;

[0029] Figure 2 a schematic diagram of the hydraulic control system in another embodiment of the present application.

[0030]

Explanation of reference signs

[0031] 100: first hydraulic oil cylinder; 200: second hydraulic oil cylinder;

[0032] 301: first main line; 302: first branch line; 3021: first electromagnetic valve; 303: second branch line; 3031: second electromagnetic valve; 304: second damper;

[0033] 400: pressure compensation type proportional valve; 401: proportional adjusting part; 402: pressure compensation part; 4021: first inlet; 4022: first outlet; 4023: second inlet; 4024: second outlet;

[0034] 501: second main line; 502: third branch line; 503: fourth branch line; 504: first check valve;

[0035] 600: fifth branch line; 601: first damper;

[0036] 700: sixth branch line; 701: pressure compensation flow valve;

[0037] 800: seventh branch line; 801: overflow valve;

[0038] P: total oil inlet; T: total oil return; P1: first load; T1: first oil return. DETAILED DESCRIPTION

[0039] In order to make the purpose, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are some of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0040] Unless otherwise defined, all technical and scientific terms used in the present application have the same meaning as commonly understood by one of ordinary skill in the art to which the present application belongs; the terms used in the specification of the present application are only for the purpose of describing specific embodiments of the present application, and are not intended to limit the present application; the terms "include" and "have" and any variations thereof in the specification and claims of the present application and the above description of drawings are intended to cover non-exclusive inclusion. The terms "first", "second" and the like in the specification and claims of the present application and the above description of drawings are used to distinguish different objects, and are not intended to describe a particular order or primary and secondary relationship.

[0041] Reference within this application to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are they necessarily mutually exclusive of one another. As used in this application, the term "or" is intended to mean an inclusive "or" rather than an exclusive "or". That is, unless specified otherwise, or clear from context, "X employs A or B" means that X employs A or B or both. The term "a" or "an" is defined as one or more unless explicitly indicated to the contrary or otherwise evident from the context. The term "plurality" is defined as two or more unless explicitly indicated to the contrary or otherwise evident from the context.

[0042] In the description of the application, it is necessary to explain that, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connecting", "attachment" should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be directly connected, or indirectly connected through an intermediate medium, or the internal communication of two elements. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0043] The term "and / or" in this application is only to describe the association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B can mean that A exists alone, A and B exist together, and B exists alone. In addition, the character " / " in this application generally represents that the front and rear associated objects have an "or" relationship.

[0044] "Multiple" appearing in this application refers to more than two (including two), and similarly, "multiple groups" refers to more than two groups (including two groups), and "multiple pieces" refers to more than two pieces (including two pieces).

[0045] At present, the working principle of the hydraulic control system of the swing arm truck is as follows: the hydraulic oil output by the pump passes through the oil inlet, passes through the one-way valve and the four-way pressure compensation valve, and is divided into two ways, one way is through the priority port of the four-way pressure compensation valve and then through the proportional valve to reach the electromagnetic valve connected with the boom and other load oil ports. The other load oil port oil path can continue to be connected with other oil paths to realize other functions. The oil outlet of the electromagnetic valve connected with the boom is connected with the rod cavity or the rodless cavity of the oil cylinder of the boom. If one end of the electromagnetic valve connected with the boom is electrified, the boom rises, and if the other end is electrified, the boom descends. The damping between the electromagnetic valve connected with the boom and the boom can make the boom action start smoothly, and play a transition buffering role. The proportional valve can be used to adjust the action speed of the boom.

[0046] Another way is that the oil passes through the bypass port of the four-way pressure compensation valve (the spool of the priority valve is displaced through the bypass), and then reaches the electromagnetic valve connected with the platform and other load oil ports. The other load oil circuit can continue to be connected with other oil circuits to realize other functions. The outlet of the electromagnetic valve connected with the platform is connected with the swing cylinder of the rotating platform. For example, when one end of the electromagnetic valve connected with the platform is powered, the swing cylinder rotates to the left, and when the other end is powered, the swing cylinder rotates to the right. The damping between the electromagnetic valve connected with the platform and the platform can limit the speed of the swing cylinder rotation, and has a buffering effect. However, this oil circuit cannot adjust the swing speed of the rotating platform through a proportional valve.

[0047] All movements of the above-mentioned curved arm vehicle need to be controlled by two oil circuits, and the oil circuit design is complex and the cost is relatively high.

[0048] Therefore, there is a need for a hydraulic control system with a simple oil circuit design.

[0049] In a first aspect, with reference to Figure 1 The embodiments of the present application provide a hydraulic control system, which comprises a first main circuit 301, a second main circuit 501, a first subsystem, a second subsystem and a pressure compensation type proportional valve 400. One end of the first main circuit 301 is configured as a total oil inlet P. One end of the second main circuit 501 is configured as a total oil return T. The first subsystem comprises a first hydraulic cylinder 100 and a first electromagnetic valve 3021 connected thereto. The first electromagnetic valve 3021 is used to switch the flow path of the first subsystem. The first main circuit 301 and the second main circuit 501 are both communicated with the first hydraulic cylinder 100 through the first electromagnetic valve 3021. The second subsystem comprises a second hydraulic cylinder 200 and a second electromagnetic valve 3031 connected thereto. The second electromagnetic valve 3031 is used to switch the flow path of the second subsystem. The first main circuit 301 and the second main circuit 501 are both communicated with the second hydraulic cylinder 200 through the second electromagnetic valve 3031. The pressure compensation type proportional valve 400 is arranged in the first main circuit 301. The pressure compensation type proportional valve 400 is communicated with the first subsystem and the second subsystem respectively. The pressure compensation type proportional valve 400 is used to adjust the flow of hydraulic oil entering the first subsystem and the second subsystem.

[0050] The first main line 301 is communicated with the first hydraulic cylinder 100 through the first electromagnetic valve 3021, and the first electromagnetic valve 3021 is controlled to be opened or closed to realize the opening or closing of the first hydraulic cylinder 100. The first hydraulic cylinder 100 can be connected with a load, and the hydraulic control system controls the action of the load by controlling the oil supply of the first hydraulic cylinder 100. When the first electromagnetic valve 3021 is opened, the hydraulic oil in the first main line 301 enters the first hydraulic cylinder 100 through the first electromagnetic valve 3021, and the load connected with the first hydraulic cylinder 100 is driven to move. The hydraulic oil in the first hydraulic cylinder 100 flows out through another opening of the first hydraulic cylinder 100, enters the second main line 501 through the first electromagnetic valve 3021, and then flows out from the total oil return port T of the second main line 501. When the first electromagnetic valve 3021 is closed, the first hydraulic cylinder 100 stops supplying oil, and the load connected with the first hydraulic cylinder 100 stops moving.

[0051] The first main line 301 is communicated with the second hydraulic cylinder 200 through the second electromagnetic valve 3031, and the second electromagnetic valve 3031 is controlled to be opened or closed to realize the opening or closing of the second hydraulic cylinder 200. The second hydraulic cylinder 200 can be connected with a load, and the hydraulic control system controls the action of the load by controlling the oil supply of the second hydraulic cylinder 200. When the second electromagnetic valve 3031 is opened, the hydraulic oil in the first main line 301 enters the second hydraulic cylinder 200 through the second electromagnetic valve 3031, and the load connected with the second hydraulic cylinder 200 is driven to move. The hydraulic oil in the second hydraulic cylinder 200 flows out through another opening of the second hydraulic cylinder 200, enters the second main line 501 through the second electromagnetic valve 3031, and then flows out from the total oil return port T of the second main line 501. When the second electromagnetic valve 3031 is closed, the second hydraulic cylinder 200 stops supplying oil, and the load connected with the second hydraulic cylinder 200 stops moving.

[0052] The hydraulic control system provided in the embodiment of the application is characterized in that the pressure compensation proportional valve 400 is arranged in the first main line 301, and the hydraulic oil from the total oil inlet port P passes through the pressure compensation proportional valve 400, and then enters the first hydraulic system through the first electromagnetic valve 3021 or enters the second hydraulic system through the second electromagnetic valve 3031. The action of the load connected with the first hydraulic cylinder 100 or the action of the load connected with the second hydraulic cylinder 200 is directly affected by the hydraulic oil from the first main line 301, so that the oil circuit design of the hydraulic control system is simplified. In addition, the pressure compensation proportional valve 400 can adjust the flow of the hydraulic oil entering the first hydraulic cylinder 100 to control the action speed of the load connected with the first hydraulic cylinder 100, and the pressure compensation proportional valve 400 can adjust the flow of the hydraulic oil entering the second hydraulic cylinder 200 to control the action speed of the load connected with the second hydraulic cylinder 200, so that the speed of the load connected with the hydraulic control system can be adjusted.

[0053] Optionally, the pressure compensation type proportional valve 400 comprises a proportional adjusting part 401, an inlet of the proportional adjusting part 401 is communicated with the total oil inlet port P, and outlets of the proportional adjusting part 401 are respectively communicated with the first subsystem and the second subsystem.

[0054] When the first hydraulic cylinder 100 or the second hydraulic cylinder 200 needs hydraulic oil to work, the hydraulic oil of the total oil inlet port P enters the proportional adjusting part 401, and then enters the first electromagnetic valve 3021 or the second electromagnetic valve 3031 from the outlet of the proportional adjusting part 401, so as to supply oil to the first hydraulic cylinder 100 or the second hydraulic cylinder 200. When the action speed of the load connected with the first hydraulic cylinder 100 or the load connected with the second hydraulic cylinder 200 needs to be adjusted, the hydraulic oil entering the first hydraulic cylinder 100 or the second hydraulic cylinder 200 is adjusted through the proportional adjusting part 401, so as to adjust the action speed of the load connected with the first hydraulic cylinder 100 or the load connected with the second hydraulic cylinder 200.

[0055] Optionally, the pressure compensation type proportional valve 400 further comprises a pressure compensation part 402, the pressure compensation part 402 comprises a first inlet 4021 and a first outlet 4022, the first inlet 4021 is communicated with the total oil inlet port P, and the first outlet 4022 is communicated with the second main path 501.

[0056] Specifically, the pressure compensation part 402 has the first inlet 4021 and the first outlet 4022, when the flow of the hydraulic oil flowing out of the total oil inlet port P is greater than the hydraulic oil required by the first hydraulic cylinder 100 or the second hydraulic cylinder 200, the excessive hydraulic oil can enter the compensation cavity of the pressure compensation part 402 through the first inlet 4021, so as to flow out from the first outlet 4022 to the second main path 501, and then flow out from the total oil return port T, thereby realizing pressure relief of the hydraulic oil in the first main path 301. Or when the load connected with the first hydraulic cylinder 100 or the load connected with the second hydraulic cylinder 200 does not need to act, the hydraulic oil can enter the compensation cavity of the pressure compensation part 402 through the first inlet 4021, so as to flow out from the first outlet 4022 to the second main path 501, and then flow out from the total oil return port T, thereby realizing pressure relief of the hydraulic oil in the first main path 301. Or when the pump of the hydraulic control system stops outputting hydraulic oil, the hydraulic oil of the total oil inlet port P enters the pressure compensation part 402 and is directly discharged from the pressure compensation part 402 to the second main path 501.

[0057] Optionally, the pressure compensation part 402 further comprises a second inlet 4023 and a second outlet 4024, the second inlet is communicated with the outlet of the proportional adjusting part 401, and the second outlet of the pressure compensation part 402 is respectively communicated with the first subsystem and the second subsystem.

[0058] The pressure-compensating proportional valve 400 in this application integrates a proportional adjustment unit 401 and a pressure compensation unit 402, which can simultaneously adjust the flow rate of hydraulic oil in the pipeline and relieve pressure in the pipeline, simplifying the oil circuit of the hydraulic control system and making the oil circuit design simpler.

[0059] In other words, the pressure compensation proportional valve 400 can adjust the hydraulic oil entering the first hydraulic cylinder 100 or the second hydraulic cylinder 200 through the proportional adjustment unit 401, thereby adjusting the operating speed of the load connected to the first hydraulic cylinder 100 or the load connected to the second hydraulic cylinder 200; it can also adjust the pressure of the first main circuit 301 through the pressure compensation unit 402, thereby releasing the hydraulic oil pressure on the first main circuit 301.

[0060] Optionally, refer to Figure 2 The hydraulic control system also includes a fifth branch 600, one end of which is connected to the main oil inlet P, and the other end of which is connected to the first subsystem. A first damper 601 is provided on the fifth branch 600.

[0061] The hydraulic oil in the main inlet P can enter the first hydraulic cylinder 100 through the first damper 601 to control the movement of the load connected to the first hydraulic cylinder 100. The first damper 601 buffers the hydraulic oil entering the first hydraulic cylinder 100, thereby making the driving action of the first hydraulic cylinder 100 more stable.

[0062] Specifically, the first subsystem also includes a first branch 302, which connects a first solenoid valve 3021 and a pressure-compensated proportional valve 400; the first subsystem also includes a second branch 303, which connects a second solenoid valve 3031 and a pressure-compensated proportional valve 400.

[0063] In some implementations, under normal operating conditions, such as when the load connected to the first hydraulic cylinder 100 does not require speed adjustment, the pressure compensation proportional valve 400 can be closed, and the hydraulic oil from the main inlet P enters the first branch 302 through the first damper 601, and then enters the first hydraulic cylinder 100 through the first solenoid valve 3021, thereby realizing the action of the load connected to the first hydraulic cylinder 100. When the load connected to the first hydraulic cylinder 100 needs to adjust its speed, the pressure-compensating proportional valve 400 is opened. Part of the hydraulic oil in the main inlet P enters the first branch 302 through the first damper 601, and the other part enters the second inlet 4023 of the pressure compensation section 402 through the proportional adjustment section 401 of the pressure-compensating proportional valve 400. Then, it flows out through the second outlet 4024 of the pressure compensation section 402, passes through the first branch 302, and the hydraulic oil that has passed through the first damper 601 and the pressure-compensating proportional valve 400 converges in the first branch 302 before entering the first hydraulic cylinder 100 through the first solenoid valve 3021.

[0064] It should be understood that when the second hydraulic cylinder 200 works, the hydraulic oil of the total oil inlet P enters the second inlet 4023 of the pressure compensation part 402 through the proportional adjusting part 401 of the pressure compensation type proportional valve 400, and then flows out from the second outlet 4024 of the pressure compensation part 402 through the second branch 303. A part of the hydraulic oil also enters the first branch 302 through the first damper 601, and then enters the second branch 303 through the first branch 302. The hydraulic oil passing through the first damper 601 and the hydraulic oil passing through the pressure compensation type proportional valve 400 converge in the second branch 303, and then enter the second hydraulic cylinder 200 through the second electromagnetic valve 3031.

[0065] Optionally, with reference to Figure 1 and Figure 2 , the hydraulic control system further comprises a second damper 304, which is arranged on the first branch 302 and located between the first electromagnetic valve 3021 and the end of the first branch 302 connected with the fifth branch 600.

[0066] The second damper 304 arranged on the first branch 302 buffers the hydraulic oil entering the first electromagnetic valve 3021 and the first hydraulic cylinder 100 through the pressure compensation type proportional valve 400 and the first damper 601, so that the driving action of the first hydraulic cylinder 100 is more stable.

[0067] Optionally, the aperture of the second damper 304 is larger than the aperture of the first damper 601.

[0068] The hydraulic oil converges in the first branch 302 after passing through the first damper 601 of the fifth branch 600 and the pressure compensation type proportional valve 400, and then passes through the second damper 304. The second damper 304 buffers the converged hydraulic oil, so that the driving action of the first hydraulic cylinder 100 is more stable.

[0069] When the required hydraulic flow of the load action is small and the action speed does not need to be adjusted, the pressure compensation type proportional valve 400 does not work, and the hydraulic oil passes through the first damper 601. The flow rate and pressure change of the hydraulic oil are mainly limited by the first damper 601, so as to improve the stability of the entire hydraulic control system. When the required hydraulic flow of the load is large or the action speed needs to be adjusted, the pressure compensation type proportional valve 400 works, and the second damper 304 mainly buffers the hydraulic oil passing through the pressure compensation type proportional valve 400, so as to ensure that the load operation has sufficient hydraulic oil flow and pressure, thereby improving the stability of the entire hydraulic control system.

[0070] Optionally, the hydraulic control system further comprises a sixth branch 700, one end of the sixth branch 700 is in communication with the first subsystem and the second subsystem respectively, the other end of the sixth branch 700 is in communication with the second main line 501, and the sixth branch 700 is provided with a pressure compensation flow valve 701. That is, the hydraulic control system further comprises a sixth branch 700, one end of the sixth branch 700 is in communication with the first branch 302 and the second branch 303 respectively, the other end of the sixth branch 700 is in communication with the second main line 501, and the sixth branch 700 is provided with a pressure compensation flow valve 701.

[0071] The pressure compensation flow valve 701 can continuously output a certain flow, so that the flow of hydraulic oil to the first hydraulic cylinder 100 and the second hydraulic cylinder 200 is stable. When the first hydraulic cylinder 100 is working and the load action does not need to be adjusted by the pressure compensation proportional valve 400, the pressure compensation proportional valve 400 is closed, the hydraulic oil enters the first branch 302 through the first damper 601, and then flows into the first hydraulic cylinder 100 from the first branch 302. Since the first damper 601 is arranged on the fifth branch 600, the fifth branch 600 is in communication with the first branch 302, and the first branch 302 is in communication with the second outlet 4024 of the pressure compensation part 402, the hydraulic oil flowing through the fifth branch 600 will enter the second outlet 4024 of the pressure compensation part 402 and the second branch 303 from the first branch 302. The pressure of the hydraulic oil entering the second outlet 4024 will push the compensation valve core of the pressure compensation part 402 to move, thereby closing the first outlet 4022 of the pressure compensation part 402, so that the pressure relief passage of the pressure compensation part 402 is closed, which will affect the pressure relief of the first main line 301. If the hydraulic oil entering the second outlet 4024 and the second branch 303 cannot be discharged in time, the pressure in the pipeline will rise, affecting the normal operation of the system. The pressure compensation flow valve 701 can discharge the hydraulic oil in the second outlet 4024 and the second branch 303, stabilize the pressure of the second outlet 4024 and the second branch 303, and reduce the risk of abnormal closing of the pressure relief passage of the pressure compensation part 402, thereby improving the stability of the entire hydraulic control system.

[0072] In addition, the leakage of the hydraulic oil of the second outlet 4024 of the pressure compensation part 402 itself will also make the compensation valve core of the pressure compensation part 402 move to close the first outlet 4022 of the pressure compensation part 402, and the hydraulic oil accumulated in the second outlet 4024 of the pressure compensation part 402 can also be discharged through the pressure compensation flow valve 701 to achieve the purpose of pressure relief.

[0073] Among them, the pressure compensation flow valve 701 can stably output a certain flow, which is not affected by the inlet pressure before the pressure compensation flow valve 701, and can keep the flow of the first hydraulic cylinder 100, the second hydraulic cylinder 200 or the first load P1 stable. The flow of the pressure compensation flow valve 701 is generally less than 500 mL / min.

[0074] Optionally, the hydraulic control system further comprises a seventh branch 800, one end of the seventh branch 800 is connected to the first main line 301 and located between the total oil inlet P and the pressure compensation proportional valve 400, the other end of the seventh branch 800 is in communication with the second main line 501, and the seventh branch 800 is provided with an overflow valve 801.

[0075] The overflow valve 801 is used to limit the maximum pressure in the hydraulic control system. When the pressure in the hydraulic control system exceeds the predetermined pressure of the overflow valve 801, the overflow valve 801 is opened, and the excess oil is discharged to the second main line 501, so that the pressure of the hydraulic control system is stabilized below the predetermined pressure, the probability of damaging components or safety accidents of the hydraulic control system due to excessive pressure is reduced, and the stability of the hydraulic control system is improved.

[0076] Optionally, the second main line 501 is further provided with a first one-way valve 504, and the first one-way valve 504 is located at the total oil return port T and one end of the seventh branch 800 connected to the second main line 501.

[0077] In the hydraulic control system, the first one-way valve 504 is arranged to increase the oil return back pressure, so that the oil return resistance of the first hydraulic oil cylinder 100 or the second hydraulic oil cylinder 200 is increased, the hydraulic oil flows more smoothly, and the occurrence of the crawling phenomenon is effectively reduced, and the stability of the load action is improved.

[0078] In addition, during the start, stop or replacement of the action, due to the inertia and pressure change of the hydraulic oil, impact and vibration will be generated, and appropriate oil return back pressure can play a buffering role in these processes, slow down the flow rate change of the hydraulic oil, reduce the impact and vibration, and make the hydraulic control system run more smoothly.

[0079] Optionally, the hydraulic control system further comprises a first load P1, and the first load P1 is in communication with the second branch 303 and the second main line 501 respectively. In addition to being used for the first hydraulic oil cylinder 100 and the second hydraulic oil cylinder 200, the hydraulic oil in the hydraulic control system also provides hydraulic oil for the first load P1 to execute the action, and since the first load P1 is in communication with the second branch 303, the first load P1 can also adjust the flow of the hydraulic oil through the pressure compensation proportional valve 400, so as to adjust the action speed of the first load P1. After the hydraulic oil enters the first load P1, it enters the second main line 501 through the first oil return port T1.

[0080] In a second aspect, the embodiments of the present application provide a swing arm vehicle, which comprises the hydraulic control system, the platform and the boom of any one of the above embodiments, the platform is connected with the first hydraulic oil cylinder 100, and the boom is connected with the second hydraulic oil cylinder 200.

[0081] When the platform needs to rotate, the hydraulic oil of the total oil inlet P passes through the fifth branch 600, the first damper 601, the first electromagnetic valve 3021, and then enters the first hydraulic oil cylinder 100, so that the first hydraulic oil cylinder 100 controls the rotation of the platform; if the rotation speed of the platform needs to be adjusted, the hydraulic oil of the total oil inlet P is divided into two paths, one path passes through the pressure compensation type proportional valve 400 and enters the first branch 302, and the other path passes through the first damper 601 of the fifth branch 600 and enters the first branch 302, and the two paths of hydraulic oil are combined in the first branch 302 and then enter the first electromagnetic valve 3021 through the second damper 304, and then enter the first hydraulic oil cylinder 100, so that the first hydraulic oil cylinder 100 controls the speed of the rotation of the platform.

[0082] When the boom needs to act, the hydraulic oil of the total oil inlet P passes through the pressure compensation type proportional valve 400 and enters the second branch 303, enters the second electromagnetic valve 3031, and then enters the second hydraulic oil cylinder 200, so that the second hydraulic oil cylinder 200 controls the boom action, and the speed of the boom action can be adjusted through the pressure compensation type proportional valve 400.

[0083] In this application, when the platform is in the middle position, the hydraulic oil of the total oil inlet P is divided into two paths, one path passes through the first damper 601 of the fifth branch 600 and enters the first branch 302, and the other path enters the first main branch 301, the hydraulic oil passes through the proportional adjustment part 401 and enters the first branch 302, and the two paths of hydraulic oil can enter the first load P1 after being combined in the first branch 302, the first load P1 can be actuated or not according to the need, or can enter the first electromagnetic valve 3021 and the first hydraulic oil cylinder 100 after passing through the second damper 304. The hydraulic oil passing through the second damper 304 passes through the first electromagnetic valve 3021, the oil outlet of the first electromagnetic valve 3021 communicates with the first hydraulic oil cylinder 100, and the hydraulic oil reaches the A1 port or the B1 port of the first hydraulic oil cylinder 100, wherein the first electromagnetic valve 3021 can be a three-position four-way electromagnetic valve, and the rotation action of the platform is controlled by the first electromagnetic valve 3021. When the platform needs to rotate, the first electromagnetic valve 3021 is powered, for example, the S1 end of the first electromagnetic valve 3021 is powered, the hydraulic oil enters the A1 port of the first hydraulic oil cylinder 100, controls the left rotation of the platform, and the hydraulic oil from the B1 port of the first hydraulic oil cylinder 100 enters the third branch 502 through the first electromagnetic valve 3021 and returns to the oil; the S2 end of the first electromagnetic valve 3021 is powered, the hydraulic oil enters the B1 port of the first hydraulic oil cylinder 100, the first hydraulic oil cylinder 100 controls the right rotation of the platform, and the hydraulic oil from the A1 port of the first hydraulic oil cylinder 100 enters the third branch 502 through the first electromagnetic valve 3021 and returns to the oil.

[0084] It should be understood that when the speed of the platform rotation action needs to be adjusted, the pressure compensation proportional valve 400 can be opened, and then the hydraulic oil flows through the first damper 601 of the fifth branch 600 and the pressure compensation proportional valve 400 of the first main line 301 to converge at the first branch 302, and then enters the first hydraulic oil cylinder 100, thereby controlling the rotation of the platform and the adjustment of the rotation speed. When the speed of the platform rotation action does not need to be adjusted, the pressure compensation proportional valve 400 is closed, and then the hydraulic oil enters the first damper 601 of the fifth branch 600 from the total oil inlet P, enters the first branch 302, and then enters the first hydraulic oil cylinder 100, thereby controlling the rotation of the platform.

[0085] When the boom action is needed, the pressure compensation proportional valve 400 and the second electromagnetic valve 3031 are energized, the second electromagnetic valve 3031 can be a three-position four-way electromagnetic valve, the hydraulic oil enters the second branch 303 through the proportional adjusting part 401 and the pressure compensation part 402, and then enters the second electromagnetic valve 3031 and the first load P1, the first load P1 can be executed according to the need of action, the oil outlet of the first electromagnetic valve 3021 is communicated with the first hydraulic oil cylinder 100, the hydraulic oil entering the first electromagnetic valve 3021 enters the second hydraulic oil cylinder 200, and the hydraulic oil reaches the A2 port or the B2 port of the second hydraulic oil cylinder 200, thereby controlling the lifting and lowering of the boom. Exemplarily, the S1 end of the second electromagnetic valve 3031 is energized, the hydraulic oil enters the A2 port of the second hydraulic oil cylinder 200, the boom is lifted, and the hydraulic oil from the B2 port of the second hydraulic oil cylinder 200 enters the fourth branch 503 through the second electromagnetic valve 3031 to return to oil; the S2 end of the second electromagnetic valve 3031 is energized, the hydraulic oil enters the B2 port of the second hydraulic oil cylinder 200, the boom is lowered, and the hydraulic oil from the A2 port of the second hydraulic oil cylinder 200 enters the fourth branch 503 through the second electromagnetic valve 3031 to return to oil.

[0086] In this application, because the hydraulic oil in the fifth branch 600 enters the first branch 302, the hydraulic oil of the first branch 302 will backflow to the second outlet 4024 of the pressure compensation part 402, and the second outlet 4024 of the pressure compensation part 402 will also have the leakage oil of the pressure compensation part 402 itself, so that the pipeline pressure between the second outlet 4024 and the first load P1 rises. The hydraulic oil at the second outlet 4024 will push the valve core of the pressure compensation part 402 to move, thereby closing the first outlet 4022 of the pressure compensation part 402, affecting the pressure relief of the first main line 301, at this time the hydraulic oil in the second outlet 4024 and the second branch 303 can be output through the pressure compensation flow valve 701.

[0087] That is, when the pressure compensation type proportional valve 400 is not working, the hydraulic oil entering the first branch 302 through the fifth branch 600 will enter the second outlet 4024 of the pressure compensation part 402, and the hydraulic oil leaking from the second outlet 4024 of the pressure compensation part 402 itself, so that the compensation valve core of the pressure compensation part 402 moves to close the first outlet 4022 of the pressure compensation part 402, and the hydraulic oil accumulated in the second outlet 4024 of the pressure compensation part 402 can be discharged through the pressure compensation flow valve 701, so as to achieve the purpose of pressure relief.

[0088] When the pressure compensation type proportional valve 400 is working, if the hydraulic oil flow of the total oil inlet P is greater than the flow required by the load, the excess hydraulic oil can enter the pressure compensation part 402 through the first inlet 4021 of the pressure compensation part 402 at a lower pressure and be discharged to the total oil return port T through the first outlet 4022; or when the pump of the hydraulic control system stops outputting hydraulic oil, the hydraulic oil of the total oil inlet P can enter the pressure compensation part 402 through the first inlet 4021 of the pressure compensation part 402 and be discharged to the total oil return port T through the first outlet 4022, so as to quickly reduce the pressure of the total oil inlet P.

[0089] It should also be noted that the terms "comprising", "containing", or any other variant thereof are intended to cover non-exclusive inclusions, so that a process, method, article or apparatus that includes a list of elements not only includes those elements, but also includes other elements not explicitly listed, or inherent to such a process, method, article or apparatus. Without more limitations, the element defined by the statement "comprising a" does not exclude the presence of additional identical elements in the process, method, article or apparatus that includes the element.

[0090] Each of the embodiments in the specification is described in a progressive manner, and the same and similar parts between the embodiments can be referred to each other. Each embodiment focuses on the difference from other embodiments. In particular, for the system embodiment, since it is basically similar to the method embodiment, the description is relatively simple, and the relevant parts can be referred to the part of the method embodiment.

[0091] The above only describes the embodiments of the present application and does not limit the present application. Those skilled in the art can make various modifications and changes to the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the scope of the claims of the present application.

[0092] Although the embodiments of the present application are described in conjunction with the drawings, those skilled in the art can make various modifications and changes without departing from the spirit and scope of the present application, and such modifications and changes fall within the scope defined by the appended claims.

Claims

1. A hydraulic control system characterized by, The hydraulic control system comprises: a first main path (301), one end of which is configured as a total oil inlet (P); a second main path (501), one end of which is configured as a total oil return (T); a first subsystem comprising a first hydraulic cylinder (100) and a first electromagnetic valve (3021) connected thereto, the first electromagnetic valve (3021) being used to switch the flow path of the first subsystem, the first main path (301) and the second main path (501) being in communication with the first hydraulic cylinder (100) through the first electromagnetic valve (3021); a second subsystem comprising a second hydraulic cylinder (200) and a second electromagnetic valve (3031) connected thereto, the second electromagnetic valve (3031) being used to switch the flow path of the second subsystem, the first main path (301) and the second main path (501) being in communication with the second hydraulic cylinder (200) through the second electromagnetic valve (3031); a pressure-compensated proportional valve (400) provided in the first main path (301), the pressure-compensated proportional valve (400) being in communication with the first subsystem and the second subsystem respectively, and the pressure-compensated proportional valve (400) being used to adjust the flow rate of hydraulic oil entering the first subsystem and the second subsystem.

2. The hydraulic control system of claim 1, wherein, The pressure-compensated proportional valve (400) comprises a proportional adjusting part (401), the inlet of the proportional adjusting part (401) being in communication with the total oil inlet (P), and the outlet of the proportional adjusting part (401) being in communication with the first subsystem and the second subsystem respectively.

3. The hydraulic control system of claim 2, wherein, The pressure-compensated proportional valve (400) further comprises a pressure compensation part (402), the pressure compensation part (402) comprising a first inlet (4021) and a first outlet (4022), the first inlet (4021) being in communication with the total oil inlet (P), and the first outlet (4022) being in communication with the second main path (501).

4. The hydraulic control system of claim 3, wherein, The pressure compensation part (402) further comprises a second inlet (4023) and a second outlet (4024), the second inlet (4023) being in communication with the outlet of the proportional adjusting part (401), and the second outlet (4024) being in communication with the first subsystem and the second subsystem respectively.

5. The hydraulic control system of claim 1, wherein, The hydraulic control system further comprises a fifth branch path (600), one end of the fifth branch path (600) being in communication with the total oil inlet (P), and the other end of the fifth branch path (600) being in communication with the first subsystem, and a first damper (601) being provided on the fifth branch path (600).

6. The hydraulic control system of claim 5, wherein, The first subsystem further comprises a first branch path (302), the first branch path (302) connecting the first electromagnetic valve (3021) and the pressure-compensated proportional valve (400); The hydraulic control system further comprises a second damper (304), the second damper (304) being provided on the first branch path (302), and the second damper (304) being located between the first electromagnetic valve (3021) and the end of the first branch path (302) where the fifth branch path (600) is connected.

7. The hydraulic control system of claim 6, wherein, The second damping (304) has a larger pore diameter than the first damping (601).

8. The hydraulic control system of claim 1, wherein, A sixth branch (700) is further included, one end of the sixth branch (700) being in communication with the first subsystem and the second subsystem respectively, the other end of the sixth branch (700) being in communication with the second main road (501), and a pressure compensation flow valve (701) being arranged on the sixth branch (700).

9. The hydraulic control system of claim 1, wherein, A seventh branch (800) is further included, one end of the seventh branch (800) being connected to the first main road (301) and being located between the total oil inlet (P) and the pressure compensation type proportional valve, the other end of the seventh branch (800) being in communication with the second main road (501), and an overflow valve (801) being arranged on the seventh branch (800).

10. A scooter characterized in that, Comprise: The hydraulic control system according to any one of claims 1-9; A platform connected with the first hydraulic cylinder (100) and a boom connected with the second hydraulic cylinder (200).

Images