CN214935623U - Hydraulic control system and cable tensioning system - Google Patents

Abstract

A hydraulic control system and a cable tensioning system, the hydraulic control system comprises a hydraulic motor, a hydraulic oil tank, a quantitative hydraulic pump and a variable hydraulic pump, wherein the quantitative hydraulic pump and the variable hydraulic pump are communicated with the hydraulic oil tank; the hydraulic control system also comprises a valve body assembly, wherein the valve body assembly comprises a hydraulic control reversing valve group and a mode switching valve, and the hydraulic control reversing valve group comprises a hydraulic control reversing valve; the first working end of the hydraulic control reversing valve is connected with the variable hydraulic pump; the first working end of the mode switching valve is connected with the quantitative hydraulic pump and is configured to be communicated with the variable hydraulic pump, the hydraulic control reversing valve and the hydraulic motor to form a first oil supply loop when the mode switching valve is switched to the first conduction state. The driving process of the hydraulic control system is safe and reliable, and the hydraulic control system is easy to operate.

Description

Hydraulic control system and cable tensioning system

Technical Field

Embodiments of the present disclosure relate to a hydraulic control system and a cable tensioning system.

Background

When the deep sea operation robot carries out underwater operation, an umbilical cable is required to be connected to a power supply system and a control system of a ship. In a non-operation state, an umbilical cable needs to be wound on an umbilical cable winch drum to realize storage, a certain pretightening force needs to be applied to the cable in the winding process, the pretightening force can be several tons or dozens of tons, so that the phenomena of cable disorder, cable jumping and the like in the winding process of the winch drum of the cable are avoided, the phenomenon of cable biting caused by bearing large load in the process of lowering and lifting the deep sea operation robot and an auxiliary system of the deep sea operation robot is avoided, therefore, equipment for simulating the applied load to increase the pretightening force is needed when the cable is wound, and the equipment is called a cable tensioner.

SUMMERY OF THE UTILITY MODEL

At least one embodiment of the present disclosure provides a hydraulic control system, which includes a hydraulic motor, a hydraulic tank, and a fixed-displacement hydraulic pump and a variable-displacement hydraulic pump communicated with the hydraulic tank, wherein the hydraulic tank may contain a liquid; the valve body assembly comprises a hydraulic control reversing valve group and a mode switching valve, and the hydraulic control reversing valve group comprises a hydraulic control reversing valve; the first working end of the hydraulic control reversing valve is connected with the variable hydraulic pump; the first working end of the mode switching valve is connected with a fixed displacement hydraulic pump, and the mode switching valve is configured to be in a first conduction state, so that the variable displacement hydraulic pump, the hydraulic control reversing valve and the hydraulic motor are communicated to form a first oil supply loop.

For example, in the hydraulic control system provided by at least one embodiment of the present disclosure, the valve body assembly further includes a pilot relief valve and a pilot-controlled relief valve that controls a working pressure of the pilot relief valve, and when the mode switching valve is switched to the second conduction state, the hydraulic motor is communicated with the pilot relief valve and the pilot-controlled relief valve to form a second oil supply circuit.

For example, in the hydraulic control system provided in at least one embodiment of the present disclosure, the hydraulic motor has a first oil port and a second oil port, the first oil port and the second oil port are respectively connected to the second working end and the third working end of the hydraulic control directional control valve, the valve body assembly further includes a selection handle valve group, the selection handle valve group is connected to the fixed-displacement hydraulic pump, and has a first control valve and a second control valve, the first control valve and the second control valve are respectively connected to the first control end and the second control end of the hydraulic control directional control valve, and are configured to select a conduction state of the hydraulic control directional control valve, so as to control one of the first oil port and the second oil port to be an oil inlet and the other to be an oil outlet.

For example, in the hydraulic control system provided by at least one embodiment of the present disclosure, the pilot-controlled directional valve set further includes two relief valves, and the two relief valves are respectively configured to be communicable with the second working end and the third working end of the pilot-controlled directional valve, so as to limit the pressure fed back to the variable hydraulic pump by the second working end and the third working end.

For example, at least one embodiment of the present disclosure provides a hydraulic control system, wherein a first shuttle valve is disposed between the two relief valves, and is configured to select a maximum pressure transmitted from the second working end and the third working end to be returned to the variable displacement hydraulic pump.

For example, in the hydraulic control system provided by at least one embodiment of the present disclosure, the valve body assembly further includes a first on-off valve between the third working end and the second oil port of the pilot-operated directional valve, and the first on-off valve is configured to be opened when the mode switching valve is switched to the first conduction state, and to be closed when the mode switching valve is switched to the second conduction state.

For example, in a hydraulic control system provided by at least one embodiment of the present disclosure, the mode switching valve includes a two-position four-way valve, the first switch valve includes a first two-position two-way valve, and a control end of the first two-position two-way valve is connected to the first working end of the mode switching valve so as to be controlled by the mode switching valve.

For example, at least one embodiment of the present disclosure provides a hydraulic control system further including a brake, wherein the valve body assembly further includes a brake valve and a second shuttle valve, the brake valve being connected to the first control valve and the second control valve through the second shuttle valve, configured to control the brake-lock target driving device when the first control valve and the second control valve are in a disconnected state, and to control the brake-unlock target driving device when the first control valve or the second control valve is in an opened state.

For example, in a hydraulic control system provided in at least one embodiment of the present disclosure, the valve body assembly further includes an oil supply anti-impact valve group connecting the first oil port and the second oil port, and the oil supply anti-impact valve group is configured to supply oil to one of the first oil port and the second oil port.

For example, in the hydraulic control system provided in at least one embodiment of the present disclosure, the oil replenishment anti-impact valve group includes a first check valve connected to the first oil port and a first overflow valve connected to the first check valve, and further includes a second check valve connected to the second oil port and a second overflow valve connected to the second check valve, and the configuration is such that the first oil port is an oil inlet and the second oil port is an oil outlet.

For example, at least one embodiment of the present disclosure provides a hydraulic control system, wherein the valve body assembly further includes a second on-off valve between the pilot relief valve and the pilot relief valve, the second on-off valve being opened when the mode switching valve is switched to the second conduction state, and the second on-off valve being closed when the mode switching valve is switched to the first conduction state.

For example, in a hydraulic control system provided by at least one embodiment of the present disclosure, the mode switching valve includes a two-position four-way valve, and the second switching valve includes a second two-position two-way valve, and a control end of the second two-position two-way valve is connected to the second working end of the mode switching valve so as to be controlled by the mode switching valve.

For example, in the hydraulic control system provided in at least one embodiment of the present disclosure, the valve body assembly further includes an oil replenishment anti-impact overflow valve and a third switch valve, a first working end of the oil replenishment anti-impact overflow valve is connected to the hydraulic oil tank, a second working end of the oil replenishment anti-impact overflow valve is connected to a first working end of the third switch valve, a second working end of the third switch valve is connected to one of the two overflow valves of the hydraulic control directional valve group, and the configuration is that the oil replenishment anti-impact overflow valve is communicated with the first oil port through one of the two overflow valves when the third switch valve is in an open state, and the oil replenishment anti-impact overflow valve is disconnected from the first oil port when the third switch valve is in a disconnected state.

For example, in a hydraulic control system provided by at least one embodiment of the present disclosure, a control end of the third on/off valve is connected to the mode switching valve, and the third on/off valve is configured to be opened when the mode switching valve is switched to the second conduction state, and to be closed when the mode switching valve is switched to the first conduction state.

For example, at least one embodiment of the present disclosure provides the hydraulic control system further including a first filter disposed between the hydraulic oil tank and the fixed displacement hydraulic pump, and a second filter disposed between the hydraulic oil tank and the variable displacement hydraulic pump.

For example, at least one embodiment of the present disclosure provides a hydraulic control system, wherein the fixed displacement hydraulic pump includes a gear pump or a vane pump; the variable displacement hydraulic pump comprises a load-sensitive control plunger pump or a pressure compensation control plunger pump.

At least one embodiment of the present disclosure further provides a cable tensioning system, including the hydraulic control system provided in the embodiment of the present disclosure and a cable tensioner, where the cable tensioner has a normal mode, and when the mode switching valve of the hydraulic control system is switched to the first conduction state, the cable tensioner is in the normal mode, and the cable tensioner can achieve cable retracting and cable releasing functions.

For example, in the cable tensioning system provided by at least one embodiment of the present disclosure, the valve body assembly of the hydraulic control system further includes a pilot relief valve and a hydraulic control relief valve for controlling a working pressure of the pilot relief valve, and when the mode switching valve is switched to the second conduction state, the hydraulic motor is communicated with the pilot relief valve and the hydraulic control relief valve to form a second oil supply loop; the cable tensioner also has a load mode in which the cable tensioner is in the load mode when the mode switching valve is switched to the second conduction state, the cable tensioner being capable of performing a passive payout function to simulate a load weight.

Drawings

To more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description relate only to some embodiments of the present disclosure and are not limiting to the present disclosure.

FIG. 1 is a schematic block diagram of a hydraulic control system provided in accordance with at least one embodiment of the present disclosure;

FIG. 2 is another schematic block diagram of a hydraulic control system provided in accordance with at least one embodiment of the present disclosure;

FIG. 3 is a schematic diagram of the circuit connections of a hydraulic control system provided by at least one embodiment of the present disclosure; and

fig. 4 is a schematic line connection diagram of a cable tensioning system according to at least one embodiment of the present disclosure.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present disclosure more apparent, the technical solutions of the embodiments of the present disclosure will be described clearly and completely with reference to the drawings of the embodiments of the present disclosure. It is to be understood that the described embodiments are only a few embodiments of the present disclosure, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the disclosure without any inventive step, are within the scope of protection of the disclosure.

Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this disclosure belongs. The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather is used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.

At present, a mooring rope tensioning system on the market usually has a simple working mode, only has basic functions of cable winding, cable releasing and the like, a driving system is driven by a driving motor and the like, the function is single, the safety coefficient is low, and the requirements of users cannot be met.

At least one embodiment of the present disclosure provides a hydraulic control system, which includes a hydraulic motor, a hydraulic tank, and a fixed-displacement hydraulic pump and a variable-displacement hydraulic pump communicated with the hydraulic tank, wherein the hydraulic tank may contain a liquid; the hydraulic control system also comprises a valve body assembly, wherein the valve body assembly comprises a hydraulic control reversing valve group and a mode switching valve, and the hydraulic control reversing valve group comprises a hydraulic control reversing valve; the first working end of the hydraulic control reversing valve is connected with the variable hydraulic pump; the first working end of the mode switching valve is connected with the quantitative hydraulic pump and is configured to be communicated with the variable hydraulic pump, the hydraulic control reversing valve and the hydraulic motor to form a first oil supply loop when the mode switching valve is switched to the first conduction state.

At least one embodiment of the present disclosure further provides a cable tensioning system, which includes the above-mentioned hydraulic control system and a cable tensioner, wherein the cable tensioner has a normal mode and a load mode, in the normal mode, the cable tensioner can realize cable retracting and cable releasing functions, in the load mode, the cable tensioner can realize a passive cable releasing function to simulate a load weight, thereby having multiple functionalities; on the other hand, the cable tensioning system is driven by a hydraulic driving device, the driving process is safe and reliable, and the operation is easy.

The hydraulic control system and cable tensioning system provided by the embodiments of the present disclosure are described below in terms of several specific embodiments.

At least one embodiment of the present disclosure provides a hydraulic control system, and fig. 1 shows a schematic block diagram of the hydraulic control system, as shown in fig. 1, the hydraulic control system includes a hydraulic motor 13, a hydraulic oil tank 1, and a fixed-quantity hydraulic pump 5 and a variable-quantity hydraulic pump 6 which are communicated with the hydraulic oil tank 1, and the hydraulic oil tank 1 can contain liquid, such as hydraulic oil or other liquid capable of transmitting power. The hydraulic control system further comprises a valve body assembly, wherein the valve body assembly comprises a hydraulic control reversing valve group and a mode switching valve 16, and the hydraulic control reversing valve group comprises a hydraulic control reversing valve 81; the first working end of the hydraulic control reversing valve 81 is connected with the variable hydraulic pump 6; the mode switching valve 16 has a first working end connected to the fixed displacement hydraulic pump 5, and is configured such that the variable displacement hydraulic pump 6, the pilot-operated directional valve 81, and the hydraulic motor 13 communicate with each other to form a first oil supply circuit when the mode switching valve 16 is switched to the first conduction state.

For example, the hydraulic pressure output by the quantitative hydraulic pump 5 is constant, and is used for providing pilot pressure oil for the valve body assembly to realize the reversing function of each valve in the valve body assembly; the output pressure of the variable hydraulic pump 6 is adjustable, so that different hydraulic pressures are provided, and different driving forces are provided. For example, in some examples, the fixed displacement hydraulic pump 5 may comprise a gear pump or a vane pump, etc.; the variable displacement hydraulic pump 6 includes a load-sensitive control plunger pump or a pressure-compensated control plunger pump or the like. The embodiment of the present disclosure does not limit the specific form of the fixed-amount hydraulic pump 5 and the variable-amount hydraulic pump 6.

For example, in some embodiments, as shown in fig. 2, the valve body assembly may further include a pilot relief valve 20 and a pilot-controlled relief valve 19 that controls the operating pressure of the pilot relief valve 20, and in the switching of the mode switching valve 16 to the second conduction state, the hydraulic motor 13 communicates with the pilot relief valve 20 and the pilot-controlled relief valve 19 to form a second oil supply circuit.

Therefore, the hydraulic control system can be provided with at least two oil supply circuits to realize multi-path oil supply and driving functions. For example, the hydraulic control system may be used to drive a winch, cable tensioner, etc. to place the winch, cable tensioner, etc. in different operating conditions under different oil supply circuits.

For example, fig. 3 shows a specific circuit connection schematic diagram of a hydraulic control system according to at least one embodiment of the present disclosure, as shown in fig. 3, the hydraulic motor 13 has a first oil port a and a second oil port B, the first oil port a and the second oil port B are respectively connected to the second working end C and the third working end D of the hydraulic control directional valve 81, when the hydraulic control directional valve 81 is in different states, a direction of a first oil supply loop formed between the variable displacement hydraulic pump 6, the hydraulic control directional valve 81 and the hydraulic motor 13 may be the hydraulic oil tank 1, the variable displacement hydraulic pump 6, the hydraulic control directional valve 81, the first oil port a of the hydraulic motor 13, the second oil port B of the hydraulic motor 13, the hydraulic control directional valve 81, and the hydraulic oil tank 1, or the first oil supply loop may be the hydraulic oil tank 1, the variable displacement hydraulic pump 6, the hydraulic control directional valve 81, the second oil port B of the hydraulic motor 13, the first oil port a-hydraulic oil change of the hydraulic motor 13 Directional valve 81-hydraulic tank 1.

For example, the hydraulic motor 13 may be connected to the target drive device 14 to drive the target drive device 14 to operate. For example, the target drive 14 may be a winch, a cable tensioner, etc., so that different oil supply circuits of the hydraulic drive system may achieve different operating states of the winch and the cable tensioner.

For example, as shown in fig. 3, in some embodiments, the valve body assembly may further include a selective handle valve group 10, the selective handle valve group 10 is connected to the fixed-displacement hydraulic pump 5, and has a first control valve 01 and a second control valve 02, the first control valve 01 and the second control valve 02 are respectively connected to a first control end C1 and a second control end C2 of the pilot-controlled directional valve 81, and are configured to select a conducting state of the pilot-controlled directional valve 81, so as to control one of the first oil port a and the second oil port B of the hydraulic motor 13 as an oil inlet and the other one as an oil outlet.

For example, in some embodiments, the pilot operated directional valve block may be an electrically proportional directional valve block with a load feedback function. For example, the pilot-controlled directional valve group further includes two relief valves 24, and the two relief valves 24 are respectively configured to be communicable with the second working end C and the third working end D of the pilot-controlled directional valve 81, for example, communication can be achieved in different directional states of the pilot-controlled directional valve 81, so as to limit the pressure fed back from the second working end C and the third working end D to the variable hydraulic pump 6. For example, the two relief valves 24 have feedback ports LS/a and LS/B, respectively, and the variable displacement hydraulic pump 6 has a feedback port LS, and the feedback ports LS/a and LS/B are both connected to the feedback port LS of the variable displacement hydraulic pump 6. Thereby, the variable displacement hydraulic pump 6 can adjust the output hydraulic pressure of the variable displacement hydraulic pump 6 according to the feedback pressure obtained by the feedback port LS.

For example, in some examples, a first shuttle valve 23 is disposed between the two relief valves 24, and the first shuttle valve 23 is configured to select a maximum pressure transmitted in the second working end C and the third working end D to be returned to the variable displacement hydraulic pump 6, so that the variable displacement hydraulic pump 6 can control the working pressure of the variable displacement hydraulic pump 6 based on the maximum pressure.

For example, as shown in fig. 3, in some embodiments, the valve body assembly may further include a first on-off valve 21 between the third working end D and the second port B of the pilot-controlled directional valve 81, and the first on-off valve 21 is configured to open when the mode switching valve 16 is switched to the first conduction state, and close when the mode is switched to the second conduction state, so as to control the switching of the oil supply circuit.

For example, in some examples, the first switching valve 21 comprises a first two-position two-way valve, a control end 3 of which is connected with the first working end 3 of the mode switching valve, such that the first two-position two-way valve is controlled by the mode switching valve 16.

For example, as shown in fig. 1, in some embodiments, the valve body assembly may further include an oil compensation anti-impact valve group 22 connecting the first port a and the second port B of the hydraulic motor 13, where the oil compensation anti-impact valve group 22 is configured to supply oil to one of the first port a and the second port B, so as to avoid undesirable phenomena such as suction and the like caused by the hydraulic motor 13 being dragged and rotated by an external force in case of a user's wrong operation, and also to effectively avoid transient hydraulic impact. For example, in the case of an erroneous operation by a user, the hydraulic motor 13 is dragged by an external force to rotate, and at this time, the oil supply anti-impact valve group 22 functions to supply oil and reduce pressure impact of the hydraulic motor 13, thereby protecting and extending the service life of the hydraulic motor 13.

For example, in some examples, the oil replenishment anti-impact valve set 22 includes a first check valve connected to the first port a and a first overflow valve connected to the first check valve, and further includes a second check valve connected to the second port B and a second overflow valve connected to the second check valve, and these valve bodies cooperate with each other such that the first port a is an oil inlet and the second port B is an oil outlet.

For example, the hydraulic motor 13 may be a self-mounted brake or an external brake. For example, as shown in fig. 3, in some embodiments, the cable tensioning system may further include a brake 12, the valve body assembly may further include a brake valve 11 and a second shuttle valve 9, the brake valve 11 is connected to the first control valve 01 and the second control valve 02 through the second shuttle valve 9, and is configured to control the brake 12 to lock the target actuator 14 when the first control valve 01 and the second control valve 02 are in the off state, and to control the brake 12 to unlock the target actuator 14 when the first control valve 01 and the second control valve 02 are in the on state. Thus, the second shuttle valve 9 automatically selects the higher pressure oil output from the first control valve 01 and the second control valve 02 of the handle valve group 10 to switch the direction of the brake valve 11, and further to release the brake 12. Thus, the brake 12 can be automatically released by operating the handle valve group 10. For example, in some examples, the brake valve 11 includes a two-position, three-way valve.

For example, as shown in fig. 3, in some embodiments, the valve body assembly may further include a second switching valve 17 between the pilot relief valve 20 and the pilot relief valve 19, and in the switching of the mode switching valve 16 to the second conduction state, the second switching valve 17 is opened so that the hydraulic motor 13 communicates with the pilot relief valve 20 and the pilot relief valve 19 to form an oil supply circuit; when the mode switching valve 16 is switched to the second conduction state, the second on-off valve 14 is closed, the pilot relief valve 20 and the pilot relief valve 19 are disconnected from each other, and the hydraulic motor 13 cannot form an oil supply circuit with the pilot relief valve 20 and the pilot relief valve 19.

For example, in some embodiments, a pressure gauge 18 is further provided between the pilot-controlled relief valve 19 and the second switching valve 17, and is used for detecting the set pressure of the pilot-controlled relief valve 19.

For example, in some examples, the second switch valve 17 comprises a second two-position two-way valve, a control end 3 of which is connected with the second working end 4 of the mode switching valve 17, such that the second two-position two-way valve is controlled by the mode switching valve 17. For example, the oil inlet port 1 of the mode switching valve 17 is connected to the constant displacement hydraulic pump 5 to obtain a switching driving force, and the oil outlet port 2 of the mode switching valve 17 is connected to the oil tank to return oil.

For example, in some embodiments, the valve body assembly may further include an oil compensation impact-proof overflow valve 26 and a third switch valve 25, a first working end T of the oil compensation impact-proof overflow valve 26 is connected to the hydraulic oil tank 1, a second working end P of the oil compensation impact-proof overflow valve 26 is connected to the first working end 1 of the third switch valve 25, and a second working end 2 of the third switch valve 25 is connected to one of the two overflow valves 24 of the hydraulic control reversing valve group, and configured such that in an open state of the third switch valve 25, the oil compensation impact-proof overflow valve 26 is communicated with the first port a through one of the two overflow valves 24, for example, the hydraulic control reversing valve 81, and in an open state of the third switch valve 25, the oil compensation impact-proof overflow valve 26 is disconnected from the first port a. From this, the oil supplementing anti-impact overflow valve 26 can realize the function of controlling the pressure of the second working end C of the hydraulic control directional valve 81, and then realize the function of adjusting the pressure of the first port a of the hydraulic motor 13, and the pressure can be adjusted to be low, so as to realize that the hydraulic motor 13 is dragged by the load to realize the passive rotating oil supplementing anti-suction function, and then realize the function of protecting the hydraulic motor 13.

For example, in some embodiments, the control terminal 4 of the third on/off valve 25 is connected to the mode switching valve 16, and is configured such that the third on/off valve 25 is opened when the mode switching valve 16 is switched to the second conducting state, and the third on/off valve 25 is closed when the mode switching valve 16 is switched to the first conducting state. For example, in some examples, the third on/off valve 25 comprises a two-position, three-way valve.

For example, as shown in fig. 1, in some embodiments, the hydraulic driving system may further include a first filter disposed between the hydraulic oil tank 1 and the fixed displacement hydraulic pump 5 and a second filter disposed between the hydraulic oil tank 1 and the variable displacement hydraulic pump 6 to filter impurities in the liquid to protect the fixed displacement hydraulic pump 5 and the variable displacement hydraulic pump 6, to prolong the service lives of the fixed displacement hydraulic pump 5 and the variable displacement hydraulic pump 6, and to prevent impurities in the liquid from entering into the connecting lines to cause defects such as clogging or inaccurate hydraulic supply.

For example, as shown in fig. 1, in some embodiments, the constant-displacement hydraulic pump 5 may be further connected with a relief valve 3 and a pressure gauge 4. For example, the overflow valve 3 may be a pilot overflow valve or a direct-acting overflow valve, the overflow valve 3 may set the working pressure of the constant displacement hydraulic pump 5, and the pressure gauge 4 is used to measure the working pressure of the constant displacement hydraulic pump 5.

For example, a port P of the variable hydraulic pump 6 is connected with a port P of the pilot operated directional valve group 8, and a second pressure gauge 7 is arranged in the middle for measuring the outlet pressure of the variable hydraulic pump 6 and further displaying the working state of the variable hydraulic pump 6.

In addition, it should be noted that the connection ports of all the above elements in the hydraulic drive system may be connected by using hydraulic hoses or metal pipes, and the connection lines between the elements are not particularly limited by the embodiments of the present disclosure.

In the following, a cable tensioning system in which a hydraulic drive system drives a cable tensioner will be described, taking the target drive device 14 as an example of a cable tensioner. It should be noted that, when the target drive device 14 is a winch or other device, the structure, the driving manner, and the like of the target drive device are substantially the same as those of the cable tensioning system, and therefore, reference may be made to the description of the cable tensioning system.

At least one embodiment of the present disclosure further provides a cable tensioning system, including the hydraulic control system and the cable tensioner provided by the embodiment of the present disclosure, the cable tensioner has a normal mode, and when the mode switching valve of the hydraulic control system is switched to the first conduction state, the cable tensioner is in the normal mode, and the cable tensioner can realize the cable winding and cable unwinding functions.

For example, the valve body assembly of the hydraulic control system further comprises a pilot overflow valve and a hydraulic control overflow valve for controlling the working pressure of the pilot overflow valve, and when the mode switching valve is switched to the second conduction state, the hydraulic motor is communicated with the pilot overflow valve and the hydraulic control overflow valve to form a second oil supply loop; at this time, the cable tensioner also has a load mode, and when the mode switching valve is switched to the second conduction state, the cable tensioner is in the load mode, and the cable tensioner can realize a passive cable laying function to simulate load weight.

For example, fig. 4 shows a schematic diagram of the wiring connections of the cable tensioning system.

As shown in fig. 4, the cable tensioning system comprises the above-mentioned hydraulic control system and the cable tensioner 14, the cable tensioner 14 has a normal mode in which the cable tensioner 14 can perform the cable retracting and cable releasing functions and a load mode in which the cable tensioner can perform the passive cable releasing function to simulate the load weight.

For example, the hydraulic control system includes a hydraulic motor 13, a hydraulic oil tank 1, and a fixed-displacement hydraulic pump 5 and a variable-displacement hydraulic pump 6 that communicate with the hydraulic oil tank 1. For example, the hydraulic pressure output by the quantitative hydraulic pump 5 is constant, and is used for providing pilot pressure oil for the valve body assembly to realize the reversing function of each valve in the valve body assembly; the output pressure of the variable hydraulic pump 6 is adjustable, so that different hydraulic pressures are provided, and different driving forces are provided. The hydraulic tank 1 may contain a liquid, for example hydraulic oil or another liquid that may transmit power.

For example, in some examples, the fixed displacement hydraulic pump 5 may comprise a gear pump or a vane pump, etc.; the variable hydraulic pump 6 may include a load-sensitive control plunger pump or a pressure-compensated control plunger pump, so as to implement a hydraulic feedback function, and further automatically adjust the hydraulic pressure provided by the variable hydraulic pump 6 according to the hydraulic feedback.

For example, the valve body assembly is composed of a plurality of valves including a plurality of connection ends respectively connected (directly or indirectly) to the fixed displacement hydraulic pump 5, the variable displacement hydraulic pump 6, and the cable tensioner 14 to control the flow direction of the fluid in the hydraulic oil tank 1, thereby controlling the operating state of the cable tensioner 14.

For example, the valve body assembly may include a pilot operated directional valve block 8 and a mode switching valve 16, the pilot operated directional valve block 8 including a pilot operated directional valve 81. The first working end W1 of the pilot-operated directional control valve 81 is connected to the variable displacement hydraulic pump 6. For example, in some examples, a pressure gauge 7 is further connected between the first working end W1 of the pilot operated directional control valve 81 and the variable displacement hydraulic pump 6 for detecting the working pressure of the variable displacement hydraulic pump 6 and further displaying the working state of the variable displacement hydraulic pump 6. The first working end of the mode switching valve 16 (i.e., the port 1 of the mode switching valve 16 shown in the drawing) is connected to the constant-displacement hydraulic pump 5, and is configured to control the operating state of the cable tensioner 14, and when the mode switching valve 16 is switched to place the cable tensioner 14 in the normal mode, the variable-displacement hydraulic pump 6, the pilot-operated directional valve 81, and the cable tensioner 14 are communicated to form an oil supply circuit, and at this time, the cable tensioner 14 can perform cable retracting and releasing functions.

For example, in some examples, the pilot operated directional valve 81 comprises a three-position, seven-way valve and the mode switching valve 16 comprises a two-position, four-way valve. For example, the mode switching valve 16 may be controlled manually or electrically.

For example, as shown in fig. 4, in some embodiments, the cable tensioner 14 comprises a tensioner reel, and the hydraulic motor 13 is configured to control the rotational direction and rotational speed of the tensioner reel, and thus the payout and retraction states and the payout and retraction speeds of the tensioner reel. For example, in some examples, there may be a speed reducer 15 between the cable tensioner 14 and the hydraulic motor 13, an output shaft of the hydraulic motor 13 is connected to an input end of the speed reducer 15 by a spline or a flat key, and an output end of the speed reducer 13 is connected to the cable tensioner 14, so that the hydraulic motor 13 may serve as a driving element of the speed reducer 15 and the cable tensioner 14 to drive the speed reducer 15 and the cable tensioner 14 to rotate and transmit torque.

For example, as shown in fig. 4, the hydraulic motor 13 has a first oil port a and a second oil port B, which are respectively connected to the second working end C and the third working end D of the pilot-controlled directional control valve 8, when the pilot-controlled directional control valve 8 is in different states, the direction of the oil supply loop formed between the variable displacement hydraulic pump 6, the pilot-controlled directional control valve 81 and the hydraulic motor 13 may be hydraulic oil tank 1-variable displacement hydraulic pump 6-pilot-controlled directional control valve 81-first oil port a of the hydraulic motor 13-second oil port B of the hydraulic motor 13-pilot-controlled directional control valve 81-hydraulic oil tank 1, or the oil supply loop may be hydraulic oil tank 1-variable displacement hydraulic pump 6-pilot-controlled directional control valve 81-second oil port B of the hydraulic motor 13-first oil port a of the hydraulic motor 13-hydraulic oil tank 81-hydraulic oil tank 1, one of the two oil supply loops can realize the cable laying function of the cable tensioner, and the other oil supply loop can realize the cable collecting function.

For example, as shown in fig. 4, in some embodiments, the valve body assembly may further include a selective handle valve group 10, the selective handle valve group 10 is connected to the fixed displacement hydraulic pump 5, and has a cable-releasing control valve (shown as cable, implemented as the first control valve 01) and a cable-retracting control valve (shown as cable, implemented as the second control valve 02) connected to the first control end C1 and the second control end C2 of the pilot-controlled directional valve 81, respectively, and configured to select a conducting state of the pilot-controlled directional valve 81, so as to control one of the first oil port a and the second oil port B of the hydraulic motor 13 as an oil inlet and the other one as an oil outlet.

For example, in some embodiments, the pilot operated directional valve block may be an electrically proportional directional valve block with a load feedback function. For example, the pilot-controlled directional valve group further includes two relief valves 24, and the two relief valves 24 are respectively configured to be communicable with the second working end C and the third working end D of the pilot-controlled directional valve 81, for example, communication can be achieved in different directional states of the pilot-controlled directional valve 81, so as to limit the pressure fed back from the second working end C and the third working end D to the variable hydraulic pump 6. For example, the two relief valves 24 have feedback ports LS/a and LS/B, respectively, and the variable displacement hydraulic pump 6 has a feedback port LS, and the feedback ports LS/a and LS/B are both connected to the feedback port LS of the variable displacement hydraulic pump 6. Thereby, the variable displacement hydraulic pump 6 can adjust the output hydraulic pressure of the variable displacement hydraulic pump 6 according to the feedback pressure obtained by the feedback port LS.

For example, in some examples, a first shuttle valve 23 is disposed between the two relief valves 24, and the first shuttle valve 23 is configured to select a maximum pressure transmitted in the second working end C and the third working end D to be returned to the variable displacement hydraulic pump 6, so that the variable displacement hydraulic pump 6 can control the working pressure of the variable displacement hydraulic pump 6 based on the maximum pressure.

For example, as shown in fig. 4, in some embodiments, the valve body assembly may further include a first on-off valve 21 between the third working end D and the second port B of the pilot-controlled directional valve 81, the first on-off valve 21 is configured to place the cable tensioner 14 in the normal mode and open the first on-off valve 21 when the mode switching valve is switched to the first conduction state, and to place the cable tensioner 14 in the load mode and close the first on-off valve 21 when the mode switching valve is switched to the second conduction state, so as to control the switching of the oil supply circuit.

For example, in some examples, the first switching valve 21 comprises a first two-position two-way valve, a control end 3 of which is connected with the first working end 3 of the mode switching valve, such that the first two-position two-way valve is controlled by the mode switching valve 16.

For example, as shown in fig. 4, in some embodiments, the valve body assembly may further include an oil compensation anti-impact valve group 22 connecting the first port a and the second port B of the hydraulic motor 13, where the oil compensation anti-impact valve group 22 is configured to supply oil to one of the first port a and the second port B, so as to avoid undesirable phenomena such as suction and the like caused by the hydraulic motor 13 being dragged and rotated by an external force in case of a user's wrong operation, and also to effectively avoid transient hydraulic impact. For example, in the case of an erroneous operation by a user, the hydraulic motor 13 is dragged by an external force to rotate, and at this time, the oil supply anti-impact valve group 22 functions to supply oil and reduce pressure impact of the hydraulic motor 13, thereby protecting and extending the service life of the hydraulic motor 13.

For example, in some examples, the oil replenishment anti-impact valve set 22 includes a first check valve connected to the first port a and a first overflow valve connected to the first check valve, and further includes a second check valve connected to the second port B and a second overflow valve connected to the second check valve, and these valve bodies cooperate with each other such that the first port a is an oil inlet and the second port B is an oil outlet.

For example, the hydraulic motor 13 may be a self-mounted brake or an external brake. For example, as shown in fig. 1, in some embodiments, the cable tensioning system may further include a brake 12, the valve body assembly may further include a brake valve 11 and a second shuttle valve 9, the brake valve 11 is connected to the cable pay-off control valve and the cable retraction control valve through the second shuttle valve 9, and is configured to control the brake 12 to lock the cable tensioner 14 when the cable pay-off control valve and the cable retraction control valve are in a disconnected state, and to control the brake 12 to unlock the cable tensioner 14 when the cable pay-off control valve or the cable retraction control valve is in an opened state. Thus, the second shuttle valve 9 will automatically select the higher pressure oil output from the cable releasing control valve and the cable retracting control valve of the handle valve set 10 to switch the direction of the brake valve 11, and further to release the brake 12. Thus, the brake 12 can be automatically released by operating the handle valve group 10. For example, in some examples, the brake valve 11 includes a two-position, three-way valve.

For example, as shown in fig. 4, in some embodiments, the valve body assembly may further include a pilot relief valve 20 and a pilot-controlled relief valve 19 that controls the operating pressure of the pilot relief valve 20, and when the mode switching valve 16 is switched to the second conduction state, the cable tensioner 14 is in the load mode, and the cable tensioner 14 communicates with the pilot relief valve 20 and the pilot-controlled relief valve 19 to form the oil supply circuit. Thus, in the load mode of the cable tensioner 14, the pilot operated spill valve 19 can control the magnitude of the dummy load by controlling the pilot spill valve 20 operating pressure, which is proportional to the pilot spill valve 20 operating pressure.

For example, in the load mode, the hydraulic motor 13 can be rotated by the cable tension applied to the cable tensioner 14, the magnitude of which is determined by the set pressure of the pilot-controlled relief valve 19.

For example, as shown in fig. 4, in some embodiments, the valve body assembly may further include a second switching valve 17 between the pilot spill valve 20 and the pilot spill valve 19, the cable tensioner 14 is in the load mode and the second switching valve 17 is opened in the second conduction state of the mode switching valve 16, so that the cable tensioner 14 communicates with the pilot spill valve 20 and the pilot spill valve 19 to form the oil supply circuit; when the mode switching valve 16 is switched to the first conduction state, the cable tensioner 14 is in the normal mode, the second on-off valve 14 is closed, the pilot relief valve 20 and the pilot relief valve 19 are disconnected from each other, the cable tensioner 14, the pilot relief valve 20 and the pilot relief valve 19 cannot form a fuel supply circuit, and thus the load mode cannot be realized.

For example, in some embodiments, a pressure gauge 18 is further provided between the pilot-controlled relief valve 19 and the second on-off valve 17, and is used for detecting the set pressure of the pilot-controlled relief valve 19 and further deducing the magnitude of the simulated load.

For example, in some examples, the second switch valve 17 comprises a second two-position two-way valve, a control end 3 of which is connected with the second working end 4 of the mode switching valve 17, such that the second two-position two-way valve is controlled by the mode switching valve 17. For example, the oil inlet port 1 of the mode switching valve 17 is connected to the constant displacement hydraulic pump 5 to obtain a switching driving force, and the oil outlet port 2 of the mode switching valve 17 is connected to the oil tank to return oil.

For example, in some embodiments, the valve body assembly may further include an oil compensation impact-proof overflow valve 26 and a third switch valve 25, a first working end T of the oil compensation impact-proof overflow valve 26 is connected to the hydraulic oil tank 1, a second working end P of the oil compensation impact-proof overflow valve 26 is connected to the first working end 1 of the third switch valve 25, and a second working end 2 of the third switch valve 25 is connected to one of the two overflow valves 24 of the hydraulic control reversing valve group, and configured such that in an open state of the third switch valve 25, the oil compensation impact-proof overflow valve 26 is communicated with the first port a through one of the two overflow valves 24, for example, the hydraulic control reversing valve 81, and in an open state of the third switch valve 25, the oil compensation impact-proof overflow valve 26 is disconnected from the first port a. From this, the oil supplementing anti-impact overflow valve 26 can realize the function of controlling the pressure of the second working end C of the hydraulic control directional valve 81, and then realize the function of adjusting the pressure of the first port a of the hydraulic motor 13, and the pressure can be adjusted to be low, so as to realize that the hydraulic motor 13 is dragged by the load to realize the passive rotating oil supplementing anti-suction function, and then realize the function of protecting the hydraulic motor 13.

For example, in some embodiments, the control end 4 of the third on/off valve 25 is connected to the mode switching valve 16 and configured to place the cable tensioner 14 in the load mode when the mode switching valve 16 is switched to the second conduction state, the third on/off valve 25 is open, and to place the cable tensioner 14 in the normal mode when the mode switching valve 16 is switched to the first conduction state, the third on/off valve 25 is closed, so that the oil replenishment anti-impact relief valve 26 is enabled when the cable tensioner 14 is placed in the load mode. For example, in some examples, the third on/off valve 25 comprises a two-position, three-way valve.

For example, as shown in fig. 4, in some embodiments, the cable tensioning system may further include a first filter disposed between the hydraulic oil tank 1 and the fixed displacement hydraulic pump 5 and a second filter disposed between the hydraulic oil tank 1 and the variable displacement hydraulic pump 6 to filter impurities in the liquid to protect the fixed displacement hydraulic pump 5 and the variable displacement hydraulic pump 6, to prolong the service life of the fixed displacement hydraulic pump 5 and the variable displacement hydraulic pump 6, and to prevent impurities in the liquid from entering into the connection lines to cause defects such as blockage or inaccurate hydraulic supply.

For example, as shown in fig. 4, in some embodiments, the constant-volume hydraulic pump 5 may be further connected with a relief valve 3 and a pressure gauge 4. For example, the overflow valve 3 may be a pilot overflow valve or a direct-acting overflow valve, the overflow valve 3 may set the working pressure of the constant displacement hydraulic pump 5, and the pressure gauge 4 is used to measure the working pressure of the constant displacement hydraulic pump 5.

For example, the port P of the variable hydraulic pump 6 is connected with the port P of the pilot operated directional control valve 8, and the middle part is provided with a second pressure gauge 7 for measuring the outlet pressure of the variable hydraulic pump 6 and further displaying the working state of the variable hydraulic pump 6.

In addition, it should be noted that the connection ports of all the above-mentioned elements in the cable tensioning system may be connected by using hydraulic hoses or metal pipes, and the connection lines between the elements are not particularly limited by the embodiments of the present disclosure.

The operation of the cable tensioning system provided by the disclosed embodiment to achieve the normal mode and the load mode of the cable tensioner 14 is described below by an exemplary operation.

For the normal mode, the mode switching valve 16 is first switched to the first conduction state, the cable tensioner 14 is in the normal mode, and at this time, the pilot pressure oil supplied from the fixed displacement hydraulic pump 5 flows to the control end of the second switching valve 17 (e.g., the two-position two-way valve) through the ports 1 to 4 of the mode switching valve 16 (i.e., the port 3 of the second switching valve 17 shown in the figure), and pushes the second switching valve 17 to switch to the disconnection state, and the inlet oil passage using the pilot operated relief valve 19 and the pressure gauge 18 is disconnected and does not function. At this time, the first switch valve 21 (e.g., a two-position two-way valve) is in a connected state, and the hydraulic motor 13 and the hydraulic control directional valve 81 form a complete fluid flow loop, and at this time, by pressing the cable releasing control valve or the cable retracting control valve of the selection handle valve group 10, the brake 12 is released, and the connection loop of the hydraulic control directional valve 81 is controlled, so that the rotation direction of the hydraulic motor 13 can be controlled, and the speed reducer 15 and the cable tensioner 14 are further driven to rotate. In the normal mode, the third switching valve 25 (e.g., a two-position three-way valve) is disconnected from the LS/a port of the hydraulic control directional valve set, and does not affect the working pressure of the hydraulic motor 13. Considering that in the normal mode, the hydraulic motor 13 is not allowed to be dragged and rotated by the cable in principle, because in this case, the hydraulic motor 13 will rotate passively and the problem of suction occurs, but the user may operate erroneously during operation, so the oil supplementing and impact preventing valve set 22 is added on the pipeline between the hydraulic motor 13 and the pilot-operated directional valve 81, and therefore, even if the user operates erroneously, the hydraulic motor 13 is dragged and rotated by external force, the oil supplementing and impact preventing valve set 22 will also play a role in supplementing oil and reducing the pressure impact of the hydraulic motor 13, and play a role in protecting and prolonging the service life of the hydraulic motor 13.

For the load mode, the mode switching valve 16 is first switched to the second conducting state, the cable tensioner 14 is in the load mode, at this time, the pilot pressure oil provided by the constant displacement hydraulic pump 5 drives the first switching valve 21 (e.g., two-position two-way valve) to the disconnected state through the ports 1 to 3 of the mode switching valve 16, at this time, the second port B of the hydraulic motor 13 can only be connected to the pilot relief valve 20, and the port R of the pilot relief valve 20 is connected to the pilot relief valve 19 and the pressure gauge 18 through the second switching valve 17 (e.g., two-position two-way valve), so that the pilot relief valve 19 can remotely adjust the working pressure of the pilot relief valve 20. In the load mode, the hydraulic motor 13 is dragged by the load cable to realize passive rotation, the second port B of the hydraulic motor 13 is used as an oil outlet of the motor, the pilot-controlled relief valve 19 is used for adjusting the actual set pressure of the pilot-controlled relief valve 20, which is also equivalent to the oil return back pressure of the hydraulic motor 13, and the back pressure also determines the magnitude of the simulated load which can be provided by the cable tensioner 14 in the load mode, and the magnitude of the simulated load is in linear proportion to the set pressure of the pilot-controlled relief valve 19. When the mode switching valve 16 is switched to the load mode, the state of the third switching valve 25 (e.g., a two-position three-way valve) is switched to a state that the oil compensation anti-impact relief valve 26 and the LS/a port of the hydraulic control directional valve set are in a communication state, the oil compensation anti-impact relief valve 26 realizes a function of controlling the pressure of the first control port C1 of the hydraulic control directional valve 81, and the pressure can be adjusted to be very low, so that the hydraulic motor 13 is dragged by a load to realize a passive rotation oil compensation anti-suction effect.

The following points need to be explained:

(1) the drawings of the embodiments of the disclosure only relate to the structures related to the embodiments of the disclosure, and other structures can refer to the common design.

(2) Without conflict, embodiments of the present disclosure and features of the embodiments may be combined with each other to arrive at new embodiments.

The above is only a specific embodiment of the present disclosure, but the scope of the present disclosure is not limited thereto, and the scope of the present disclosure should be determined by the scope of the claims.

Claims (18)

1. A hydraulic control system, comprising:

the hydraulic pump comprises a hydraulic motor, a hydraulic oil tank, a quantitative hydraulic pump and a variable hydraulic pump, wherein the quantitative hydraulic pump and the variable hydraulic pump are communicated with the hydraulic oil tank; and

the valve body assembly comprises a hydraulic control reversing valve group and a mode switching valve, and the hydraulic control reversing valve group comprises a hydraulic control reversing valve; the first working end of the hydraulic control reversing valve is connected with the variable hydraulic pump; the first working end of the mode switching valve is connected with the fixed displacement hydraulic pump, and the mode switching valve is configured to be in a first conduction state, so that the variable displacement hydraulic pump, the hydraulic control reversing valve and the hydraulic motor are communicated to form a first oil supply loop.

2. The hydraulic control system according to claim 1, wherein the valve body assembly further includes a pilot relief valve and a pilot-controlled relief valve that controls a working pressure of the pilot relief valve,

and when the mode switching valve is switched to a second conduction state, the hydraulic motor is communicated with the pilot overflow valve and the hydraulic control overflow valve to form a second oil supply loop.

3. The hydraulic control system of claim 2, wherein the hydraulic motor has a first oil port and a second oil port, the first oil port and the second oil port are connected with the second working end and the third working end of the pilot-controlled directional control valve, respectively,

the valve body assembly further comprises a selection handle valve group, the selection handle valve group is connected with the quantitative hydraulic pump and is provided with a first control valve and a second control valve, the first control valve and the second control valve are respectively connected with a first control end and a second control end of the hydraulic control reversing valve and are configured to select the conduction state of the hydraulic control reversing valve, and then one of the first oil port and the second oil port is controlled to be an oil inlet, and the other one of the first oil port and the second oil port is controlled to be an oil outlet.

4. The hydraulic control system of claim 3, wherein the pilot operated directional control valve block further comprises two relief valves configured to be respectively communicable with the second and third working ends of the pilot operated directional control valve to limit the pressure fed back to the variable displacement hydraulic pump by the second and third working ends.

5. The hydraulic control system of claim 4, wherein a first shuttle valve is disposed between the two spill valves and configured to select a maximum pressure delivered in the second and third work ports to return to the variable displacement hydraulic pump.

6. The hydraulic control system of any one of claims 3-5, wherein the valve body assembly further includes a first on-off valve between the third working end and the second port of the pilot-operated directional control valve, and configured to open when the mode switching valve is switched to the first conducting state and close when the mode switching valve is switched to the second conducting state.

7. The hydraulic control system of claim 6, wherein the mode switching valve comprises a two-position, four-way valve, and the first switching valve comprises a first two-position, two-way valve, a control end of the first two-way valve being connected to the first working end of the mode switching valve to be controlled by the mode switching valve.

8. The hydraulic control system of any one of claims 3-5, further comprising a brake, wherein,

the valve body assembly further includes a brake valve and a second shuttle valve, the brake valve being connected to the first control valve and the second control valve through the second shuttle valve, configured to control the brake lock target driving device when the first control valve and the second control valve are in a disconnected state, and to control the brake unlock target driving device when the first control valve or the second control valve is in an opened state.

9. The hydraulic control system of any of claims 3-5, wherein the valve body assembly further comprises an oil makeup shock valve set connecting the first and second ports, the oil makeup shock valve set configured to supply oil to one of the first and second ports.

10. The hydraulic control system of claim 9, wherein the oil replenishment anti-impact valve set comprises a first check valve connected to the first port and a first overflow valve connected to the first check valve, and further comprises a second check valve connected to the second port and a second overflow valve connected to the second check valve, and the second overflow valve is configured such that the first port is an oil inlet and the second port is an oil outlet.

11. The hydraulic control system according to claim 2, characterized in that the valve body assembly further includes a second on-off valve between the pilot spill valve and the pilot spill valve, the second on-off valve being open when the mode switching valve is switched to the second conducting state, and being closed when the mode switching valve is switched to the first conducting state.

12. The hydraulic control system of claim 11, wherein the mode switching valve includes a two-position, four-way valve, and the second switching valve includes a second two-position, two-way valve, a control end of the second two-position, two-way valve being connected to the second working end of the mode switching valve to be controlled by the mode switching valve.

13. The hydraulic control system according to claim 4, wherein the valve body assembly further includes an oil replenishment impact prevention overflow valve and a third switching valve, a first working end of the oil replenishment impact prevention overflow valve is connected to the hydraulic tank, a second working end of the oil replenishment impact prevention overflow valve is connected to a first working end of the third switching valve, and a second working end of the third switching valve is connected to one of the two overflow valves of the hydraulic control directional valve group, and is configured such that the oil replenishment impact prevention overflow valve is communicated with the first port through one of the two overflow valves when the third switching valve is in an open state, and the oil replenishment impact prevention overflow valve is disconnected from the first port when the third switching valve is in a disconnected state.

14. The hydraulic control system of claim 13, wherein a control end of the third switching valve is connected to the mode switching valve and configured to open the third switching valve when the mode switching valve is switched to the second conducting state and close the third switching valve when the mode switching valve is switched to the first conducting state.

15. The hydraulic control system according to any one of claims 1 to 5, further comprising a first filter provided between the hydraulic oil tank and the fixed-displacement hydraulic pump and a second filter provided between the hydraulic oil tank and the variable-displacement hydraulic pump.

16. The hydraulic control system of any one of claims 1-5, wherein the fixed displacement hydraulic pump comprises a gear pump or a vane pump; the variable displacement hydraulic pump comprises a load-sensitive control plunger pump or a pressure compensation control plunger pump.

17. A cable tensioning system, comprising:

the hydraulic control system of any one of claims 1-16, and

the cable tensioner is in a normal mode when the mode switching valve of the hydraulic control system is switched to a first conduction state, and can achieve cable retracting and releasing functions.

18. The cable tensioning system according to claim 17, wherein the valve body assembly of the hydraulic control system further comprises a pilot relief valve and a pilot-controlled relief valve that controls a working pressure of the pilot relief valve, and the hydraulic motor communicates with the pilot relief valve and the pilot-controlled relief valve to form a second oil supply circuit in the mode switching valve switched to the second conduction state;

the cable tensioner also has a load mode in which the cable tensioner is in the load mode when the mode switching valve is switched to the second conduction state, the cable tensioner being capable of performing a passive payout function to simulate a load weight.

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