Hydraulic control system and working machine

Abstract

The utility model relates to the technical field of hydraulic systems, and provides a hydraulic control system and an operation machine. In the hydraulic control system, a first hydraulic pump is connected with a winch control assembly, a second hydraulic pump is connected with a telescopic control assembly and a variable amplitude control assembly, and the telescopic control assembly and the variable amplitude control assembly are arranged in parallel. And the shunting and converging control assembly is connected between the first hydraulic pump and the second hydraulic pump and is used for controlling the first hydraulic pump and the second hydraulic pump to supply oil in a converging manner or a shunting manner. When the hoisting mechanism needs to perform composite action with one of telescopic motion of the cargo boom and amplitude variation of the cargo boom, the shunting and converging control assembly is switched to a shunting state, so that the first hydraulic pump supplies oil to the hoisting control assembly, and the second hydraulic pump only supplies oil to the telescopic control assembly or the amplitude variation control assembly. Therefore, the phenomenon that the flow distribution is influenced by different loads of the executing mechanisms can be avoided without additionally installing a differential pressure compensation valve, and further, the pressure loss and the power loss of the hydraulic control system can be reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulic systems, in particular to a hydraulic control system and an operating machine. Background Art

[0002] Cranes are widely used operating machines in engineering construction. In the existing hydraulic control systems used to drive cranes for lifting operations, hydraulic pumps are usually used as power sources to drive the actions of the hoisting mechanism, telescopic arm, and luffing actuator. During the operation process, the hoisting mechanism, telescopic arm, and luffing actuator of the crane usually perform single actuator actions, or the hoisting mechanism and one of the telescopic arm and luffing actuator perform compound actions. In order to avoid the phenomenon that the different load pressures in the compound action of the hoisting mechanism and the telescopic arm or the luffing mechanism affect the distribution of the output flow of the hydraulic pump, a pressure differential compensation valve is usually provided at the hoisting control valve, the telescopic control valve, and the luffing control valve. However, the pressure differential compensation valve will inevitably generate a pressure difference during operation, which will cause a certain pressure loss and power loss. Utility Model Content

[0003] The utility model provides a hydraulic control system and an operating machine, which are used to solve the problem that in the existing hydraulic control system for driving a crane to perform lifting operations, a pressure difference compensation valve is added to avoid the phenomenon that different load pressures in the compound action of a hoisting mechanism and a telescopic arm or a luffing mechanism affect the distribution of the output flow of a hydraulic pump, which will cause a certain pressure loss and power loss.

[0004] According to a first aspect of the utility model, a hydraulic control system is provided, comprising a first hydraulic pump, a second hydraulic pump, a winch control component, a telescopic control component, a luffing control component and a separation and merging control component.

[0005] The first hydraulic pump is connected to the hoisting control assembly. The second hydraulic pump is connected to the telescopic control assembly and the amplitude control assembly. The telescopic control assembly and the amplitude control assembly are arranged in parallel. The split-and-join flow control assembly is connected between the first hydraulic pump and the second hydraulic pump and is used to control the first hydraulic pump and the second hydraulic pump to join or split the flow of oil.

[0006] According to a hydraulic control system provided by the utility model, the hoisting control assembly includes a hoisting actuator, a hoisting reversing control valve, a first hoisting pilot valve and a second hoisting pilot valve. The first hydraulic pump is connected to the hoisting reversing control valve. The hoisting reversing control valve is connected to the hoisting actuator. The first hoisting pilot valve and the second hoisting pilot valve are connected to the control oil port of the hoisting reversing control valve to control the switching of the working position of the hoisting reversing control valve.

[0007] The hydraulic control system further comprises a main control valve, the second hydraulic pump is connected to the main control valve, and the main control valve is connected to the first hoisting pilot valve and the second hoisting pilot valve.

[0008] According to a hydraulic control system provided by the utility model, the telescopic control component includes a telescopic actuator, a telescopic reversing control valve, a first telescopic pilot valve and a second telescopic pilot valve. The second hydraulic pump is connected to the telescopic reversing control valve. The telescopic reversing control valve is connected to the telescopic actuator. The first telescopic pilot valve and the second telescopic pilot valve are connected to the control oil port of the telescopic reversing valve control valve to control the switching of the working position of the telescopic reversing control valve. The main control valve is connected to the first telescopic pilot valve and the second telescopic pilot valve.

[0009] According to a hydraulic control system provided by the utility model, the amplitude control component includes an amplitude actuator, an amplitude reversing control valve, a first amplitude pilot valve and a second amplitude pilot valve. The second hydraulic pump is connected to the amplitude reversing control valve. The amplitude reversing control valve is connected to the amplitude actuator. The amplitude reversing control valve is arranged in parallel with the telescopic reversing control valve. The first amplitude pilot valve and the second amplitude pilot valve are connected to the control oil port of the amplitude reversing control valve to control the switching of the working position of the amplitude reversing control valve. The main control valve is connected to the first amplitude pilot valve and the second amplitude pilot valve.

[0010] According to a hydraulic control system provided by the utility model, the split-and-join flow control component includes a main oil circuit split-and-join flow control valve and a total split-and-join flow pilot valve.

[0011] Wherein, the main control valve is connected to the control oil port of the main oil circuit separation and merging control valve through the main separation and merging pilot valve. The main separation and merging pilot valve is used to control the working position of the main oil circuit separation and merging control valve. The main oil circuit separation and merging control valve is connected between the first hydraulic pump and the second hydraulic pump. The main oil circuit separation and merging control valve is used to control the first hydraulic pump and the second hydraulic pump to merge the oil supply or separate the oil supply.

[0012] According to a hydraulic control system provided by the utility model, the first hydraulic pump includes a first load pressure feedback oil port. The second hydraulic pump includes a second load pressure feedback oil port. The separation and confluence control assembly also includes a load feedback separation and confluence control valve. The main control valve is connected to the control oil port of the load feedback separation and confluence control valve through the main separation and confluence pilot valve. The main separation and confluence pilot valve is used to control the working position of the load feedback separation and confluence control valve.

[0013] The hydraulic control system further includes a first shuttle valve, a second shuttle valve and a third shuttle valve. The first oil inlet of the first shuttle valve is connected to the winch reversing control valve. The second oil inlet of the first shuttle valve is connected to the oil outlet of the second shuttle valve through the load feedback flow separation and merging control valve. The oil outlet of the first shuttle valve is connected to the first load pressure feedback oil outlet. The first oil inlet of the second shuttle valve is connected to the telescopic reversing control valve. The second oil inlet of the second shuttle valve is connected to the amplitude reversing control valve. The oil outlet of the second shuttle valve is connected to the first oil inlet of the third shuttle valve. The second oil inlet of the third shuttle valve is connected to the oil outlet of the first shuttle valve. The oil outlet of the third shuttle valve is connected to the second load pressure feedback oil outlet.

[0014] According to a hydraulic control system provided by the utility model, a pressure reducing valve is arranged between the second hydraulic pump and the main control valve.

[0015] According to a hydraulic control system provided by the utility model, a first overflow valve is provided at the oil outlet of the first hydraulic pump, and a second overflow valve is provided at the oil outlet of the second hydraulic pump.

[0016] According to a hydraulic control system provided by the utility model, both the first relief valve and the second relief valve are electric proportional relief valves.

[0017] According to a second aspect of the utility model, a working machine is provided, comprising the hydraulic control system as described above.

[0018] The hydraulic control system provided by the utility model includes a first hydraulic pump, a second hydraulic pump, a winch control assembly, a telescopic control assembly, a boom control assembly and a separation and confluence control assembly. The winch control assembly is used to drive the crane's winch mechanism to be retracted and extended to lift heavy objects. The telescopic control assembly is used to drive the crane's boom to be telescopic to adjust the length of the boom. The boom control assembly is used to adjust the operating angle of the boom. In order to ensure the safety of the operation, in the actual working process, the retraction and extension of the winch mechanism, the telescopic movement of the boom and the boom boom are usually performed separately, or the retraction and extension of the winch mechanism and one of the telescopic movement of the boom and the boom boom are performed in combination.

[0019] The first hydraulic pump is connected to the hoisting control assembly, and it can supply hydraulic oil to the hoisting control assembly. The second hydraulic pump is connected to the telescopic control assembly and the amplitude control assembly, and the telescopic control assembly and the amplitude control assembly are arranged in parallel, and the second hydraulic pump can supply hydraulic oil to the telescopic control assembly and the amplitude control assembly respectively. A split-and-joint flow control assembly is arranged between the first hydraulic pump and the second hydraulic pump, and the split-and-joint flow control assembly can control the first hydraulic pump and the second hydraulic pump to join the oil supply or split the oil supply. In actual use, when the hoisting mechanism and the telescopic and boom of the boom are required to perform a composite action, the split-and-joint flow control assembly is switched to the split state, so that the first hydraulic pump supplies oil to the hoisting control assembly, and the second hydraulic pump only supplies oil to the telescopic control assembly or the amplitude control assembly. Among them, which one of the telescopic control assembly or the amplitude control assembly the second hydraulic pump supplies oil to depends on the respective working states of the telescopic control assembly and the amplitude control assembly. For example, when the winch mechanism needs to be retracted and extended and the boom needs to be extended and retracted, the winch control assembly and the retracting control assembly are switched to a connected state, and the split-and-joint flow control valve is switched to a split-flow state. Alternatively, when the winch mechanism needs to be retracted and extended and the boom needs to be luffed, the winch control assembly and the luffing control assembly are switched to a connected state, and the split-and-joint flow control valve is switched to a split-flow state.

[0020] Through the above-mentioned structural setting, the phenomenon that the loads of various actuators affect the flow distribution can be avoided without installing an additional pressure difference compensation valve, thereby reducing the pressure loss and power loss of the hydraulic control system.

[0021] Furthermore, in the working machine provided by the present invention, since it includes the hydraulic control system as described above, it also has the advantages as described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0023] Figure 1 It is a system principle diagram of the hydraulic control system provided by the utility model.

[0024] Figure numerals: 100, first hydraulic pump; 200, second hydraulic pump; 310, winch reversing control valve; 320, first winch pilot valve; 330, second winch pilot valve; 400, main control valve; 510, telescopic reversing control valve; 520, first telescopic pilot valve; 530, second telescopic pilot valve; 610, amplitude reversing control valve; 620, first amplitude pilot valve; 630, second amplitude pilot valve; 710, main oil circuit separation and confluence control valve; 720, main separation and confluence pilot valve; 730, load feedback separation and confluence control valve; LS1, first load pressure feedback oil port; LS2, second load pressure feedback oil port; 810, first shuttle valve; 820, second shuttle valve; 830, third shuttle valve; 910, pressure reducing valve; 920, first relief valve; 930, second relief valve. DETAILED DESCRIPTION

[0025] The following is a further detailed description of the implementation of the present utility model in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present utility model, but cannot be used to limit the scope of the present utility model.

[0026] In the description of the embodiments of the present utility model, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the embodiments of the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the embodiments of the present utility model. In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0027] In the description of the embodiments of the present utility model, it should be noted that, unless otherwise clearly specified and limited, the terms "connected" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the embodiments of the present utility model can be understood according to specific circumstances.

[0028] In the embodiments of the present invention, unless otherwise clearly specified and limited, the first feature being "above" or "below" the second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "above" and "above" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. The first feature being "below", "below" and "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0029] In the description of this specification, the description of reference terms such as "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model embodiment. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, in the absence of mutual contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples to make the purpose, technical solutions and advantages of the utility model embodiment clearer. The technical solutions in the utility model embodiment will be clearly and completely described below in conjunction with the drawings in the utility model embodiment. Obviously, the described embodiments are part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in the field without making creative work belong to the scope of protection of the utility model.

[0030] Combine the following Figure 1 A hydraulic control system and a working machine provided by an embodiment of the utility model are described. It should be understood that the following description is only an illustrative implementation of the utility model and does not constitute any particular limitation to the utility model.

[0031] The embodiment of the first aspect of the utility model provides a hydraulic control system, such as Figure 1 As shown, the hydraulic control system includes a first hydraulic pump 100, a second hydraulic pump 200, a hoisting control component, a telescopic control component, a luffing control component and a separation and merging control component.

[0032] The first hydraulic pump 100 is connected to the winch control assembly. The second hydraulic pump 200 is connected to the telescopic control assembly and the amplitude control assembly. The telescopic control assembly and the amplitude control assembly are arranged in parallel. The split-and-join control assembly is connected between the first hydraulic pump 100 and the second hydraulic pump 200, and is used to control the first hydraulic pump 100 and the second hydraulic pump 200 to join or split the oil supply.

[0033] The hydraulic control system provided by the utility model includes a first hydraulic pump 100, a second hydraulic pump 200, a hoisting control component, a telescopic control component, a boom control component and a separation and converging control component. The hoisting control component is used to drive the hoisting mechanism of the crane to be retracted and extended to lift heavy objects. The telescopic control component is used to drive the crane's boom to be retracted and extended to adjust the length of the boom. The boom control component is used to adjust the operating angle of the boom. In order to ensure the safety of the operation, in the actual working process, the retraction and extension of the hoisting mechanism, the extension and retraction of the boom, and the boom boom are usually performed separately, or the retraction and extension of the hoisting mechanism and one of the extension and retraction of the boom and the boom boom are performed in combination.

[0034] The first hydraulic pump 100 is connected to the hoisting control assembly, and it can supply hydraulic oil to the hoisting control assembly. The second hydraulic pump 200 is connected to the telescopic control assembly and the amplitude control assembly, and the telescopic control assembly and the amplitude control assembly are arranged in parallel, and the second hydraulic pump 200 can supply hydraulic oil to the telescopic control assembly and the amplitude control assembly respectively. A split-and-joint flow control assembly is arranged between the first hydraulic pump 100 and the second hydraulic pump 200, and the split-and-joint flow control assembly can control the first hydraulic pump 100 and the second hydraulic pump 200 to join and supply oil or split and supply oil. In actual use, when the hoisting mechanism and the telescopic and boom of the boom are required to perform a composite action, the split-and-joint flow control assembly is switched to the split state, so that the first hydraulic pump 100 supplies oil to the hoisting control assembly, and the second hydraulic pump 200 only supplies oil to the telescopic control assembly or the amplitude control assembly. Among them, which one of the telescopic control assembly or the amplitude control assembly the second hydraulic pump 200 supplies oil to depends on the respective working states of the telescopic control assembly and the amplitude control assembly. For example, when the winch mechanism needs to be retracted and extended and the boom needs to be extended and retracted, the winch control assembly and the retracting control assembly are switched to a connected state, and the split-and-joint flow control valve is switched to a split-flow state. Alternatively, when the winch mechanism needs to be retracted and extended and the boom needs to be luffed, the winch control assembly and the luffing control assembly are switched to a connected state, and the split-and-joint flow control valve is switched to a split-flow state.

[0035] Through the above-mentioned structural setting, the phenomenon that the loads of various actuators affect the flow distribution can be avoided without installing an additional pressure difference compensation valve, thereby reducing the pressure loss and power loss of the hydraulic control system.

[0036] In addition, during the separate actions of the hoisting mechanism retracting and extending, the boom telescopic and the boom amplitude variation, when the speed of the corresponding action needs to be increased, the split-and-joint control component can be switched to the merge state. For example, when the speed of the independent retracting and extending action of the hoisting mechanism needs to be increased, the hoisting control component is switched to the connected state, the telescopic control component and the amplitude variation control component are switched to the cut-off state, and the split-and-joint control component is switched to the merge state, so that the first hydraulic pump 100 and the second hydraulic pump 200 merge to supply the hoisting control component.

[0037] In one embodiment of the utility model, the hoisting control assembly includes a hoisting actuator, a hoisting reversing control valve 310, a first hoisting pilot valve 320 and a second hoisting pilot valve 330. The first hydraulic pump 100 is connected to the hoisting reversing control valve 310. The hoisting reversing control valve 310 is connected to the hoisting actuator. The first hoisting pilot valve 320 and the second hoisting pilot valve 330 are connected to the control oil port of the hoisting reversing control valve 310 to control the switching of the working position of the hoisting reversing control valve 310.

[0038] The hydraulic control system further includes a main control valve 400. The second hydraulic pump 200 is connected to the main control valve 400. The main control valve 400 is connected to the first hoisting pilot valve 320 and the second hoisting pilot valve 330.

[0039] In one embodiment of the utility model, the telescopic control assembly includes a telescopic actuator, a telescopic reversing control valve 510, a first telescopic pilot valve 520 and a second telescopic pilot valve 530. The second hydraulic pump 200 is connected to the telescopic reversing control valve 510. The telescopic reversing control valve 510 is connected to the telescopic actuator. The first telescopic pilot valve 520 and the second telescopic pilot valve 530 are connected to the control oil port of the telescopic reversing valve control valve to control the switching of the working position of the telescopic reversing control valve 510. The main control valve 400 is connected to the first telescopic pilot valve 520 and the second telescopic pilot valve 530.

[0040] Further, in one embodiment of the utility model, the amplitude control assembly includes an amplitude actuator, an amplitude reversing control valve 610, a first amplitude pilot valve 620 and a second amplitude pilot valve 630. The second hydraulic pump 200 is connected to the amplitude reversing control valve 610. The amplitude reversing control valve 610 is connected to the amplitude actuator. The amplitude reversing control valve 610 is arranged in parallel with the telescopic reversing control valve 510. The first amplitude pilot valve 620 and the second amplitude pilot valve 630 are connected to the control oil port of the amplitude reversing control valve 610 to control the switching of the working position of the amplitude reversing control valve 610. The main control valve 400 is connected to the first amplitude pilot valve 620 and the second amplitude pilot valve 630.

[0041] Specifically, if Figure 1As shown, the winch reversing control valve 310, the telescopic reversing control valve 510, and the variable amplitude reversing control valve 610 are all hydraulically controlled reversing valves. The first control oil port and the second control oil port are respectively provided at both ends of the winch reversing control valve 310, the telescopic reversing control valve 510, and the variable amplitude reversing control valve 610. And all three are provided with a forward working position, a reverse working position, and a working stop position. The working position of the corresponding control valve can be controlled by controlling the pressure at each first control oil port and the second control oil port. For example, when the winch reversing control valve 310 is switched to the forward working position, the winch actuator can drive the winch mechanism to perform a lifting action, when the winch reversing valve is switched to the reverse working position, the winch actuator can drive the winch mechanism to perform a lowering action, and when the winch reversing valve is switched to the working stop position, the winch actuator remains stationary, and accordingly, the winch mechanism also remains in the current state unchanged. The working process of the telescopic reversing control valve 510 and the variable amplitude reversing control valve 610 is similar.

[0042] The first hoist pilot valve 320, the second hoist pilot valve 330, the first telescopic pilot valve 520, the second telescopic pilot valve 530, the first amplitude-changing pilot valve 620, the second amplitude-changing pilot valve 630 and the main control valve 400 are all electromagnetic reversing valves. Among them, the second hydraulic pump 200 can be connected to the first hoist pilot valve 320, the second hoist pilot valve 330, the first telescopic pilot valve 520, the second telescopic pilot valve 530, the first amplitude-changing pilot valve 620, and the second amplitude-changing pilot valve 630 through the main control valve 400, and further, can be connected to the first control oil port and the second control oil port of the hoist reversing control valve 310, the first control oil port and the second control oil port of the telescopic reversing control valve 510, and the first control oil port and the second control oil port of the amplitude-changing reversing control valve 610. The first winch pilot valve 320, the second winch pilot valve 330, the first telescopic pilot valve 520, the second telescopic pilot valve 530, the first amplitude-changing pilot valve 620, the second amplitude-changing pilot valve 630 and the main control valve 400 all include a connected state and a cut-off state. When the main control valve 400 is in the connected state, the oil output by the second hydraulic pump 200 can be respectively delivered to the first winch pilot valve 320, the second winch pilot valve 330, the first telescopic pilot valve 520, the second telescopic pilot valve 530, the first amplitude-changing pilot valve 620 and the second amplitude-changing pilot valve 630 through the main control valve 400, and then, the operator can switch the working state of the corresponding pilot valve to the connected state according to the actual action requirements. For example, when it is necessary to make the winch mechanism perform lifting action independently, the main control valve 400 is switched to the connected state, the first winch pilot valve 320 is switched to the connected state, and the second winch pilot valve 330, the first telescopic pilot valve 520, the second telescopic pilot valve 530, the first amplitude-changing pilot valve 620 and the second amplitude-changing pilot valve 630 are all maintained in the cut-off state. At this time, if the flow separation and confluence control component is in the diversion state, the first hydraulic pump 100 drives the winch actuator through the winch reversing control valve 310 to drive the winch mechanism to perform lifting action. If the flow separation and confluence control component is in the confluence state, the first hydraulic pump 100 and the second hydraulic pump 200 merge and then drive the winch actuator through the winch reversing control valve 310 to drive the winch mechanism to accelerate the lifting action.

[0043] In one embodiment of the present invention, the flow separation and merging control assembly includes a main oil circuit flow separation and merging control valve 710 and a total flow separation and merging pilot valve 720 .

[0044] The main control valve 400 is connected to the control oil port of the main oil circuit separation and confluence control valve 710 through the main separation and confluence pilot valve 720. The main separation and confluence pilot valve 720 is used to control the working position of the main oil circuit separation and confluence control valve 710. The main oil circuit separation and confluence control valve 710 is connected between the first hydraulic pump 100 and the second hydraulic pump 200. The main oil circuit separation and confluence control valve 710 is used to control the confluence or separation of the first hydraulic pump 100 and the hydraulic pump.

[0045] Further, in one embodiment of the utility model, the first hydraulic pump 100 includes a first load pressure feedback oil port LS1. The second hydraulic pump 200 includes a second load pressure feedback oil port LS2. The split-and-join flow control assembly also includes a load feedback split-and-join flow control valve 730. The main control valve 400 is connected to the control oil port of the load feedback split-and-join flow control valve 730 through the main split-and-join flow pilot valve 720. The main split-and-join flow pilot valve 720 is used to control the working position of the load feedback split-and-join flow control valve 730.

[0046] The hydraulic control system further includes a first shuttle valve 810, a second shuttle valve 820 and a third shuttle valve 830. The first oil inlet of the first shuttle valve 810 is connected to the winch reversing control valve 310. The second oil inlet of the first shuttle valve 810 is connected to the oil outlet of the second shuttle valve 820 through the load feedback separation and confluence control valve 730. The oil outlet of the first shuttle valve 810 is connected to the first load pressure feedback oil port LS1. The first oil inlet of the second shuttle valve 820 is connected to the telescopic reversing control valve 510. The second oil inlet of the second shuttle valve 820 is connected to the amplitude reversing control valve 610. The oil outlet of the second shuttle valve 820 is connected to the first oil inlet of the third shuttle valve 830. The second oil inlet of the third shuttle valve 830 is connected to the oil outlet of the first shuttle valve 810. The oil outlet of the third shuttle valve 830 is connected to the second load pressure feedback oil port LS2.

[0047] For example, Figure 1 As shown, the main oil circuit split-and-join pilot valve 720 is an electromagnetic reversing valve. The main oil circuit split-and-join control valve 710 is a hydraulically controlled reversing valve, which is provided with a control spring on one side and a control oil port on the other side. The second hydraulic pump 200 is connected to the main oil circuit split-and-join pilot valve 720 through the main control valve 400, and the main oil circuit split-and-join pilot valve 720 is connected to the control oil port of the main oil circuit split-and-join control valve 710. The main oil circuit split-and-join control valve 710 includes a split position and a joining position. Figure 1In the state shown, the main control valve 400 is in the cut-off state when it is not powered on, that is, the second hydraulic pump 200 is cut off from the control oil port of the main oil circuit dividing and merging control valve 710 through the main control valve 400. At this time, the main oil circuit dividing and merging control valve 710 is in the merging position, that is, the oil outlet of the first hydraulic pump 100 can be connected with the oil outlet of the second hydraulic pump 200. When the main control valve 400 is powered on and switched to the connected state, the oil output by the second hydraulic pump 200 can be delivered to the control oil port of the main oil circuit dividing and merging control valve 710 through the main control valve 400 to drive the main oil circuit dividing and merging control valve 710 to switch to the diverting position. At this time, the oil outlet of the first hydraulic pump 100 and the oil outlet of the second hydraulic pump 200 are cut off from each other, and the two are in the diverting oil supply state.

[0048] In this embodiment, the first hydraulic pump 100 and the second hydraulic pump 200 are both load-sensitive hydraulic pumps. The first hydraulic pump 100 includes a first load pressure feedback oil port LS1, and the second hydraulic pump 200 includes a second load pressure feedback oil port LS2. The split-and-join flow control assembly also includes a load feedback split-and-join flow control valve 730. Among them, the load feedback split-and-join flow control valve 730 is a hydraulically controlled reversing valve, and a control spring and a control oil port are respectively provided at both ends. The second hydraulic pump 200 is connected to the total split-and-join flow pilot valve 720 through the total control valve 400, and the total split-and-join flow pilot valve 720 is connected to the control oil port of the load feedback split-and-join flow control valve 730 to adjust the working position of the load feedback split-and-join flow control valve 730. The load feedback split-and-join flow control valve 730 includes a split-and-join flow feedback position and a joining flow feedback position.

[0049] The first oil inlet of the first shuttle valve 810 is connected to the working oil port of the winch reversing control valve 310, and the second oil inlet of the first shuttle valve 810 is connected to the oil outlet of the second shuttle valve 820 through the working oil port of the load feedback separation and confluence control valve 730. The oil outlet of the first shuttle valve 810 is connected to the first load pressure feedback oil port LS1. When the load feedback separation and confluence control valve 730 is in the separation feedback position, the second oil inlet of the first shuttle valve 810 and the oil outlet of the second shuttle valve 820 are cut off; when the load feedback separation and confluence control valve 730 is in the confluence feedback position, the second oil inlet of the first shuttle valve 810 is connected to the oil outlet of the second shuttle valve 820.

[0050] The first oil inlet of the second shuttle valve 820 is connected to the working oil port of the telescopic reversing control valve 510. The second oil inlet of the second shuttle valve 820 is connected to the working oil port of the amplitude reversing control valve 610. The oil outlet of the second shuttle valve 820 is connected to the first oil inlet of the third shuttle valve 830. The second oil inlet of the third shuttle valve 830 is connected to the oil outlet of the first shuttle valve 810. The oil outlet of the third shuttle valve 830 is connected to the second load pressure feedback oil port LS2.

[0051] That is, the pressure at the oil outlet of the first shuttle valve 810 can be fed back to the first load pressure feedback oil port LS1 of the first hydraulic pump 100 to adjust the output flow of the first hydraulic pump 100. The pressure at the oil outlet of the third shuttle valve 830 can be fed back to the second load pressure feedback oil port LS2 of the second hydraulic pump 200 to adjust the output flow of the second hydraulic pump 200.

[0052] When the main oil circuit split-and-join control valve 710 is in the split position, the load feedback split-and-join control valve 730 should be in the split feedback position. When the main oil circuit split-and-join control valve 710 is in the join position, the load feedback split-and-join control valve 730 should be in the join feedback position.

[0053] In actual operation, when the main oil circuit flow separation and confluence control valve 710 is in the flow separation position, and the load feedback flow separation and confluence control valve 730 is in the flow separation feedback position, the pressure at the first load pressure feedback oil port LS1 is the pressure at the hoisting direction reversing control valve 310, that is, the load pressure of the hoisting actuator. The pressure at the second load pressure feedback oil port LS2 is the maximum output pressure of the hoisting direction reversing control valve 310, the telescopic direction reversing control valve 510, and the amplitude reversing control valve 610, that is, the maximum load pressure of the hoisting actuator, the telescopic actuator, and the amplitude reversing actuator. When the main oil circuit flow separation and confluence control valve 710 is in the confluence position, and the load feedback flow separation and confluence control valve 730 is in the confluence feedback position, the pressures at the first load pressure feedback oil port LS1 and the second load feedback oil port are equal, both of which are the maximum output pressure of the hoisting direction reversing control valve 310, the telescopic direction reversing control valve 510, and the amplitude reversing control valve 610, that is, the maximum load pressure of the hoisting actuator, the telescopic actuator, and the amplitude reversing actuator.

[0054] Since the second hydraulic pump 200 is used to supply the telescopic control component or the amplitude control component, its output pressure is relatively large. In order to ensure the working safety of the pilot oil circuit, a pressure reducing valve 910 can be provided between the second hydraulic pump 200 and the main control valve 400.

[0055] In addition, a first relief valve 920 is provided between the oil outlet of the first hydraulic pump 100 and the oil tank, and a second relief valve 930 is provided between the oil outlet of the second hydraulic pump 200 and the oil tank to ensure the safety of the entire hydraulic control system.

[0056] Among them, in one embodiment of the utility model, the first relief valve 920 and the second relief valve 930 are both electric proportional relief valves. By setting the working pressure of each electric proportional relief valve in real time, compound action multi-stage pressure control can be completed, and the valve core opening of the winch reversing control valve 310, the telescopic reversing control valve 510 and the variable amplitude reversing control valve 610 can be coordinated to achieve dual pressure and flow control.

[0057] In actual operation, when performing compound actions, the main oil circuit separation and confluence control valve 710 is in the diversion position, and the first relief valve 920 and the second relief valve 930 can respectively set the main pressure of the first hydraulic pump 100 and the second hydraulic pump 200 according to the actual action pressure requirements. When performing a single action, the main oil circuit separation and confluence control valve 710 is in the confluence position, and the first relief valve 920 and the second relief valve 930 can jointly set the main pressure of the first hydraulic pump 100 and the second hydraulic pump 200 according to the actual action pressure requirements. Since the pressure set by the first relief valve 920 and the second relief valve 930 is the required pressure rather than the maximum working pressure of the system, the overflow loss of the entire system is reduced.

[0058] An embodiment of the second aspect of the utility model provides a working machine, comprising the hydraulic control system as described above.

[0059] For example, in one embodiment of the present invention, the working machine is a crane, which includes a boom and a hoisting mechanism. The hydraulic control system drives and controls the retracting and extending action of the hoisting mechanism, as well as the telescopic length of the boom and the adjustment action of the working angle.

[0060] It should be noted that the above embodiment is only an illustrative embodiment of the utility model and does not constitute any limitation to the utility model. That is to say, the above working machinery includes but is not limited to cranes, and any working machinery including the above hydraulic control system should be within the protection scope of the utility model.

[0061] Furthermore, in the working machine provided by the present invention, since it includes the hydraulic control system as described above, it also has the advantages as described above.

[0062] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the utility model, rather than to limit it. Although the utility model has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the utility model.

Claims

1. A hydraulic control system, characterized in that: It comprises a first hydraulic pump (100), a second hydraulic pump (200), a winch control component, a telescopic control component, a luffing control component and a flow separation and merging control component; The first hydraulic pump (100) is connected to the hoisting control component, the second hydraulic pump (200) is connected to the telescopic control component and the amplitude control component, the telescopic control component and the amplitude control component are arranged in parallel, and the merging and splitting control component is connected between the first hydraulic pump (100) and the second hydraulic pump (200), and is used to control the merging or splitting of the first hydraulic pump (100) and the second hydraulic pump (200) for oil supply.

2. The hydraulic control system according to claim 1, characterized in that: The hoist control assembly comprises a hoist actuator, a hoist reversing control valve (310), a first hoist pilot valve (320) and a second hoist pilot valve (330); the first hydraulic pump (100) is connected to the hoist reversing control valve (310); the hoist reversing control valve (310) is connected to the hoist actuator; the first hoist pilot valve (320) and the second hoist pilot valve (330) are connected to the control oil port of the hoist reversing control valve (310) to control the switching of the working position of the hoist reversing control valve (310); The hydraulic control system further comprises a main control valve (400), the second hydraulic pump (200) is connected to the main control valve (400), and the main control valve (400) is connected to the first hoisting pilot valve (320) and the second hoisting pilot valve (330).

3. The hydraulic control system according to claim 2, characterized in that: The telescopic control assembly comprises a telescopic actuator, a telescopic reversing control valve (510), a first telescopic pilot valve (520) and a second telescopic pilot valve (530); the second hydraulic pump (200) is connected to the telescopic reversing control valve (510); the telescopic reversing control valve (510) is connected to the telescopic actuator; the first telescopic pilot valve (520) and the second telescopic pilot valve (530) are connected to the control oil port of the telescopic reversing valve control valve to control the switching of the working position of the telescopic reversing control valve (510); and the main control valve (400) is connected to the first telescopic pilot valve (520) and the second telescopic pilot valve (530).

4. The hydraulic control system according to claim 3, characterized in that: The amplitude control assembly comprises an amplitude actuator, an amplitude reversing control valve (610), a first amplitude pilot valve (620) and a second amplitude pilot valve (630); the second hydraulic pump (200) is connected to the amplitude reversing control valve (610); the amplitude reversing control valve (610) is connected to the amplitude actuator; the amplitude reversing control valve (610) is arranged in parallel with the telescopic reversing control valve (510); the first amplitude pilot valve (620) and the second amplitude pilot valve (630) are connected to the control oil port of the amplitude reversing control valve (610) to control the switching of the working position of the amplitude reversing control valve (610); and the main control valve (400) is connected to the first amplitude pilot valve (620) and the second amplitude pilot valve (630).

5. The hydraulic control system according to claim 4, characterized in that: The split-and-join flow control assembly comprises a main oil circuit split-and-join flow control valve (710) and a main split-and-join flow pilot valve (720). The main control valve (400) is connected to the control oil port of the main oil circuit separation and merging control valve (710) through the main separation and merging pilot valve (720); the main separation and merging pilot valve (720) is used to control the working position of the main oil circuit separation and merging control valve (710); the main oil circuit separation and merging control valve (710) is connected between the first hydraulic pump (100) and the second hydraulic pump (200); the main oil circuit separation and merging control valve (710) is used to control the first hydraulic pump (100) and the second hydraulic pump (200) to merge or separate the oil supply.

6. The hydraulic control system according to claim 5, characterized in that: The first hydraulic pump (100) comprises a first load pressure feedback oil port (LS1), the second hydraulic pump (200) comprises a second load pressure feedback oil port (LS2), the flow separation and merging control assembly further comprises a load feedback flow separation and merging control valve (730), the main control valve (400) is connected to the control oil port of the load feedback flow separation and merging control valve (730) via the main flow separation and merging pilot valve (720), the main flow separation and merging pilot valve (720) is used to control the working position of the load feedback flow separation and merging control valve (730), The hydraulic control system further comprises a first shuttle valve (810), a second shuttle valve (820) and a third shuttle valve (830); a first oil inlet of the first shuttle valve (810) is connected to the winch reversing control valve (310); a second oil inlet of the first shuttle valve (810) is connected to an oil outlet of the second shuttle valve (820) via the load feedback flow separation and confluence control valve (730); an oil outlet of the first shuttle valve (810) is connected to the first load pressure feedback oil port (LS1); and a second oil inlet of the first shuttle valve (810) is connected to an oil outlet of the second shuttle valve (820) via the load feedback flow separation and confluence control valve (730). The first oil inlet of the valve (820) is connected to the telescopic reversing control valve (510), the second oil inlet of the second shuttle valve (820) is connected to the amplitude-changing reversing control valve (610), the oil outlet of the second shuttle valve (820) is connected to the first oil inlet of the third shuttle valve (830), the second oil inlet of the third shuttle valve (830) is connected to the oil outlet of the first shuttle valve (810), and the oil outlet of the third shuttle valve (830) is connected to the second load pressure feedback oil port (LS2).

7. The hydraulic control system according to claim 2, characterized in that: A pressure reducing valve (910) is provided between the second hydraulic pump (200) and the main control valve (400).

8. The hydraulic control system according to claim 1, characterized in that: A first overflow valve (920) is provided at the oil outlet of the first hydraulic pump (100), and a second overflow valve (930) is provided at the oil outlet of the second hydraulic pump (200).

9. The hydraulic control system according to claim 8, characterized in that: The first relief valve (920) and the second relief valve (930) are both electric proportional relief valves.

10. A working machine, characterized in that: Comprising a hydraulic control system according to any one of claims 1 to 9.

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