CN211174847U - Integral linkage vehicle-mounted crane double-pump bidirectional confluence multi-way valve - Google Patents
Integral linkage vehicle-mounted crane double-pump bidirectional confluence multi-way valve Download PDFInfo
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- CN211174847U CN211174847U CN201921857898.9U CN201921857898U CN211174847U CN 211174847 U CN211174847 U CN 211174847U CN 201921857898 U CN201921857898 U CN 201921857898U CN 211174847 U CN211174847 U CN 211174847U
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Abstract
An integral linkage truck-mounted crane double-pump two-way confluence multi-way valve comprises a valve body, wherein an oil inlet P1, a P2, an oil return port T and four groups of working ports A1, B1, A2, B2, A3, B3, A4 and B4 are arranged on the valve body, four valve rods are sequentially arranged in the valve body, and a first reversing valve, a second reversing valve, a third reversing valve, a fourth reversing valve and the valve body are formed; an P, P' port of the first reversing valve is respectively communicated with an oil inlet P2, and a A, B port of the first reversing valve is respectively communicated with the working ports A4 and B4 correspondingly; the port P2 'of the first reversing valve is communicated with the port P, P' of the second reversing valve, and the two ports P2 'of the first reversing valve are communicated with the port P2' of the first reversing valve through an oil passage and a one-way valve which are arranged in the valve body; when the first reversing valve and the second reversing valve are located at the middle positions, the oil inlet P2 is communicated with the oil inlet P1 through the first reversing valve and the second reversing valve and an oil passage arranged in the valve body. The valve can supply oil to the working ports of the winch motor and the telescopic oil cylinder in a confluence manner, so that the working efficiency is improved; the leakage point is few, compact structure, fine inching performance and high sensitivity.
Description
Technical Field
The utility model relates to a hydrovalve, in particular to integral linkage vehicle-mounted hangs two-way confluence multiple unit valve of double pump.
Background
At present, a hydraulic system for getting on a lorry-mounted crane generally adopts a single-pump system, and the system cannot meet the flow requirements of each actuating mechanism; the flow rate required by the hoisting and stretching actions is large, the flow rate required by the rotation and amplitude variation actions is small, and the flow rate surplus of a single pump system is large during the rotation action, so that impact can be formed, and the rotation action is unstable; the speed is lower during the hoisting action, and the efficiency is lower; and the simultaneous action of multiple actuating mechanisms cannot be realized, so that the working efficiency of the whole machine is not high.
Disclosure of Invention
The utility model aims to solve the technical problem of providing an integral linkage truck-mounted crane double-pump bidirectional confluence multi-way valve which can supply oil to a winch motor and a telescopic oil cylinder working port in a confluence manner, so as to improve the rotation speed of the winch motor and the speed of the telescopic oil cylinder; the leakage point is few, compact structure, fine inching performance and high sensitivity.
The technical scheme of the utility model as follows:
an integral linkage truck-mounted crane double-pump two-way confluence multi-way valve comprises a valve body, wherein an oil inlet P1, a P2, an oil return port T and four groups of working ports A1, B1, A2, B2, A3, B3, A4 and B4 are arranged on the valve body, a rotary valve rod, an amplitude-variable valve rod, a telescopic valve rod and a lifting valve rod are sequentially arranged in the valve body, the rotary valve rod and the valve body form a first reversing valve, the first reversing valve is a manual five-position eight-way valve, the amplitude-variable valve rod, the telescopic valve rod and the lifting valve rod respectively form second to fourth reversing valves with the valve body, and the second to fourth reversing valves are manual three-position six-way valves;
an P, P' port of the first reversing valve is respectively communicated with an oil inlet P2, and a A, B port of the first reversing valve is respectively communicated with the working ports A4 and B4 correspondingly; for controlling the rotary motor; the port P2 'of the first reversing valve is communicated with the port P, P' of the second reversing valve, and the two ports P2 'of the first reversing valve are communicated with the port P2' of the first reversing valve through an oil passage and a one-way valve which are arranged in the valve body;
when the first reversing valve and the second reversing valve are positioned at the middle positions, the oil inlet P2 is communicated with the oil inlet P1 through the first reversing valve and the second reversing valve and an oil passage arranged in the valve body; when the first reversing valve is at one end position, the port P 'is communicated with the port A, and the port B is communicated with one of the working ports P2'; when the first reversing valve is positioned at the other end position, the port P 'is communicated with the port B, and the port A is communicated with the other working port P2'; the oil return for realizing the working port A4 or B4 is converged and supplied with oil from an oil inlet P1 through a first reversing valve and a second reversing valve;
an A, B port of the second reversing valve is respectively and correspondingly communicated with a working port A3 and a working port B3 and is used for controlling the amplitude variation oil cylinder; an P, P' port of the third reversing valve is communicated with an O port of the fourth reversing valve, and a A, B port of the third reversing valve is correspondingly communicated with working ports A2 and B2 respectively and used for controlling the telescopic oil cylinder; an A, B port of the fourth reversing valve is correspondingly communicated with a working port A1 and a working port B1 respectively and is used for controlling a hoisting motor; and P, P' ports of the fourth reversing valve are respectively communicated with the oil inlet P1.
More preferably, when the first reversing valve is in a neutral position, the P port is communicated with the P2 ', the P ' port is closed, and the A, B port and the two P2 ' ports are communicated with the T port of the first reversing valve; when the first reversing valve is positioned at one side position adjacent to the middle position, the port P ' is communicated with the port A, the port B is communicated with the port T and one of the ports P2 ', and the port P is communicated with the port P2 ' through a throttling groove arranged on the rotary valve rod; the rotary motor is used for realizing the forward rotation and low-speed rotation of the rotary motor.
More preferably, when the first reversing valve is positioned at the other side position adjacent to the middle position, the port P ' is communicated with the port B, the port A is communicated with the port T and the other port P2 ', and the port P is communicated with the port P2 ' through a throttling groove arranged on the rotary valve rod; for effecting reverse low-speed rotation of the swing motor.
Preferably, a cartridge shuttle valve is further arranged in the valve body, two inlets of the shuttle valve are respectively communicated with the working ports A4 and B4, and an outlet of the shuttle valve is communicated with a control interface Z arranged on the valve body and used for connecting a rotary brake to control the rotating speed of the rotary motor.
More preferably, when the second reversing valve is in a neutral position, the port P is communicated with the port O, and the other ports are blocked; when the second reversing valve is at two end positions, the ports P', T and A, B are alternately communicated, and the other ports are cut off.
Preferably, when the third reversing valve is in a neutral position, the port P is communicated with the port T, and the other ports are blocked; when the third reversing valve is at two end positions, the ports P', T and A, B are alternately communicated, and the other ports are cut off.
More preferably, when the fourth reversing valve is in the neutral position, the port P is communicated with the port O, and the other ports are blocked; when the fourth reversing valve is at one end position, the port P' is communicated with the port A, the port B is communicated with the port O, and the other ports are closed; when the fourth reversing valve is at the other end position, the port P' is communicated with the port B, the port A is communicated with the port O, and the other ports are closed.
Preferably, a relief valve is further arranged in the valve body, and two ports of the relief valve are respectively communicated with the oil inlet P1 and the oil return port T through oil passages and are used for controlling the oil pressure after the oil inlets P1 and P2 are converged.
The utility model has the advantages that:
1. because the multi-way valve adopts a valve body, a rotary valve rod, an amplitude-variable valve rod, a telescopic valve rod and a lifting valve rod are sequentially arranged in the valve body, the four valve rods and the valve body form four reversing valves which are respectively communicated with four groups of working ports through oil ducts in the valve body and are respectively used for controlling the work of a rotary motor, an amplitude-variable oil cylinder, a telescopic oil cylinder and a winch motor, and an integral casting oil duct is adopted, the multi-way valve has the advantages of few leakage points, compact structure, good micromotion performance and high sensitivity; the pressure and power loss are small, and the system efficiency is high; the hydraulic elements are arranged in order, the operation is convenient, the centralized control is easy to realize, and the reliability of the host can be improved.
2. When the first reversing valve and the second reversing valve are in the neutral positions, the oil inlet P2 is communicated with the oil inlet P1 through the first reversing valve and the second reversing valve and an oil passage arranged in the valve body; when the first reversing valve is at one end position, the port P 'is communicated with the port A, and the port B is communicated with one of the working ports P2'; when the first reversing valve is positioned at the other end position, the port P 'is communicated with the port B, and the port A is communicated with the other working port P2'; the oil return for realizing the working port A4 or B4 is converged and supplied with oil from an oil inlet P1 through a first reversing valve and a second reversing valve; therefore, when the first reversing valve is positioned at the middle position and the two end positions, the oil supply of the oil inlet P2 and the oil inlet P1 can be realized in a converging manner, the rotating speed of the hoisting motor and the speed of the telescopic oil cylinder can be increased, and the working efficiency is improved.
Drawings
Fig. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a top view of fig. 1.
Fig. 3 is a sectional view a-a of fig. 1.
Fig. 4 is a sectional view B-B of fig. 1.
Fig. 5 is a cross-sectional view C-C of fig. 1.
Fig. 6 is a cross-sectional view E-E of fig. 1.
Fig. 7 is a sectional view F-F of fig. 1.
Fig. 8 is a sectional view taken along line G-G of fig. 1.
Fig. 9 is a cross-sectional view D-D of fig. 2.
Fig. 10 is a hydraulic schematic diagram of the present invention.
In the figure: the valve comprises a valve body 1, a first reversing valve 2, a second reversing valve 3, a third reversing valve 4, a fourth reversing valve 5, an overflow valve 6, a rotary valve rod 7, a variable amplitude valve rod 8, a telescopic valve rod 9 and a lifting valve rod 10. Oil inlets P1, P2, an oil return port T, working ports A1, B1, working ports A2, B2, working ports A3, B3, working ports A4, B4, a control interface Z and a test port G.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by a person of ordinary skill in the art without creative efforts belong to the protection scope of the present invention.
As shown in fig. 1-10, the utility model relates to an integral linkage vehicle-mounted crane double-pump two-way confluence multi-way valve, including a valve body 1, be equipped with oil inlet P1, P2 on valve body 1, oil return T and four groups of work ports A1, B1, A2, B2, A3, B3, A4 and B4, install gyration valve rod 7, change width of cloth valve rod 8, flexible valve rod 9 and play to rise valve rod 10 in proper order in valve body 1, gyration valve rod 7 forms first switching-over valve 2 with valve body 1, first switching-over valve 2 is manual five-position eight-way valve; the amplitude-variable valve rod 8, the telescopic valve rod 9 and the lifting valve rod 10 form second to fourth reversing valves with the valve body 1 respectively, and the second to fourth reversing valves are manual three-position six-way valves.
The P, P' port of the first reversing valve 2 is communicated with each other and is communicated with the oil inlet P2 through an oil passage arranged in the valve body 1, and the A, B port of the first reversing valve 2 is respectively communicated with the working ports A4 and B4 through two oil passages arranged in the valve body 1; for controlling the rotary motor. The port P2 'of the first change valve 2 is communicated with the port P, P' of the second change valve 3, and the two ports P2 'of the first change valve 2 are communicated with the port P2' thereof through an oil passage and a check valve arranged in the valve body 1.
When the first reversing valve 2 is in a neutral position, the P port is communicated with the P2 ', the P ' port is closed, and the A, B port and the two P2 ' ports are communicated with the T port of the first reversing valve 2; and the oil inlet for realizing the P port directly enters the second reversing valve 3 through the first reversing valve 2. When the first reversing valve 2 is reversed to a position on one side adjacent to the middle position, the port P ' is communicated with the port A, the port B is communicated with the adjacent port P2 ' and the port T, and the port P is communicated with the port P2 ' through a throttling groove arranged on the rotary valve rod; the rotary motor is used for realizing the forward rotation and low-speed rotation of the rotary motor.
When the first reversing valve 2 is reversed to the other side position adjacent to the middle position, the P ' port is communicated with the B port, the A port is communicated with one adjacent P2 ' port and the T port, and the P port is communicated with the P2 ' through a throttling groove arranged on the rotary valve rod; for effecting reverse low-speed rotation of the swing motor.
When the first reversing valve and the second reversing valve are located at the middle positions, the oil inlet P2 is communicated with the oil inlet P1 through the first reversing valve and the second reversing valve and an oil passage arranged in the valve body. When the first reversing valve 2 is positioned at one end, the port P 'is communicated with the port A, the port B is communicated with an adjacent working port P2', and the other ports are blocked; when the first reversing valve 2 is positioned at the other end position, the port P 'is communicated with the port B, the port A is communicated with one adjacent working port P2', and the other ports are blocked; the oil return of the working port A4 or B4 is realized through the first,
The second reversing valve is in confluence with the oil inlet P1 for oil supply.
The valve body is also internally provided with a cartridge shuttle valve, two inlets of the shuttle valve are respectively communicated with the working ports A4 and B4 through oil passages in the valve body, and an outlet of the shuttle valve is communicated with a control interface Z arranged on the valve body and is used for being connected with a rotary brake to control the rotating speed of a rotary motor.
An A, B port of the second reversing valve 3 is respectively and correspondingly communicated with a working port A3 and a working port B3 and is used for controlling a luffing cylinder; the P, P' ports of the second reversing valve 3 are communicated with each other, and the O port of the second reversing valve is communicated with the oil inlet P1 through an oil passage arranged in the valve body; the oil supply device is used for realizing confluence oil supply of the oil inlets P2 and P1. When the second reversing valve 3 is positioned at the middle position, the port P is communicated with the port O, and the other ports are cut off; when the second reversing valve 3 is at one end position, the port P' is communicated with the port A, the port B is communicated with the port T, and the other ports are closed; when the second reversing valve 3 is at the other end position, the port P' is communicated with the port B, the port A is communicated with the port T, and the other ports are closed.
And ports P, P 'of the third reversing valve 4 are communicated with each other and are communicated with a port O of the fourth reversing valve 5 through an oil passage P1', and ports A, B of the third reversing valve 4 are respectively communicated with working ports A2 and B2 correspondingly and are used for controlling the telescopic oil cylinder. When the third reversing valve 4 is positioned at the middle position, the port P is communicated with the port T, and the other ports are cut off; when the third reversing valve 4 is at one end position, the port P' is communicated with the port A, the port B is communicated with the port T, and the other ports are closed; when the third reversing valve 4 is at the other end position, the port P' is communicated with the port B, the port A is communicated with the port T, and the other ports are closed.
An A, B port of the fourth reversing valve 5 is correspondingly communicated with a working port A1 and a working port B1 respectively and is used for controlling a hoisting motor; the P, P' ports of the fourth reversing valve 5 are communicated with each other and the oil inlet P1.
When the fourth reversing valve 5 is positioned at the middle position, the port P is communicated with the port O, and the other ports are blocked, so that the oil fed from the oil inlet P1 enters the third reversing valve 4 through the fourth reversing valve 5 to control the telescopic oil cylinder; when the fourth reversing valve 5 is at one end position, the port P' is communicated with the port A, the port B is communicated with the port O, and the other ports are closed; when the fourth reversing valve 5 is at the other end position, the port P' is communicated with the port B, the port A is communicated with the port O, and the other ports are closed.
An inserted overflow valve 6 is further installed in the valve body, and two ports of the overflow valve 6 are respectively communicated with the oil inlet P1 and the oil return port T through oil ducts and are used for controlling the oil pressure after the oil inlets P1 and P2 are converged. The valve body is also provided with a test port G which is communicated with a port P of the fourth reversing valve 5 through an oil passage arranged in the valve body and is used for connecting a pressure gauge to test the oil pressure of the oil inlets P1 and P2 after confluence. The T-shaped ports of the first reversing valve to the fourth reversing valve are respectively communicated with the oil return port T through oil ducts arranged in the valve body, and all the oil ducts in the valve body are casting oil ducts.
When the oil pumping unit works, oil inlets P1 and P2 are respectively connected with a first oil pump and a second oil pump, four groups of working ports A1, B1, A2, B2, A3, B3, A4 and B4 are respectively connected with a winch motor, a telescopic oil cylinder, a variable amplitude oil cylinder and a rotary motor, and the first oil pump and the second oil pump are started.
When a load hung on the lifting hook needs to be lifted, the first reversing valve, the second reversing valve, the third reversing valve and the fourth reversing valve are manually controlled to be in the middle position, the lifting valve rod is pushed inwards, the fourth reversing valve 5 is in the lower end position, the combined oil of the oil inlets P1 and P2 passes through the fourth reversing valve 5 and is discharged from the working port A1 to enter the hoisting motor, the oil returning of the hoisting motor sequentially passes through the working port B1, the fourth reversing valve 5 and the third reversing valve 4 and returns to the oil tank from the oil return port T, the hoisting motor rotates forwards, and the lifting hook is lifted. Otherwise, the lifting valve rod is pushed outwards to enable the fourth reversing valve 5 to be located at the upper end position, the combined oil of the oil inlets P1 and P2 is discharged from the working port B1 through the fourth reversing valve 5 to enter the hoisting motor, the oil returned by the hoisting motor sequentially passes through the working port A1, the fourth reversing valve 5 and the third reversing valve 4 and returns to the oil tank through the oil return port T, and the lifting hook is lowered.
When the crane arm needs to stretch, the first reversing valve, the second reversing valve and the fourth reversing valve 5 are manually controlled to be in the middle position, the telescopic valve rod is pushed inwards, the third reversing valve 4 is enabled to be in the lower end position, the combined oil of the oil inlets P1 and P2 is discharged from the working port A2 through the fourth reversing valve 5 and the third reversing valve 4 and enters the telescopic oil cylinder, the oil returned by the telescopic oil cylinder returns to the oil tank through the working port B2 and the third reversing valve 4 through the oil return port T, the telescopic oil cylinder is stretched out, and the crane arm is stretched out. Conversely, the telescopic valve rod is pulled outwards, and the telescopic oil cylinder and the crane arm can be retracted.
When amplitude variation is needed, the first reversing valve, the third reversing valve and the fourth reversing valve are manually controlled to be positioned at a middle position, the amplitude variation valve rod is pushed inwards, the second reversing valve 3 is positioned at a lower end position, oil inlet of the oil inlet P2 is discharged from the working port A3 through the first reversing valve and the second reversing valve 3 in sequence and enters the amplitude variation oil cylinder, return oil of the amplitude variation oil cylinder returns to the oil tank through the working port B3 and the second reversing valve 3 from an oil return port T, the amplitude variation oil cylinder extends out, and the angle of the boom of the crane is increased; on the contrary, the amplitude variation valve rod is pulled outwards, so that the amplitude variation oil cylinder can be retracted, and the angle of the large arm of the crane is reduced.
When the rotary table needs to rotate forwards at a low speed, the rotary valve rod is pulled outwards by one position, so that the port P' of the first reversing valve is communicated with the port A, the port B is communicated with the port T, the oil inlet of the oil inlet P2 is discharged from the working port A4 through the first reversing valve and enters the rotary motor, and the return oil of the rotary motor returns to the oil tank through the working port B4 and the first reversing valve to push the rotary table to rotate forwards. Conversely, the rotary valve rod is pushed inwards to enable the port P' of the first reversing valve to be communicated with the port B, the port A is communicated with the port T, the oil inlet of the oil inlet P2 is discharged from the working port B4 through the first reversing valve to enter the rotary motor, and the return oil of the rotary motor returns to the oil tank through the working port A4 and the first reversing valve to push the rotary table to rotate reversely.
When the rotary table needs to rotate positively at a high speed, the rotary valve rod is pulled outwards at two positions, so that the first reversing valve is positioned at the lower end position, at the moment, the port P 'of the first reversing valve is communicated with the port A, the port B is communicated with the oil inlet P1 through the adjacent working port P2' and the second reversing valve 3, the oil inlet of the oil inlet P2 is discharged from the working port A4 through the first reversing valve and enters the rotary motor, the return oil of the rotary motor is converged with the oil inlet P1 through the working port B4, the first reversing valve and the second reversing valve 3, and the rotary table can be pushed to assist a lifting motor or a telescopic oil cylinder to act when rotating positively at a full speed. And vice versa.
While the embodiments of the invention have been described above, it is not intended to be limited to the details shown, or described, but rather to cover all modifications, which would come within the scope of the appended claims, and all changes which come within the meaning and range of equivalency of the art are therefore intended to be embraced therein.
Claims (8)
1. The utility model provides an integral linkage vehicle-mounted crane double-pump two-way confluence multiple-way valve, includes a valve body, characterized by: the valve body is provided with oil inlets P1, P2, an oil return port T and four groups of working ports A1, B1, A2, B2, A3, B3, A4 and B4, a rotary valve rod, an amplitude-changing valve rod, a telescopic valve rod and a lifting valve rod are sequentially arranged in the valve body, the rotary valve rod and the valve body form a first reversing valve, the first reversing valve is a manual five-position eight-way valve, the amplitude-changing valve rod, the telescopic valve rod and the lifting valve rod respectively form second to fourth reversing valves with the valve body, and the second to fourth reversing valves are manual three-position six-way valves;
an P, P' port of the first reversing valve is respectively communicated with an oil inlet P2, and a A, B port of the first reversing valve is respectively communicated with the working ports A4 and B4 correspondingly; for controlling the rotary motor; the port P2 'of the first reversing valve is communicated with the port P, P' of the second reversing valve, and the two ports P2 'of the first reversing valve are communicated with the port P2' of the first reversing valve through an oil passage and a one-way valve which are arranged in the valve body;
when the first reversing valve and the second reversing valve are positioned at the middle positions, the oil inlet P2 is communicated with the oil inlet P1 through the first reversing valve and the second reversing valve and an oil passage arranged in the valve body; when the first reversing valve is at one end position, the port P 'is communicated with the port A, and the port B is communicated with one of the working ports P2'; when the first reversing valve is positioned at the other end position, the port P 'is communicated with the port B, and the port A is communicated with the other working port P2'; the oil return for realizing the working port A4 or B4 is converged and supplied with oil from an oil inlet P1 through a first reversing valve and a second reversing valve;
an A, B port of the second reversing valve is respectively and correspondingly communicated with a working port A3 and a working port B3 and is used for controlling the amplitude variation oil cylinder; an P, P' port of the third reversing valve is communicated with an O port of the fourth reversing valve, and a A, B port of the third reversing valve is correspondingly communicated with working ports A2 and B2 respectively and used for controlling the telescopic oil cylinder; an A, B port of the fourth reversing valve is correspondingly communicated with a working port A1 and a working port B1 respectively and is used for controlling a hoisting motor; and P, P' ports of the fourth reversing valve are respectively communicated with the oil inlet P1.
2. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 1, which is characterized in that: when the first reversing valve is in a neutral position, the P port is communicated with the P2 ', the P ' port is closed, and the A, B port and the two P2 ' ports are communicated with the T port of the first reversing valve; when the first reversing valve is positioned at one side position adjacent to the middle position, the port P ' is communicated with the port A, the port B is communicated with the port T and one of the ports P2 ', and the port P is communicated with the port P2 ' through a throttling groove arranged on the rotary valve rod; the rotary motor is used for realizing the forward rotation and low-speed rotation of the rotary motor.
3. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 2, which is characterized in that: when the first reversing valve is positioned at the other side position adjacent to the middle position, the port P ' is communicated with the port B, the port A is communicated with the port T and the other port P2 ', and the port P is communicated with the port P2 ' through a throttling groove arranged on the rotary valve rod; for effecting reverse low-speed rotation of the swing motor.
4. The integrated linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in any one of claims 1 to 3, which is characterized in that: the valve body is also internally provided with a plug-in type shuttle valve, two inlets of the shuttle valve are respectively communicated with the working ports A4 and B4, and an outlet of the shuttle valve is communicated with a control interface Z arranged on the valve body and used for being connected with a rotary brake to control the rotating speed of the rotary motor.
5. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 4, which is characterized in that: when the second reversing valve is positioned at the middle position, the port P is communicated with the port O, and the other ports are cut off; when the second reversing valve is at two end positions, the ports P', T and A, B are alternately communicated, and the other ports are cut off.
6. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 4, which is characterized in that: when the third reversing valve is positioned at the middle position, the port P is communicated with the port T, and the other ports are cut off; when the third reversing valve is at two end positions, the ports P', T and A, B are alternately communicated, and the other ports are cut off.
7. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 6, which is characterized in that: when the fourth reversing valve is positioned at the middle position, the port P is communicated with the port O, and the other ports are cut off; when the fourth reversing valve is at one end position, the port P' is communicated with the port A, the port B is communicated with the port O, and the other ports are closed; when the fourth reversing valve is at the other end position, the port P' is communicated with the port B, the port A is communicated with the port O, and the other ports are closed.
8. The integral type linkage truck-mounted crane double-pump bidirectional confluence multi-way valve as claimed in claim 1 or 7, which is characterized in that: an overflow valve is further arranged in the valve body, and two ports of the overflow valve are respectively communicated with the oil inlet P1 and the oil return port T through oil passages and are used for controlling the oil pressure after the oil inlets P1 and P2 are converged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921857898.9U CN211174847U (en) | 2019-10-31 | 2019-10-31 | Integral linkage vehicle-mounted crane double-pump bidirectional confluence multi-way valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921857898.9U CN211174847U (en) | 2019-10-31 | 2019-10-31 | Integral linkage vehicle-mounted crane double-pump bidirectional confluence multi-way valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211174847U true CN211174847U (en) | 2020-08-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921857898.9U Active CN211174847U (en) | 2019-10-31 | 2019-10-31 | Integral linkage vehicle-mounted crane double-pump bidirectional confluence multi-way valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211174847U (en) |
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2019
- 2019-10-31 CN CN201921857898.9U patent/CN211174847U/en active Active
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