CN113550939A

CN113550939A - Hydraulic motor balance valve group with energy recovery and safety release functions

Info

Publication number: CN113550939A
Application number: CN202010330412.7A
Authority: CN
Inventors: 任建辉; 袁宏超; 陈忱; 李云辉; 占俊涛
Original assignee: China Railway Engineering Machinery Research and Design Institute Co Ltd
Current assignee: China Railway Engineering Machinery Research and Design Institute Co Ltd
Priority date: 2020-04-24
Filing date: 2020-04-24
Publication date: 2021-10-26

Abstract

The invention discloses a hydraulic motor balance valve group with energy recovery and safety release functions, wherein a balance valve, a hydraulic control reversing valve and a shuttle valve are arranged in the balance valve group, and an opening A and an opening B of the balance valve group are respectively communicated with an external oil supply path; the port A of the balance valve group is communicated with the port A1 of the hydraulic motor through a balance valve and a first oil way; the port B of the balance valve group is communicated with the port B1 of the hydraulic motor through a third stop valve and a second oil way; the balance valve group is also provided with a first electromagnetic reversing valve and an eighth stop valve, an a port of the first electromagnetic reversing valve is communicated with the first oil way, a b port of the first electromagnetic reversing valve is communicated with a b port of the eighth stop valve through a third oil way, an a port of the eighth stop valve is communicated with an XQ port of the balance valve group, and the XQ port of the balance valve group is connected with an external energy accumulator. The invention has the beneficial effects that: the problems that the release can not be safely carried out at a low tension value, the release potential energy can not be recycled and reused, and the motor is too low in release speed and is rapidly overheated are solved.

Description

Hydraulic motor balance valve group with energy recovery and safety release functions

Technical Field

The invention relates to a winch driving mechanism, in particular to a hydraulic motor balance valve bank with energy recovery and safety release functions.

Background

When the hoisting machinery is used for hoisting, the situation that the power of the whole hoisting machinery disappears frequently occurs, and the hoisted goods are suspended in the air. For safety, it is generally necessary to lower the sling. But for the very expensive hoisting weight, the lowering with a certain low set tension value is a safe necessity; if the heavy object stays outside the safe lowering range when the power disappears, the hoisting machinery needs to be hoisted and lifted, the amplitude of the arm support is adjusted, the rotation angle is adjusted, and an additional power source is needed for driving.

In order to make the weight safely lowered, a manual release function is usually adopted. The manual release is achieved by opening the hoist brake and communicating the hoist motor A, B. The conventional motor balance valve bank does not have the function of controlling the low tension value between the ports of the motor A, B, so that the low tension control between the ports of the motor A, B cannot be realized under the emergency working condition, and the operation of effectively and safely releasing the valuable load is not facilitated; when the whole machine loses power, the conventional motor balance valve group cannot collect weight lowering potential energy, and weight lowering in a safe area cannot be realized under the condition of full power loss. Therefore, there is an urgent need to develop a motor balancing valve assembly that can solve the above problems.

Disclosure of Invention

The invention aims to provide a hydraulic motor balance valve group with energy recovery and safe release functions aiming at the defects of the prior art, and solves the problems that the conventional motor balance valve group cannot automatically store energy when a heavy object is placed down in an emergency and cannot realize low-tension value communication between two cavities of a motor A, B in the emergency.

The novel technical scheme adopted by the invention is as follows: a hydraulic motor balance valve group with energy recovery and safety release functions is characterized in that a balance valve, a hydraulic control reversing valve and a shuttle valve are arranged in the balance valve group, and an A port of the balance valve group is communicated with an A1 port of a hydraulic motor through the balance valve and a first oil way; the port B of the balance valve group is communicated with the port B1 of the hydraulic motor through a third stop valve and a second oil way; the port A of the balance valve group is communicated with a second oil way through a shuttle valve; an x port of the balance valve is communicated with the second oil way; the port l0 of the balance valve is communicated with the port t of the hydraulic control reversing valve; the shuttle valve is communicated with a port p and a pilot control port x of the hydraulic control reversing valve, and a port a of the hydraulic control reversing valve is respectively communicated with an SC port and an SB port of the balance valve group; the balance valve group is also provided with a first electromagnetic reversing valve and an eighth stop valve, an a port of the first electromagnetic reversing valve is communicated with the first oil way, a b port of the first electromagnetic reversing valve is communicated with a b port of the eighth stop valve through a third oil way, an a port of the eighth stop valve is communicated with an XQ port of the balance valve group, and the XQ port of the balance valve group is connected with an external energy accumulator.

According to the scheme, a second electromagnetic directional valve and a first overflow valve are additionally arranged in the balance valve group, an a port of the second electromagnetic directional valve is communicated with the first oil way and an a port of the first electromagnetic directional valve, and a b port of the second electromagnetic directional valve is communicated with the second oil way through the first overflow valve; the first overflow valve is a low-pressure overflow valve.

According to the scheme, the balance valve group is additionally provided with an L port connected with an external oil way system, the port L0 of the balance valve and the port t of the hydraulic control reversing valve are respectively communicated with the port L of the balance valve group, and oil drainage of the port L0 and the port t of the hydraulic control reversing valve are drained to the external oil way system through the port L of the balance valve group.

According to the scheme, the third oil path is communicated with an HY port of the balance valve group through a third overflow valve and enters an external oil tank through the HY port; the third oil path is communicated with a GY port of the balance valve group through a sixth stop valve; the third oil path is communicated with a QJ port of the balance valve group through a seventh stop valve; the third overflow valve is a high-pressure overflow valve.

According to the scheme, the balance valve group is additionally provided with a first stop valve and a first throttling hole, the port a of the first stop valve is communicated with the first oil path, and the port b of the first stop valve is communicated with the second oil path through the first throttling hole.

According to the scheme, a second overflow valve and a check valve are additionally arranged in the balance valve group, a p port of the second overflow valve is communicated with the first oil way, a t port of the second overflow valve is communicated with the second oil way, and a t port of the second overflow valve is communicated with a BY port of the balance valve group through the check valve.

According to the scheme, the balance valve group is internally and additionally provided with the pressure sensor, and the detection end of the pressure sensor is positioned in the third oil way.

The invention has the beneficial effects that:

1. the motor balancing valve group solves the problems that the motor can not be safely released at a low tension value, the release potential energy can not be recycled and reused, and the release speed is too low and the motor is overheated quickly by designing the connection of a first electromagnetic reversing valve, a second electromagnetic reversing valve, an overflow valve, a stop valve and the like and related pipelines; meanwhile, the problems that oil is supplemented to a motor B port, the brake is started by external pressure oil, and the normal closing of a balance valve is possibly influenced due to the fact that the pressure value of the external oil supplementing or brake pressure oil is too high when the cavities of the motor A, B are communicated are solved, the normal use of the hoisting equipment and the reliability of safe release of heavy objects are improved, the safety coefficient is high, and the adaptability is strong.

2. The motor balance valve group has the advantages of higher integration degree, flexible control, convenient disassembly and inspection, higher safety degree, normal lowering of the hoisting weight, safe release of the hoisting weight, recovery of energy released by the hoisting weight, capability of serving as a power source to drive other mechanisms and the like, and fully guarantees the safe hoisting of hoisting machinery.

Drawings

Fig. 1 is a schematic structural diagram of an embodiment of the present invention.

Wherein: 1. a hydraulic motor; 2. a balancing valve; 3. filtering with a screen; 4. a one-way valve; 5. a shuttle valve; 6. a pressure reducing valve; 7. a hydraulic control directional control valve; 8. a pressure sensor; JZ1, first shut-off valve; JZ2, second stop valve; JZ3, third stop valve; JZ4, fourth stop valve; JZ5, fifth stop valve; JZ6, sixth stop valve; JZ7, seventh stop valve; JZ8, eighth stop valve; JL1, first throttle valve; JL2, pilot throttle; YL1, a first overflow valve; YL2, second overflow valve; YL3, third overflow valve; DC1, a first solenoid directional valve; DC2, second solenoid directional valve.

Detailed Description

For a better understanding of the present invention, reference is made to the following detailed description taken in conjunction with the accompanying drawings.

As shown in fig. 1, a balance valve group of a hydraulic motor with energy recovery and safety release functions is provided, wherein a balance valve 2, a hydraulic control reversing valve 7 and a shuttle valve 5 are arranged in the balance valve group, and an opening a of the balance valve group is communicated with an opening a1 of the hydraulic motor 1 through the balance valve 2 and a first oil path; the port B of the balance valve group is communicated with the port B1 of the hydraulic motor 1 through a third stop valve JZ3 and a second oil path; an opening A and an opening B of the balance valve group are respectively communicated with an external oil supply path to realize the in-and-out circulation of oil, and when the hydraulic motor 1 rotates forwards (winches), an opening A of the balance valve 2 door group is used for feeding oil, and an opening B is used for discharging oil; when the hydraulic motor 1 rotates reversely (lowers), the port B of the balance valve 2 valve group takes oil in and the port A takes oil out. The port A of the balance valve group is communicated with a second oil way through a shuttle valve 5; an x port of the balance valve 2 is communicated with a second oil way; the port l0 of the balance valve 2 is communicated with the port t of the pilot-controlled directional control valve 7; the shuttle valve 5 is communicated with a port p and a pilot control port x of the pilot control reversing valve 7, and a port a of the pilot control reversing valve 7 is respectively communicated with a port SC and a port SB of the balance valve group.

In the invention, the balance valve group is also provided with a first electromagnetic reversing valve DC1 and an eighth stop valve JZ8, an a port of the first electromagnetic reversing valve DC1 is communicated with a first oil way, a b port of the first electromagnetic reversing valve DC1 is communicated with a b port of the eighth stop valve JZ8 through a third oil way, an a port of the eighth stop valve JZ8 is communicated with an XQ port of the balance valve group, and the XQ port of the balance valve group is connected with an external energy accumulator.

Specifically, in the present embodiment, the port a of the balancing valve group communicates with the port a of the balancing valve 2, and the port b of the balancing valve 2 communicates with the port a1 of the hydraulic motor 1 through the first oil passage. The port B of the balancing valve group communicates with the port a of the third cut-off valve JZ3, and the port B of the third cut-off valve JZ3 communicates with the port B1 of the hydraulic motor 1 through the second oil passage. The x port of the balance valve 2 is communicated with the second oil path through a second throttle hole JL2 and a second stop valve JZ2, specifically: the x port of the balancing valve 2 communicates with the b port of the second orifice JL2, the a port of the second orifice JL2 communicates with the b port of the second stop valve JZ2 via the strainer 3, and the a port of the second stop valve JZ2 communicates with the b port of the third stop valve JZ3 via a second oil passage. The I0 mouth of balanced valve 2 communicates with the t mouth of pilot operated directional control valve 7, and the a mouth of pilot operated directional control valve 7 communicates through the SC mouth of fourth stop valve JZ4 with the balanced valves, and the SC mouth and the external power source intercommunication of balanced valves, the a mouth of pilot operated directional control valve 7 communicate through the SB mouth of fourth stop valve JZ4 and fifth stop valve JZ5 with the balanced valves, and the SB mouth and the hoist engine brake of balanced valves link to each other. An opening a of the shuttle valve 5 is communicated with an opening A of the balance valve group, an opening b of the shuttle valve 5 is communicated with the second oil path, and an opening c of the shuttle valve 5 is communicated with an opening p of the pilot-controlled reversing valve 7 and an opening x of the pilot control through a reducing valve 6 (the opening a of the reducing valve 6 is connected with the opening c of the shuttle valve 5, and the opening b of the reducing valve 6 is respectively communicated with the opening p of the pilot-controlled reversing valve 7 and the opening x of the pilot control).

Preferably, an L port connected with an external oil way system is additionally arranged on the balance valve group, an L0 port of the balance valve 2 and a t port of the hydraulic control reversing valve 7 are respectively communicated with the L port of the balance valve group, and oil drainage of the balance valve group and the T port of the hydraulic control reversing valve 7 are both drained to the external oil way system through the L port of the balance valve group.

Preferably, the third oil path is communicated with an HY port of the balance valve group through a third overflow valve YL3 and enters an external oil tank through the HY port; the third oil path is communicated with a GY port of the balance valve group through a sixth stop valve JZ 6; and the third oil path is communicated with a QJ port of the balance valve group through a seventh stop valve JZ 7. Preferably, the third relief valve YL3 is a high-pressure relief valve.

In the invention, a third oil path is communicated with a p port of a third overflow valve YL3, and a t port of a third overflow valve YL3 is communicated with an HY port of a balance valve group; the third oil path is communicated with a port a of a sixth stop valve JZ6, and a port b of the sixth stop valve JZ6 is communicated with a GY port of the balance valve group; the third oil passage communicates with a port a of the seventh cut-off valve JZ7, and a port b of the seventh cut-off valve JZ7 communicates with a port QJ of the balancing valve group.

Preferably, a second electromagnetic directional valve DC2 and a first overflow valve YL1 are additionally arranged in the balance valve group, a port a of the second electromagnetic directional valve DC2 is communicated with the first oil path and a port a of the first electromagnetic directional valve DC1, and a port b of the second electromagnetic directional valve DC2 is communicated with the second oil path through a first overflow valve YL 1; the first overflow valve YL1 is a low-pressure overflow valve. In this embodiment, a port b of the second electromagnetic directional valve DC2 is communicated with a port p of the first relief valve YL1, and a port t of the first relief valve YL1 is communicated with the second oil passage.

Preferably, a first shutoff valve JZ1 and a first orifice JL1 are further added in the balancing valve group, a port a of the first shutoff valve JZ1 communicates with the first oil passage, a port b of the first shutoff valve JZ1 communicates with the second oil passage through the first orifice JL1, specifically, a port b of the first shutoff valve JZ1 communicates with a port a of the first orifice JL1, and a port b of the first orifice JL1 communicates with the second oil passage.

Preferably, a second overflow valve YL2 and a check valve 4 are additionally arranged in the balance valve group, a p port of the second overflow valve YL2 is communicated with the first oil way, a t port of the second overflow valve YL2 is communicated with the second oil way, and a t port of the second overflow valve YL2 is communicated with a BY port of the balance valve group through the check valve 4.

Preferably, a pressure sensor 8 is additionally arranged in the balance valve group, and a detection end of the pressure sensor 8 is positioned in the third oil path. When the winch transfers heavy objects, the potential energy of the winch is converted into hydraulic energy to store the energy accumulator, if the winch transfers heavy objects for a long time, the energy accumulator is full, at the moment, a signal can be sent to the first electromagnetic directional valve DC1 through the pressure sensor 8 to be cut off, and oil can be released at high pressure through the second overflow valve YL 2; 2. if the winch is not used for a long time, because the balance valve group leaks, the pressure of the energy accumulator is reduced, and the pressure sensor 8 is used for monitoring, so that oil can be properly supplemented to the energy accumulator for short-distance lifting of emergency heavy objects.

In the invention, the balance valve 2 is a flow type balance valve 2; the stop valves JZ 1-JZ 8 are all throttle stop valves; second overflow valve YL2 and third overflow valve YL3 are high pressure overflow valve, and first overflow valve YL1 is the low pressure overflow valve.

As shown in fig. 1, in the present embodiment, the balancing valve set is respectively communicated with ports a1 and B1 of the hydraulic motor 1, and the ports GY of the balancing valve set are external oil supplementing ports for supplementing high-pressure oil from other external systems to enter the accumulator; the HY port is an overflow oil port after the accumulator reaches the highest pressure and is directly connected with an external oil tank of the hydraulic system; the QJ port is an oil liquid release port of the energy accumulator and is used for releasing oil liquid in the energy accumulator when the energy accumulator is damaged, replaced, cleaned and other non-working operations; the XQ port is a connecting oil port between the energy accumulator and the balance valve block, and the energy accumulator is communicated with the balance valve block through the connecting oil port; the L port is a total oil drainage port of the balance valve block and is connected with an external oil tank of the hydraulic system; other oil ports and related configurations of the balancing valve group are commonly used in the prior art, and are not described herein again. The pressure measuring point MA is additionally arranged on the A1 port communication pipeline of the hydraulic motor 1, the pressure measuring point MB is additionally arranged on the B1 port communication pipeline of the hydraulic motor 1, and other arrangements of the hydraulic motor 1 are the prior art. The present embodiment will be described in detail below.

The working principle of the embodiment is as follows:

1. safety release action

The oil liquid in the pressure cavity of the hydraulic motor 1 enters the balance valve group through the port A1, flows out from the port a of the second electromagnetic directional valve DC2 through the port B thereof, enters the p port of the first overflow valve YL1 and flows out from the port t thereof, flows out from the port B1 of the balance valve group and enters the oil suction cavity of the hydraulic motor 1, so that the high-speed stable operation of the hydraulic motor 1 under the low tension value is realized, and the release speed is improved conveniently.

The leakage oil generated by the operation of the hydraulic motor 1 flows out into the external oil tank through the port L1.

The forced oil supplementing oil enters the balance valve group through the BY port, flows in through the port a of the one-way valve 4, flows out through the port B of the one-way valve, and enters the oil suction cavity of the hydraulic motor 1 through the port B1, so that the oil supplementing is realized.

The variable control oil flows in from a port PA of a variable control cylinder of the hydraulic motor 1, enters one side of the variable control cylinder through a port ya, pushes the variable control cylinder to move the hydraulic motor 1 to the right to increase the displacement, flows out from a port yb of the other side of the variable control cylinder, flows out from a port PB of the variable control cylinder of the hydraulic motor 1, and returns to a variable balance valve bank (external) of the hydraulic motor 1.

During safe release, if release difficulty occurs (namely the hydraulic motor 1 does not run or runs slowly), the displacement setting of the hydraulic motor 1 is large, the pressure value of a pressure cavity of the hydraulic motor 1 can be increased by reducing the displacement of the hydraulic motor 1, and the pressure of pressure oil generated by the first overflow valve YL1 is increased, so that the running speed of the hydraulic motor 1 is improved; since the operation of the hydraulic motor 1 is blocked by the pressure of the first relief valve YL1, it can achieve smooth release of the heavy object in a certain speed range.

Second, energy recovery action during release

When the winch brake is released, the second stop valve JZ2, the third stop valve JZ3 and the fourth stop valve JZ4 are firstly closed, the fifth stop valve JZ5 is opened, pressure oil provided by an external power source (generally a manual pump) enters through an SB port of the balance valve group, flows through the fifth stop valve JZ5 and then flows out to the winch brake through an SC port of the balance valve group, and the winch brake is opened; the variable control oil flows to the yb port through the PB port of the variable control oil and enters the variable control cylinder to drive the displacement of the variable control cylinder to be reduced, and the oil on the other side of the variable control cylinder flows back to the oil tank through an external variable control valve after being discharged from the ya port and flowing to the PA port; when the pressure value displayed by the pressure measuring point MA meets the energy recovery pressure range, the first electromagnetic directional valve DC1 is electrified (or is manually controlled under the condition of power loss), oil enters a pressure cavity of the hydraulic motor 1 (a space enclosed by a port b of the balance valve 2 and the pressure measuring point MA detection position of the hydraulic motor 1) through a port a of the first electromagnetic directional valve DC1, flows out from a port b of the first electromagnetic directional valve DC1, flows to an XQ port of the balance valve group after passing through the eighth stop valve JZ8, and enters an (external) energy accumulator through the XQ port, so that energy storage and recovery are realized. After energy recovery is completed, oil discharged from a pressure cavity of the hydraulic motor 1 enters through a p port of an YL3 (overflow valve), is discharged through a t port of the hydraulic motor to flow to an HY port of the balance valve group, and enters an external oil tank after flowing out.

When the hydraulic motor 1 is operated, the oil discharged from the pressure chamber and the oil leaking through the port L1 (oil drain port) during operation need to be supplemented in the oil suction chamber (the space defined between the third cut-off valve JZ3 and the detection position of the pressure measuring point MB of the hydraulic motor 1). The external forced oil supplementing oil enters through a BY port of the balance valve group, flows to a port a of a DX (check valve 4), flows out to a port B1 of the balance valve group through a port B, flows into an oil suction cavity of the hydraulic motor 1 through a port B1, and completes oil supplementing.

When energy is recovered, the displacement of the hydraulic motor 1 can be adjusted in real time according to the pressure value of the pressure cavity of the hydraulic motor 1 measured by the MA port, the variable control oil of the hydraulic motor 1 flows to the yb port through the PB port and finally enters the variable control cylinder to drive the displacement to be reduced, and the oil on the other side of the variable control cylinder flows back to the oil tank through the external variable control valve after being discharged from the ya port and flowing to the PA port. When the hydraulic motor 1 runs, the pressure value of the pressure cavity of the hydraulic motor 1 is ensured to be higher than the set value of the third overflow valve YL3, so that the energy recovery and the lowering action are smooth.

Third, the action of the driving mechanism for recovering energy

The recovered energy stored in the energy accumulator (external) flows to a QJ port of the balance valve bank through the bottom gas stop valve after passing through the eighth stop valve JZ8, and flows out to a main balance valve bank (external) of other external mechanisms through the QJ port, and the other mechanisms (rotation, amplitude variation and the like) can change the rotation angle and the lifting weight amplitude of the whole machine, so that the spatial position movement of the lifting weight is realized, and the lifting weight can be placed in a safe range and can be lowered; the recovered energy stored in the (external) energy accumulator can also enter through the eighth stop valve JZ8 through the port DC1b of the first electromagnetic directional valve, flow out through the port a, and enter into the pressure chamber of the hydraulic motor 1 through the port a1, so as to push the hydraulic motor 1 to carry out forward winding operation.

In this embodiment, the oil return flow direction is as follows:

1. when the hoisting weight is lifted, oil enters through the port A of the balance valve group, enters the port A1 of the balance valve group through the balance valve 2 and flows to the pressure cavity of the hydraulic motor 1, after the hydraulic motor 1 operates, the oil flows out through the port B1 and enters the balance valve group, flows to the port B of the balance valve group through the third stop valve JZ3 and then flows out and enters the external main balance valve group;

2. during safety release, oil in a pressure cavity of the hydraulic motor 1 enters the balance valve group through an A1 port, enters through an a port of a second electromagnetic directional valve) DC2, flows out through a B port of the balance valve group, enters a p port of a first overflow valve YL1, flows out through a t port of the first overflow valve YL1, and enters an oil suction cavity of the hydraulic motor 1 after passing through a B1 port of the balance valve group;

3. when energy is recovered, oil in a pressure cavity of the hydraulic motor 1 enters the balance valve group through an A1 port, enters through an a port of a first electromagnetic directional valve DC1 and flows out through a b port of the first electromagnetic directional valve DC1, one part of the oil enters the external energy accumulator through an XQ port of the balance valve group after passing through an eighth stop valve JZ8, and the other part of the oil enters through a p port of an YL3 (overflow valve), flows out through a t port and flows out to the external oil tank through an HY port of the balance valve group;

4. when the winch mechanism is driven by recovered energy, oil enters from a port DC1B of the first electromagnetic directional valve after passing through an eighth stop valve JZ8, flows out from a port a, enters a pressure cavity of the hydraulic motor 1 from a port A1 of the balance valve group, pushes the hydraulic motor 1 to carry out forward winch operation, and oil discharged from the hydraulic motor 1 flows in from a port B1 of the balance valve group and flows out from a port B of the balance valve group after passing through a third stop valve JZ3 to enter an external main reversing valve group rear oil return tank.

In this embodiment, the oil drainage flow direction of the hydraulic system is as follows:

1. oil drainage of a hydraulic system exists no matter the working conditions of hoisting, lowering and releasing are met;

2. the oil drainage of the hydraulic motor 1 is discharged through an L1 port of the shell of the hydraulic motor 1;

3. the oil drainage of the external brake is discharged through an L port of the balance valve group;

4. all the discharged oil is collected by a pipeline outside the balance valve group and then enters an oil tank of an external main pump station.

According to the hydraulic brake control system, external oil enters the balance valve group through the port A of the balance valve group, on one hand, the port A is connected with the shuttle valve 5, the shuttle valve 5 is connected with the hydraulic control reversing valve 7, the hydraulic control reversing valve 7 is connected with the fourth stop valve JZ4, on the other hand, the fourth stop valve JZ4 is connected with the fifth stop valve JZ5, and the fifth stop valve JZ5 is connected with the SB port of the balance valve group, so that the hydraulic brake can be opened through emergency release; and the fourth stop valve JZ4 is connected with the balance valve group SC on the other hand, so that the hydraulic brake is normally opened. Oil enters the balance valve group through the port A of the balance valve group, and is connected with the balance valve 2 on the other hand, so that the dynamic braking of the hydraulic motor 1 from rotation to static is realized, and the static pressure bearing of the hydraulic motor 1 is completed. The balance valve 2 is communicated with a second overflow valve YL2, so that impact filtering and maximum pressure limiting are realized; the balance valve 2 is communicated with a second electromagnetic reversing valve DC2, and the second electromagnetic reversing valve DC2 is communicated with a first overflow valve YL1, so that impact filtering and maximum pressure limitation of the hydraulic motor 1 under low load are realized; the balance valve 2 is communicated with a first electromagnetic reversing valve DC1, the first electromagnetic reversing valve DC1 is communicated with a third overflow valve YL3, and the highest pressure limit during energy recovery is realized; the balance valve 2 is communicated with a first stop valve JZ1, the first stop valve JZ1 is communicated with a first throttling hole JL1, the ports A1 and B1 of the hydraulic motor 1 are communicated in a safe and adjustable speed mode in an emergency, the working condition of the hydraulic motor 1 on an adjustable speed free wheel is achieved, and manual release is achieved. The balance valve 2 communicates with the port a1 of the hydraulic motor 1, and realizes normal rotation (winding) of the hydraulic motor 1.

The external accumulator oil enters the balance valve group from the XQ port of the balance valve group, on one hand, the XQ port is connected with the eighth stop valve JZ8, and the eighth stop valve JZ8 is connected with the seventh stop valve JZ7, so that the accumulator oil is released; the eighth stop valve JZ8 is connected with a pressure sensor 8(PT) to realize pressure monitoring of the accumulator and the hydraulic motor 1A1 port; the eighth stop valve JZ8 is connected with a third overflow valve YL3, and the limitation of the highest pressure of the accumulator is realized; the eighth stop valve JZ8 is connected with the first electromagnetic directional valve DC1, so that the charging and the releasing of hydraulic oil between the external accumulator and the hydraulic motor 1 are realized; and the eighth stop valve JZ8 is connected with the sixth stop valve JZ6 to realize the accumulator charging.

Oil enters the balance valve group through a port B of the balance valve group, the port B is connected with a third stop valve JZ3, a third stop valve JZ3 is connected with a shuttle valve 5, the shuttle valve 5 is connected with a hydraulic control reversing valve 7, the hydraulic control reversing valve 7 is connected with a fourth stop valve JZ4, the fourth stop valve JZ4 is connected with a fifth stop valve JZ5 on one hand, and the fifth stop valve JZ5 is connected with a port SB of the balance valve group, so that the hydraulic brake can be opened through emergency release; and the fourth stop valve JZ4 is connected with the balance valve group SC on the other hand, so that the hydraulic brake is normally opened. The third stop valve JZ3 is connected with the second stop valve JZ2, the second stop valve JZ2 is connected with the pilot filter screen 3 of the balance valve 2, and the pilot filter screen 3 is connected with the second throttling hole JL2 of the balance valve 2, so that the balance valve 2 is opened stably; the third stop valve JZ3 is communicated with the first throttle hole JL1, the first throttle hole JL1 is communicated with the first stop valve JZ1, the ports A1 and B1 of the hydraulic motor 1 are communicated in an emergency, the speed-adjustable free wheel working condition of the hydraulic motor 1 is realized, and manual release is realized. The third cut-off valve JZ3 communicates with the B1 port of the hydraulic motor 1, and realizes reverse (downward) rotation operation of the hydraulic motor 1.

The external oil supplementing oil enters the balance valve group through a BY port of the balance valve group, the BY port is connected with the check valve 4, the check valve 4 is connected with a B1 port of the hydraulic motor 1, and oil supplementing of the hydraulic motor 1 during normal transfer parking and emergency transfer is achieved.

It should be noted that the above-mentioned embodiments are only preferred embodiments of the present invention, and the present invention is not limited thereto, and although the present invention has been described in detail with reference to the embodiments, it will be apparent to those skilled in the art that modifications can be made to the technical solutions described in the above-mentioned embodiments, or equivalent substitutions of some technical features, but any modifications, equivalents, improvements and the like within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A hydraulic motor balance valve group with energy recovery and safety release functions is characterized in that a balance valve (2), a hydraulic control reversing valve (7) and a shuttle valve (5) are arranged in the balance valve group, and an opening A and an opening B of the balance valve group are respectively communicated with an external oil supply path; the port A of the balance valve group is communicated with the port A1 of the hydraulic motor (1) through a balance valve (2) and a first oil way; the port B of the balance valve group is communicated with the port B1 of the hydraulic motor (1) through a third stop valve (JZ3) and a second oil path; the port A of the balance valve group is communicated with a second oil way through a shuttle valve (5); an x port of the balance valve (2) is communicated with the second oil way; the port l0 of the balance valve (2) is communicated with the port t of the hydraulic control reversing valve (7); the shuttle valve (5) is communicated with a p port and a pilot control x port of the hydraulic control reversing valve (7), and an a port of the hydraulic control reversing valve (7) is respectively communicated with an SC port and an SB port of the balance valve group; the balanced valve bank is further provided with a first electromagnetic directional valve (DC1) and an eighth stop valve (JZ8), an a port of the first electromagnetic directional valve (DC1) is communicated with a first oil way, a b port of the first electromagnetic directional valve (DC1) is communicated with a b port of the eighth stop valve (JZ8) through a third oil way, an a port of the eighth stop valve (JZ8) is communicated with an XQ port of the balanced valve bank, and the XQ port of the balanced valve bank is connected with an external energy accumulator.

2. The hydraulic motor balance valve group with the functions of energy recovery and safe release as claimed in claim 1, characterized in that a second electromagnetic directional valve (DC2) and a first overflow valve (YL1) are additionally arranged in the balance valve group, an a port of the second electromagnetic directional valve (DC2) is communicated with the first oil path and an a port of the first electromagnetic directional valve (DC1), and a b port of the second electromagnetic directional valve (DC2) is communicated with the second oil path through the first overflow valve (YL 1); the first overflow valve (YL1) is a low-pressure overflow valve.

3. The hydraulic motor balance valve group with the functions of energy recovery and safe release as claimed in claim 1, characterized in that the balance valve group is additionally provided with an L port connected with an external oil way system, the port L0 of the balance valve (2) and the port t of the hydraulic control reversing valve (7) are respectively communicated with the L port of the balance valve group, and oil drainage of the balance valve group and the port t are respectively drained to the external oil way system through the L port of the balance valve group.

4. The hydraulic motor balancing valve group with the functions of energy recovery and safe release as claimed in claim 1, characterized in that the third oil path is communicated with an HY port of the balancing valve group through a third overflow valve (YL3) and enters an external oil tank through the HY port; the third oil path is communicated with a GY port of the balance valve group through a sixth stop valve (JZ 6); the third oil path is communicated with a QJ port of the balance valve group through a seventh stop valve (JZ 7); the third overflow valve (YL3) is a high-pressure overflow valve.

5. The hydraulic motor balancing valve group with energy recovery and safety release functions as claimed in claim 1, characterized in that a first stop valve (JZ1) and a first orifice (JL1) are additionally arranged in the balancing valve group, wherein a port a of the first stop valve (JZ1) is communicated with the first oil passage, and a port b of the first stop valve (JZ1) is communicated with the second oil passage through the first orifice (JL 1).

6. The hydraulic motor balance valve group with the functions of energy recovery and safe release as claimed in claim 1, characterized in that a second overflow valve (YL2) and a check valve (4) are additionally arranged in the balance valve group, a p port of the second overflow valve (YL2) is communicated with the first oil path, a t port of the second overflow valve (YL2) is communicated with the second oil path, and a t port of the second overflow valve (YL2) is communicated with a BY port of the balance valve group through the check valve (4).

7. The hydraulic motor balancing valve group with the energy recovery and safety release functions as claimed in claim 1, wherein a pressure sensor (8) is additionally arranged in the balancing valve group, and a detection end of the pressure sensor (8) is located in the third oil path.