CN212429388U - Load-sensitive multi-way valve bank - Google Patents
Load-sensitive multi-way valve bank Download PDFInfo
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- CN212429388U CN212429388U CN202021530027.9U CN202021530027U CN212429388U CN 212429388 U CN212429388 U CN 212429388U CN 202021530027 U CN202021530027 U CN 202021530027U CN 212429388 U CN212429388 U CN 212429388U
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Abstract
A load-sensitive multi-way valve set comprises an oil inlet and return valve body, a reversing valve body and a pressure reducing valve body, wherein the oil inlet and return valve body is provided with an oil inlet P, an oil return port T, a pressure feedback port LS, a main safety valve, an LS overflow valve and a damping valve, and the pressure feedback port LS is respectively communicated with the oil return port T through the LS overflow valve and the damping valve; the reversing valve body is provided with two working oil ports, a main valve rod, a pressure compensation valve core and two secondary overflow valves are arranged in the reversing valve body, the main valve rod and the reversing valve body form a three-position five-way reversing valve, and the pressure compensation valve core and the reversing valve body form a three-position six-way hydraulic control valve; the A, B port is respectively and correspondingly communicated with the two working oil ports, and the C port is communicated with the other end of the pressure compensation valve core and the pressure feedback port LS; and a control oil port k of the secondary overflow valve is correspondingly communicated with the working oil ports respectively. The valve bank can accurately control output flow to be matched with the movement speed of the actuating mechanism, and redundant pressure oil higher than the main safety valve flows back to the oil tank, so that high efficiency and energy conservation are realized.
Description
Technical Field
The utility model relates to a hydrovalve field, in particular to sensitive multichannel valves of load.
Background
With the continuous development of hydraulic transmission technology, hydraulic components have been widely applied to various hosts and technical equipment, wherein engineering machinery is the largest demand market of the hydraulic components. The multi-way valve bank as a control element is a core component of a hydraulic system of the engineering machinery, and has an important influence on the comprehensive performance of a main engine.
In the years, engineering machinery develops towards the directions of environmental protection, conservation and the like, and a hydraulic system is a determining factor for realizing the requirements. The traditional throttling speed regulation type hydraulic system cannot meet the requirements of a host, so that the load sensitive hydraulic system is widely applied to the field of engineering machinery, and the system has the greatest advantages of high efficiency, energy conservation and improvement of host control performance. The load-sensitive valve group is a key component of the novel hydraulic system and belongs to the high-end manufacturing category.
At present, the front end valve used by the domestic engineering machinery basically depends on foreign manufacturers such as Leishile in Germany, Hawei, Danfoss in America and the like, has huge import substitution requirements, and simultaneously, the imported product still has a space for improvement from the technical level. Therefore, it is very important to develop a master control valve set of engineering machinery with better performance, whether to replace import or further promote the upgrading of host technology.
Currently, load-sensitive hydraulic valves produced by foreign manufacturers can be structurally classified into two categories: the first is a compensation load sensitive hydraulic valve before the valve, and the second is a compensation load sensitive hydraulic valve after the valve. The common characteristic of the two products is that the output flow of the hydraulic pump is controlled by load pressure feedback (LS signal) so as to achieve the best matching with the movement of the actuating mechanism. The difference is that the former has an LS overflow function, so that the system is more energy-saving, but has no flow sharing function, namely when the composite operation is carried out, if the output flow is insufficient, the actuator on one side with large load can not work; the latter can realize the flow sharing irrelevant to the system output, the actuating mechanism can move in proportion during the composite action, is irrelevant to the load, but does not have the LS overflow function, and the energy loss is overlarge when the mechanism is overloaded, so that the system is heated.
In view of the above, the development of a load-sensitive valve set with mutually compatible compensation functions before and after the valve must become an advanced point of industrial technology competition.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the technical problem that a sensitive multichannel valves of load is provided, this valves can control hydraulic system's output flow accurately, makes it and actuating mechanism movement speed phase-match, and no unnecessary pressure oil that is higher than main relief valve flows back the oil tank to reduce hydraulic system and overflow and rise, realize energy-efficient.
In order to achieve the above purpose, the utility model adopts the following technical scheme:
a load-sensitive multi-way valve set comprises an oil inlet and return valve body, a reversing valve body and a pressure reducing valve body, wherein the oil inlet and return valve body, the reversing valve body and the pressure reducing valve body are sequentially connected, the oil inlet P, an oil return port T and a pressure feedback port LS are arranged on the oil inlet and return valve body, a main safety valve, an LS overflow valve 2 and a damping valve are installed on the oil inlet and return valve body, the oil inlet P is communicated with the oil return port T through the main safety valve, and the pressure feedback port LS is respectively communicated with;
the reversing valve body is provided with two working oil ports, a main valve rod, a pressure compensation valve core and two secondary overflow valves are arranged in the reversing valve body, the main valve rod and the reversing valve body form a three-position five-way reversing valve, and the pressure compensation valve core and the reversing valve body form a three-position six-way hydraulic control valve;
an P, T port of the three-position five-way reversing valve is correspondingly communicated with the oil inlet P and the oil return port T respectively, a A, B port of the three-position five-way reversing valve is correspondingly communicated with a P, T port of the three-position six-way hydraulic control valve respectively, and a C port of the three-position five-way reversing valve is communicated with a P1 port of the three-position six-way hydraulic control valve, a control oil cavity at one end of a pressure compensation valve core and oil inlets i of two secondary overflow valves respectively; when the three-position five-way reversing valve is in the middle position, A, B, C ports of the three-position five-way reversing valve are communicated with the T port; when the three-position five-way reversing valve is positioned at two end positions, the port C is respectively communicated with the port A, B;
an A, B port of the three-position six-way hydraulic control valve is respectively and correspondingly communicated with the two working oil ports, and a C port is communicated with a reset oil cavity at the other end of the pressure compensation valve core and the pressure feedback port LS; the control oil ports k of the two secondary overflow valves are respectively and correspondingly communicated with the two working oil ports; when the pressure of one of the working oil ports is greater than the set pressure of the secondary overflow valve, the secondary overflow valve corresponding to the working oil port is opened, and the oil inlet i is communicated with the oil return port T through the secondary overflow valve.
Preferably, when the three-position six-way hydraulic control valve is in the initial lower position, each port is cut off; when the device is in an upper working position, the port P is communicated with the port A, the port B is communicated with the port T, and the port P1 is communicated with the port C; when the valve is in a working middle position, the port P is in throttling communication with the port A, the port B is in throttling communication with the port T, and the port P1 is cut off from the port C; when the speed control device is used for connecting more than two actuating mechanisms to perform composite action, the speed control independent of the load can be realized.
Preferably, valve covers are respectively arranged on two sides of the reversing valve body, and two ends of the main valve rod are respectively inserted into the valve covers; one of the valve covers is provided with a proportional electromagnetic valve which is composed of two oil inlet valves arranged in the right valve cover and an explosion-proof proportional electromagnet fixed on the right valve cover, oil inlet cavities of the two oil inlet valves are respectively communicated with an oil outlet of the pressure reducing valve, and oil outlets of the two oil inlet valves are respectively communicated with main valve rod cavities in the valve covers at two sides; the explosion-proof proportional electromagnet is provided with two electromagnetic valve cores which respectively correspond to the two oil inlet valves and are used for selectively controlling the conduction of the two oil inlet valves so as to control the reversing of the three-position five-way reversing valve.
Preferably, the reversing valve body is three pieces and is sequentially arranged between the oil inlet and return valve body and the pressure reducing valve body, and is used for respectively connecting and controlling the plurality of actuating mechanisms.
Preferably, the secondary overflow valve comprises a valve sleeve and a valve core which are in clearance fit through sliding, a sealing gland, an adjusting spring and an adjusting screw, the valve sleeve is inserted into the mounting hole in the top surface of the reversing valve body and limited through the sealing gland, the adjusting screw is mounted in a central hole of the sealing gland through threads, and the adjusting spring is clamped between the adjusting screw and the valve core so as to adjust the opening pressure of the secondary overflow valve.
Preferably, the valve sleeve is provided with a control oil port k and an oil inlet i which are arranged up and down along the radial direction, the middle part of the valve core corresponding to the control oil port k is provided with an annular groove, the diameter of the outer edge of the valve core above the annular groove is larger than that of the outer edge of the valve core below the annular groove, the sectional area of the annular shoulder at the upper end of the annular groove is larger than that of the annular shoulder at the lower end of the annular groove, and therefore when the pressure difference applied to the two ends of the annular groove on the valve core is larger than the pressure of the adjusting.
Preferably, an annular unloading oil cavity is arranged between the lower end of the valve sleeve and the mounting hole in the top surface of the reversing valve body, an oil drainage hole is radially arranged at the lower end of the valve sleeve, an oil return channel tangentially communicated with the unloading oil cavity is arranged on the reversing valve body, and when the valve core of the secondary overflow valve moves upwards to be opened, the oil inlet i is communicated with the oil return port T sequentially through the inner hole of the valve sleeve, the oil drainage hole, the unloading oil cavity and the oil return channel.
Preferably, the pressure reducing valve is a cartridge type pressure reducing valve and is installed in the pressure reducing valve body through threads, an oil inlet of the pressure reducing valve is communicated with the oil inlet P through an oil duct and a port P of a three-position five-way reversing valve arranged on the reversing valve body, and oil outlets of the pressure reducing valve are respectively communicated with oil inlet cavities of the oil inlet valves through oil ducts arranged on the pressure reducing valve body and the reversing valve body.
The utility model has the advantages that:
1. the valve bank and the variable plunger pump form a hydraulic system, a three-position six-way hydraulic control valve is formed by a pressure compensation valve core arranged in a reversing valve body and the reversing valve body, a port C of the three-position six-way hydraulic control valve is communicated with a reset oil cavity at the other end of the pressure compensation valve core and a pressure feedback port LS, so that the oil inlet pressure of an oil inlet P can be fed back to the variable plunger pump through the three-position five-way reversing valve and the three-position six-way hydraulic control valve through the pressure feedback port LS during working, the output flow of the hydraulic system can be accurately controlled, the output flow is matched with the movement speed of an executing mechanism, no redundant pressure oil flow higher than a main safety valve flows back to an oil tank.
2. Because two secondary overflow valves are arranged in the reversing valve body, the C port of the three-position five-way reversing valve is respectively communicated with the P1 port of the three-position six-way hydraulic control valve, the control oil cavity at one end of the pressure compensation valve core and the oil inlets i of the two secondary overflow valves, and the control oil ports k of the two secondary overflow valves are respectively correspondingly communicated with the two working oil ports; when the pressure of one of the working oil ports is greater than the set pressure of the secondary overflow valve, the secondary overflow valve corresponding to the working oil port is opened, and the oil inlet i is communicated with the oil return port T through the secondary overflow valve, so that the pressure of the pressure feedback port LS can be quickly adjusted through the secondary overflow valve, the flow of the oil inlet P and the working oil port is adjusted through the variable displacement plunger pump, the valve bank can achieve the optimal working state with high efficiency, energy conservation and accurate control, and the valve bank has the advantages of compact structure, reliable working and the like.
Drawings
Fig. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a bottom view of fig. 1.
Fig. 3 is a left side view of fig. 2.
Fig. 4 is a right side view of fig. 2.
Fig. 5 is a sectional view a-a of fig. 1.
Fig. 6 is a sectional view B-B of fig. 1.
Fig. 7 is a cross-sectional view C-C of fig. 1.
Fig. 8 is a partially enlarged view of fig. 6.
Fig. 9 is a hydraulic schematic diagram of the present invention.
In the figure: the hydraulic control valve comprises an oil inlet and return valve body 1, an LS overflow valve 2, a secondary overflow valve 3, a connecting bolt 4, a pressure reducing valve body 5, a proportional solenoid valve 6, a reversing valve body 7, a mounting hole 701, an oil return channel 702, a control oil cavity 703, a reset oil cavity 704, a main safety valve 8, a damping valve 9, a main valve rod 10, a left valve cover 11, a reset spring 12, a pressure compensation valve core 13, a right valve cover 14, a reset spring 15, a pressure reducing valve 16, a valve core 17, a valve sleeve 18, an oil drain hole 1801, a sealing gland 19, a nut 20, an adjusting screw 21, an adjusting spring 22, an oil drain oil cavity 23, a three-position five-way reversing valve 24.
Detailed Description
As shown in fig. 1-9, the utility model relates to a sensitive multichannel valves of load, include the oil return valve body 1 that advances that connects gradually through connecting bolt 4, switching-over valve body 7 establishes relief valve body 5 of relief pressure valve 16 in with, be equipped with oil inlet P on advancing return valve body 1 top surface, oil return port T, be equipped with pressure feedback mouth LS on advancing return valve body 1 outer terminal surface, draining port Y and pressure measurement mouth G, insert respectively and install main relief valve 8 through the screw thread in advancing return valve body 1, LS overflow valve 2 and damping valve 9, oil inlet P and pressure measurement mouth G intercommunication and through main relief valve 8 and establish oil duct and oil return port T intercommunication in advancing return valve body 1, pressure feedback mouth LS is respectively through establishing the oil duct in advancing return valve body 1, LS overflow valve 2 and damping valve 9 and oil return port T intercommunication.
The reversing valve bodies 7 are multiple pieces, are sequentially arranged and clamped between the oil inlet and return valve body 1 and the pressure reducing valve body 5, and are used for respectively connecting and controlling the multiple actuating mechanisms. In the embodiment, three pieces of the reversing valve body 7 are taken as an example.
Two working oil ports are respectively arranged on the top surface of each reversing valve body 7, the working oil ports of the three reversing valve bodies 7 are A1, B1, A2, B2, A3 and B3 in sequence, a main valve rod 10, a pressure compensation valve core 13 and two secondary overflow valves 3 are respectively inserted into each reversing valve body 7, the main valve rod 10 and the corresponding reversing valve body 7 respectively form a three-position five-way reversing valve 24, and the pressure compensation valve core 13 and the corresponding reversing valve body 7 respectively form a three-position six-way hydraulic control valve 25.
P, T ports of the three-position five-way reversing valve 24 on the three-piece reversing valve body 7 are communicated with each other and are correspondingly communicated with the oil inlet P and the oil return port T through oil ducts arranged in the oil inlet and return valve body 1 respectively, A, B ports of the three-position five-way reversing valve 24 are correspondingly communicated with P, T ports of the three-position six-way hydraulic control valve 25 respectively, and C ports are communicated with the P1 port of the three-position six-way hydraulic control valve 25, the control oil cavity 703 at one end of the pressure compensation valve core 13 and the oil inlets i of the two secondary overflow valves 3 through oil ducts arranged in the reversing valve body 7 and the pressure compensation valve core 13 respectively. When the three-position five-way reversing valve 24 is in the middle position, A, B, C ports of the three-position five-way reversing valve are communicated with the T port; when the three-position five-way reversing valve 24 is at two end positions, the C port is respectively communicated with the A, B ports.
The A, B ports of the three-position six-way hydraulic control valve 25 are respectively and correspondingly communicated with the two working oil ports on the corresponding reversing valve body 7, and the C port of the three-position six-way hydraulic control valve 25 is respectively and correspondingly communicated with the reset oil cavity 704 at the other end of the pressure compensation valve core 13 through an oil duct arranged in the pressure compensation valve core 13 and is communicated with the pressure feedback port LS through an oil duct. A return spring 12 is disposed in the return oil chamber 704 between the pressure compensation spool 13 and the corresponding left valve cover 11, and is used for returning the pressure compensation spool 13.
When the three-position six-way hydraulic control valve 25 is in the initial lower position, each port is stopped; when the device is in an upper working position, the port P is communicated with the port A, the port B is communicated with the port T, and the port P1 is communicated with the port C; when the valve is in a working middle position, the port P is in throttling communication with the port A, the port B is in throttling communication with the port T, and the port P1 is cut off from the port C; when the speed control device is used for connecting more than two actuating mechanisms to perform composite action, the speed control independent of the load can be realized.
The control oil ports k of the two secondary overflow valves 3 are respectively communicated with the two working oil ports on the corresponding reversing valve bodies 7 in a one-to-one correspondence manner through oil passages arranged in the reversing valve bodies 7; when the pressure of one of the working oil ports is greater than the set pressure of the secondary overflow valve 3, the secondary overflow valve 3 corresponding to the working oil port is opened, and the oil inlet i is communicated with the oil return port T through the secondary overflow valve 3.
The secondary overflow valve 3 comprises a valve sleeve 18, a valve core 17, a sealing gland 19, an adjusting spring 22 and an adjusting screw 21 which are in clearance fit through sliding, the valve sleeve 18 is inserted into a mounting hole 701 in the middle of the top surface of the reversing valve body 7 and limited by the sealing gland 19, the sealing gland 19 is inserted into the upper opening of the mounting hole 701 and fixed on the reversing valve body 7 through screws, the adjusting screw 21 is installed in a central hole of the sealing gland 19 through threads, a nut 20 is connected to the outer end of the adjusting screw 21 through threads, and the adjusting spring 22 is clamped between the adjusting screw 21 and the valve core 17 so as to adjust the opening pressure of the secondary overflow valve 3.
The valve sleeve 18 is provided with a control oil port k and an oil inlet i which are arranged up and down along the radial direction, the middle part of the valve core 17 corresponding to the control oil port k is provided with an annular groove, the diameter of the outer edge of the valve core 17 above the annular groove is larger than the diameter of the outer edge of the lower part of the annular groove, the sectional area of the annular shoulder at the upper end of the annular groove is larger than that of the annular shoulder at the lower end of the annular groove, and therefore when the pressure difference applied to the two ends of the annular groove on the valve core 17 is larger than the pressure of the adjusting.
An annular unloading oil cavity 23 is arranged between the lower end of the valve sleeve 18 and the lower end of the mounting hole 701 on the top surface of the reversing valve body 7, oil drain holes 1801 are uniformly distributed at the lower end of the valve sleeve 18 along the radial circumference, an oil return channel 702 communicated with the unloading oil cavity 23 in a tangent mode is arranged on the reversing valve body 7, and when a valve core 17 of the secondary overflow valve 3 moves upwards to be opened, an oil inlet i is communicated with an oil return port T sequentially through an inner hole of the valve sleeve 18, the oil drain holes 1801, the unloading oil cavity 23 and.
A left valve cover 11 and a right valve cover 14 are respectively connected to two sides of the reversing valve body 7 through screws, and two ends of the main valve rod 10 are respectively inserted into main valve rod cavities of the left valve cover and the right valve cover; a main valve stem cavity of the right valve housing 14 is provided with a return spring 15 sleeved on the main valve stem 10, and two ends of the return spring 15 are respectively sleeved on the main valve stem 10 through spring seats for realizing automatic return of the main valve stem 10 when no pressure pilot oil exists.
The proportional electromagnetic valve 6 is mounted on the right valve cover 14, the proportional electromagnetic valve 6 is composed of two oil inlet valves mounted in the right valve cover 14 and an explosion-proof proportional electromagnet fixed on the right valve cover 14, oil inlet cavities of the two oil inlet valves are respectively communicated with an oil outlet of the pressure reducing valve 16, and oil outlets of the two oil inlet valves are respectively communicated with main valve rod cavities in the left and right valve covers on two sides through oil passages arranged in the reversing valve body 7 and the left and right valve covers. The explosion-proof proportional electromagnet is provided with two electromagnetic valve cores which correspond to the valve cores of the two oil inlet valves respectively and are used for selectively controlling the conduction of the two oil inlet valves so as to control the reversing of the three-position five-way reversing valve 24.
The pressure reducing valve 16 is a plug-in type pressure reducing valve and is installed in the pressure reducing valve body 5 through threads, and an oil inlet f of the pressure reducing valve 16 is communicated with the oil inlet P through an oil passage and a P port of a three-position five-way reversing valve 24 arranged on the reversing valve body 7; the oil outlet c of the pressure reducing valve 16 leads out a pressure measuring port X at the outer end of the pressure reducing valve body 5, and is respectively communicated with the oil inlet cavity of each oil inlet valve through oil ducts g arranged in the pressure reducing valve body 5, the reversing valve body 7 and the right valve cover 14, and the pressure measuring port X is used for transmitting pressure oil decompressed by the pressure reducing valve to the two oil inlet valves. And oil drain ports of the proportional solenoid valve 6 and the pressure reducing valve 16 are communicated with an oil drain port Y through an oil duct arranged in the reversing valve body 7.
When the oil return valve is used, the oil inlet P and the pressure feedback port LS are respectively connected with the oil outlet and the feedback port of the variable plunger pump, the oil return port T and the oil drainage port Y are connected with the oil tank, and the working oil ports A1 and B1 on the reversing valve body 7 are connected with the actuating mechanism. The pressure can be manually adjusted according to the system requirement through the main safety valve 8, and the pipeline or equipment can be restrained from generating larger vibration through the damping valve 9, so that the amplitude is reduced, and the pipeline or equipment is protected. When the system stops working, the high pressure fed back by the pressure feedback port LS is required to be reduced to nearly no pressure, so that the displacement of the variable displacement piston pump can be reduced to the minimum. The high-pressure oil can be discharged back to the tank through the damping valve 9, so that the pressure at the pressure feedback port LS is gradually reduced.
When the valve group is in a standby state, the pressure of the pressure feedback port LS approaches zero, so that the displacement of the variable displacement plunger pump is in a minimum state, and the output flow approaches zero.
In operation, as shown in fig. 9, the position of the main valve stem 10 of the three-position five-way directional valve 24 is controlled by the proportional solenoid valve 6, thereby controlling the operation of the actuator. When the proportional solenoid valve 6 is not electrified, the main valve rod 10 is located at the middle position, the pressure feedback port LS has no pressure, the displacement of the variable displacement pump is close to zero, and the valve group does not work; when the main valve rod 10 is controlled to be reversed downwards by the proportional solenoid valve, pressure oil enters the control oil cavity 703 at one end of the pressure compensation valve core 13 through the three-position five-way reversing valve via the oil inlet P, the pressure compensation valve core 13 is pushed to be reversed to an upper position for conduction, and at the moment, the pressure oil outputs oil pressure via the working oil port B1 via the three-position six-way hydraulic control valve 25, so that the actuating mechanism works. Meanwhile, the pressure oil returns to the pressure feedback port LS through the three-position six-way pilot control valve 25, and finally the pressure signal is fed back to the variable displacement pump. When the actuating mechanism is overloaded, the pressure of the working oil port B1 is greater than the set pressure of the corresponding secondary overflow valve 3, the pressure oil entering the control oil port k acts on the valve core of the secondary overflow valve 3 to move the valve core of the secondary overflow valve 3 upwards to open, at this time, the pressure feedback port LS communicated with the oil inlet i of the secondary overflow valve is conducted and unloaded with the oil return port T through the secondary overflow valve, so that the pressure of the pressure feedback port LS is rapidly reduced, the variable displacement plunger pump automatically adjusts the output flow of the variable displacement plunger pump, the flow of the oil inlet P and the working oil port is reduced, and therefore, the load pressure of the working oil port can be adjusted by the set pressure of the secondary.
The above, only be the concrete implementation of the preferred embodiment of the present invention, but the protection scope of the present invention is not limited thereto, and any person skilled in the art is in the technical scope of the present invention, according to the technical solution of the present invention and the utility model, the concept of which is equivalent to replace or change, should be covered within the protection scope of the present invention.
Claims (8)
1. The utility model provides a sensitive multichannel valves of load, including the pressure reduction valve body of the oil valve body that advances that connects gradually, switching-over valve body and interior relief pressure valve body of establishing the relief pressure valve, characterized by: an oil inlet P, an oil return port T and a pressure feedback port LS are arranged on the oil inlet and return valve body, and a main safety valve, an LS overflow valve and a damping valve are installed on the oil inlet and return valve body;
the reversing valve body is provided with two working oil ports, a main valve rod, a pressure compensation valve core and two secondary overflow valves are arranged in the reversing valve body, the main valve rod and the reversing valve body form a three-position five-way reversing valve, and the pressure compensation valve core and the reversing valve body form a three-position six-way hydraulic control valve;
an P, T port of the three-position five-way reversing valve is correspondingly communicated with the oil inlet P and the oil return port T respectively, a A, B port of the three-position five-way reversing valve is correspondingly communicated with a P, T port of the three-position six-way hydraulic control valve respectively, and a C port of the three-position five-way reversing valve is communicated with a P1 port of the three-position six-way hydraulic control valve, a control oil cavity at one end of a pressure compensation valve core and oil inlets i of two secondary overflow valves respectively; when the three-position five-way reversing valve is in the middle position, A, B, C ports of the three-position five-way reversing valve are communicated with the T port; when the three-position five-way reversing valve is positioned at two end positions, the port C is respectively communicated with the port A, B;
an A, B port of the three-position six-way hydraulic control valve is respectively and correspondingly communicated with the two working oil ports, and a C port is communicated with a reset oil cavity at the other end of the pressure compensation valve core and the pressure feedback port LS; the control oil ports k of the two secondary overflow valves are respectively and correspondingly communicated with the two working oil ports; when the pressure of one of the working oil ports is greater than the set pressure of the secondary overflow valve, the secondary overflow valve corresponding to the working oil port is opened, and the oil inlet i is communicated with the oil return port T through the secondary overflow valve.
2. A load sensitive multi-way valve pack according to claim 1, wherein: when the three-position six-way hydraulic control valve is in the initial lower position, all the ports are cut off; when the device is in an upper working position, the port P is communicated with the port A, the port B is communicated with the port T, and the port P1 is communicated with the port C; when the valve is in a working middle position, the port P is in throttling communication with the port A, the port B is in throttling communication with the port T, and the port P1 is cut off from the port C; when the speed control device is used for connecting more than two actuating mechanisms to perform composite action, the speed control independent of the load can be realized.
3. A load sensitive multi-way valve pack according to claim 1, wherein: valve covers are respectively arranged on two sides of the reversing valve body, and two ends of the main valve rod are respectively inserted into the valve covers; one of the valve covers is provided with a proportional electromagnetic valve which is composed of two oil inlet valves arranged in the right valve cover and an explosion-proof proportional electromagnet fixed on the right valve cover, oil inlet cavities of the two oil inlet valves are respectively communicated with an oil outlet of the pressure reducing valve, and oil outlets of the two oil inlet valves are respectively communicated with main valve rod cavities in the valve covers at two sides; the explosion-proof proportional electromagnet is provided with two electromagnetic valve cores which respectively correspond to the two oil inlet valves and are used for selectively controlling the conduction of the two oil inlet valves so as to control the reversing of the three-position five-way reversing valve.
4. A load sensitive multi-way valve pack according to claim 3, wherein: the reversing valve body is three pieces and is sequentially arranged between the oil inlet and return valve body and the pressure reducing valve body and is used for respectively connecting and controlling the plurality of actuating mechanisms.
5. A load sensitive multi-way valve pack according to claim 1, wherein: the secondary overflow valve comprises a valve sleeve and a valve core which are in clearance fit through sliding, a sealing gland, an adjusting spring and an adjusting screw, the valve sleeve is inserted into a mounting hole in the top surface of the reversing valve body and limited through the sealing gland, the adjusting screw is mounted in a central hole of the sealing gland through threads, and the adjusting spring is clamped between the adjusting screw and the valve core so as to adjust the opening pressure of the secondary overflow valve.
6. The load sensitive multi-way valve block of claim 5, wherein: the valve sleeve is provided with a control oil port k and an oil inlet i which are arranged up and down along the radial direction, the middle part of the valve core corresponding to the control oil port k is provided with an annular groove, the diameter of the outer edge of the valve core above the annular groove is larger than the diameter of the outer edge of the valve core below the annular groove, the sectional area of the annular shoulder at the upper end of the annular groove is larger than that of the annular shoulder at the lower end of the annular groove, and therefore when the pressure difference applied to the two ends of the annular groove on the valve core is larger than the.
7. The load sensitive multi-way valve block of claim 6, wherein: an annular unloading oil cavity is arranged between the lower end of the valve sleeve and the mounting hole in the top surface of the reversing valve body, an oil drainage hole is arranged at the lower end of the valve sleeve along the radial direction, an oil return channel which is communicated with the unloading oil cavity in a tangent mode is arranged on the reversing valve body, and when a valve core of the secondary overflow valve moves upwards to be opened, the oil inlet i is communicated with the oil return port T sequentially through a valve sleeve inner hole, the oil drainage hole, the unloading oil cavity.
8. A load sensitive multi-way valve pack according to claim 3, wherein: the pressure reducing valve is a cartridge type pressure reducing valve and is installed in the pressure reducing valve body through threads, an oil inlet of the pressure reducing valve is communicated with an oil inlet P through an oil duct and a P port of a three-position five-way reversing valve arranged on the reversing valve body, and an oil outlet of the pressure reducing valve is respectively communicated with an oil inlet cavity of each oil inlet valve through oil ducts arranged on the pressure reducing valve body and the reversing valve body.
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| CN202021530027.9U CN212429388U (en) | 2020-07-29 | 2020-07-29 | Load-sensitive multi-way valve bank |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113669323A (en) * | 2021-10-22 | 2021-11-19 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN116181727A (en) * | 2023-02-23 | 2023-05-30 | 湖州生力液压有限公司 | Energy-saving type electric control multi-way valve with proportion |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113669323A (en) * | 2021-10-22 | 2021-11-19 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN113669323B (en) * | 2021-10-22 | 2022-02-18 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN116181727A (en) * | 2023-02-23 | 2023-05-30 | 湖州生力液压有限公司 | Energy-saving type electric control multi-way valve with proportion |
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