CN107542719B - Normally open proportional one-way flow valve - Google Patents
Normally open proportional one-way flow valve Download PDFInfo
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- CN107542719B CN107542719B CN201710999602.6A CN201710999602A CN107542719B CN 107542719 B CN107542719 B CN 107542719B CN 201710999602 A CN201710999602 A CN 201710999602A CN 107542719 B CN107542719 B CN 107542719B
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Abstract
The invention provides a normally open proportional one-way flow valve, which comprises: the center of the proportional electromagnet is provided with an armature in a sliding manner; one end of the screw sleeve is connected in the proportional electromagnet; a first oil port and a second oil port are formed in one end, far away from the threaded sleeve, of the valve body connected to the other end of the threaded sleeve; the valve sleeve is connected in the valve body and is provided with communicated oil ports corresponding to the first oil port and the second oil port respectively; the main valve core is movably connected in the valve sleeve, and a damping channel communicated with the first oil port is arranged in the main valve core; the feedback valve core is arranged in the screw sleeve and connected with the proportional electromagnet, a feedback cavity is formed between the feedback valve core and the screw sleeve, and the feedback cavity is communicated with the second oil port; the proportional one-way flow valve is simple in structure, lower in cost and free of influence of load change during working.
Description
Technical Field
The invention relates to the technical field of valves, in particular to a normally open proportional one-way flow valve.
Background
In recent years, proportional one-way flow valves are increasingly applied to lifting equipment such as truck-mounted cranes, overhead working trucks, tractor rotary ploughs, electric forklifts and the like. When the equipment stops, the proportional one-way flow valve plays a role in pressure maintaining to prevent the hydraulic cylinder from sliding downwards; when the equipment needs to descend, the proportional one-way flow valve controls the size of the opening according to the size of the input voltage signal, adjusts the flow output by the hydraulic cylinder and further controls the descending speed of the lifting equipment. For example, patent publication No. CN 105298967 a entitled "a high horsepower tractor hoist valve group" provides a hydraulic valve group for controlling a tractor hoist, in which two proportional one-way flow valves are used to control the raising and lowering speed adjustments of the hoist, respectively. Although the proportional one-way flow valve in the existing market can proportionally control the opening degree of a valve port, the speed of equipment cannot be stably controlled on some equipment with large load pressure change, the equipment descending speed is high when the load is large and the equipment descending speed is slow when the load is small given the same control voltage signal. To solve this problem, a pressure compensator is typically added to achieve load independent proportional flow control, such as the one described in the above-mentioned patent, at the inlet of the proportional one-way flow valve controlling the cylinder lift. The additional addition of a pressure compensator entails an increase in the use costs and an increase in the volume of the hydraulic valve pack, which is unacceptable to many customers.
Disclosure of Invention
Aiming at part or all of the technical problems in the prior art, the invention provides a normally open proportional one-way flow valve which is simple in structure, lower in cost and free from the influence of load change during working.
In order to achieve the above object, the present invention provides a normally open proportional one-way flow valve having the following structure, including:
the center of the proportional electromagnet is provided with an armature in a sliding manner;
one end of the threaded sleeve is connected in the proportional electromagnet;
the valve body is connected to the other end of the threaded sleeve, and a first oil port and a second oil port are formed in one end, far away from the threaded sleeve, of the valve body;
the valve sleeve is connected in the valve body and is provided with communicated oil ports corresponding to the first oil port and the second oil port respectively;
the main valve core is movably connected in the valve sleeve, and a damping channel communicated with the first oil port is arranged in the main valve core;
the feedback valve core is arranged in the screw sleeve, a stepped through hole is formed in the feedback valve core, a feedback cavity is formed between the feedback valve core and the screw sleeve, and the feedback cavity is communicated with the second oil port;
the baffle ring is fixedly connected to the upper part of the valve sleeve, and an elastic part is arranged between the baffle ring and the feedback valve core;
the large end of the pilot valve core is pressed at the step of the inner hole of the feedback valve core by an elastic element, and the small end of the pilot valve core moves towards the direction far away from the damping channel of the main valve core under the action force of the elastic element;
the push rod is arranged between the feedback valve core and the armature in a sliding mode, the upper end of the push rod abuts against the lower end of the armature, the lower end of the push rod penetrates through a through hole in the upper portion of the feedback valve core and then abuts against the large end of the pilot valve core at the lower end of the feedback valve core, and the armature pushes the push rod to control the small end of the pilot valve core to move towards the direction of closing the damping channel of the main valve core by controlling the voltage of the proportional electromagnet.
In the invention, the pressure change caused by the load change of the second oil port is guided to the feedback cavity in a feedback mode, the influence caused by the load change is eliminated by the movement of the feedback valve core and the pressure change of the control cavity to reach a new balance state, and finally the flow is not changed when the load change is reached, so that the normally-open proportional one-way flow valve disclosed by the invention is not influenced by the load change when working. In addition, the normally open proportional one-way flow valve is improved on the basis of the prior art, has a relatively simpler structure, is not influenced by load change, does not need to be additionally provided with devices such as a pressure compensator and the like during working, and has lower cost.
In one embodiment, a positioning sleeve is arranged between the feedback valve core and the threaded sleeve, and the feedback cavity formed by the feedback valve core and the threaded sleeve is: the positioning sleeve is fixedly connected with the threaded sleeve, the feedback valve core is in a shape with a large middle part and two small sides, and the feedback valve core is in sliding fit with the positioning sleeve and is respectively provided with a first feedback cavity and a second feedback cavity at the upper end and the lower end of the middle part of the feedback valve core. The influence brought by load change is eliminated through the first feedback cavity, the second feedback cavity and the control cavity, so that the output flow is not changed.
In one embodiment, the positioning sleeve is provided with a first through hole and a second through hole corresponding to the first feedback cavity and the second feedback cavity respectively, the threaded sleeve is provided with a first communicating channel communicated with the first through hole and the second through hole, the first communicating channel is connected with a second communicating channel, and the second communicating channel is communicated with the second oil port. And pressure change caused by load change connected with the second oil port is fed back to the feedback valve core through the first channel and the second channel.
In one embodiment, the diameter of the first through hole is larger than that of the second through hole, and the annular area of the first feedback cavity is equal to that of the second feedback cavity; the first communicating channel is an oblique channel, and the second communicating channel is a channel parallel to the first damping channel. When the load is increased, because the diameter of the first through hole is larger than that of the second through hole, the pressure of the first feedback cavity is equal to that of the load, the pressure of the second feedback cavity is smaller than that of the load, the downward acting force on the feedback valve core is larger than the upward acting force, the feedback valve core drives the pilot valve core to move downwards, the pressure of the control cavity acting on the main valve core is increased, the force of the second oil port and the control cavity acting on the main valve core simultaneously is balanced, and the opening of the main valve core is reduced.
In one embodiment, the damping passage in the middle of the main valve core comprises a first damping hole and a first damping passage communicated with the first damping hole, and the first damping hole is communicated with the first oil port through the first damping passage; the diameter of the first communicating channel and the diameter of the second communicating channel are both larger than the diameter of the first orifice.
In one embodiment, one end of the main valve core close to the pilot valve core assembly is of a stepped frustum structure; the lower end of the main valve core is provided with an inclined plane which is matched with the valve sleeve to seal the first oil port. The bevel here acts as a seal for the valve sleeve when the main valve element is closed.
In one embodiment, the control chamber is a chamber formed by the lower end of the feedback valve core, the lower end of the pilot valve core, the upper end of the main valve core, the lower part of the positioning sleeve and the upper end of the valve sleeve; the upper end of the main valve core is of a step-shaped circular truncated cone structure. The upper end of the main valve core is of a stepped circular truncated cone structure, so that the area of the control cavity can be increased, and multi-stage proportional control is facilitated.
In one embodiment, the end of the feedback spool near the main spool is provided with a ramp that causes load changes to act directly on the pilot spool by changing the pressure in the feedback chamber and pressure chamber as the feedback spool moves up and down.
In one embodiment, when oil is fed from the second oil port and a certain voltage is applied to the proportional electromagnet, the attraction force generated by the proportional electromagnet drives the armature to overcome the acting force of the elastic piece to push the pilot valve core to move downwards, the distance between the pilot valve core and the first damping hole is reduced, the pressure of the control cavity is increased, the main valve core is pushed to move downwards under the action of pressure difference, and the opening of the main valve core is reduced; the voltage applied to the proportional solenoid is increased and the opening of the main spool continues to decrease until it closes.
Compared with the prior art, the normally open proportional one-way flow valve has the advantages that:
the normally open proportional one-way flow valve is provided with the first feedback cavity and the second feedback cavity respectively above and below the feedback valve core, when the load changes, the load changes and acts on the main valve core through the pressure change of the control cavity to change the opening of the main valve core due to the linkage of the first feedback cavity, the second feedback cavity and the control cavity, so that the output flow of the load changes and the descending speed of equipment is basically not influenced. In addition, because a pressure compensator is not required to be added, the complexity of the whole structure is reduced, the structure is simpler, and the cost can be reduced to a great extent.
Drawings
Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings, in which:
FIG. 1 shows one embodiment of a normally open proportional one-way flow valve of the present invention;
FIG. 2 shows an enlarged structure of section I of FIG. 1;
FIG. 3 shows the functional notation of the normally open proportional one-way flow valve of the present invention.
In the drawings, like parts are provided with like reference numerals. The figures are not drawn to scale.
Detailed Description
In order to make the technical solutions and advantages of the present invention more apparent, exemplary embodiments of the present invention are described in further detail below with reference to the accompanying drawings. It is clear that the described embodiments are only a part of the embodiments of the invention, and not an exhaustive list of all embodiments. And the embodiments and features of the embodiments may be combined with each other without conflict.
The inventor notices in the process of invention that although the proportional one-way flow valve adopted in the prior art can proportionally control the opening degree of a valve port, the speed of the equipment cannot be stably controlled on some equipment with large load pressure change, the equipment descending speed is high when the load is large and the equipment descending speed is slow when the load is small given the same control voltage signal, and a pressure compensator and the like are required to be added to increase the control in some use occasions, so that the cost is increased and the whole volume is increased.
In view of the above disadvantages, the embodiment of the present invention provides a normally open proportional one-way flow valve, which is described below.
Fig. 1 shows one implementation structure of the normally open proportional one-way flow valve of the invention. In the schematic diagram, the normally open proportional one-way flow valve of the invention mainly comprises: valve body 12, main valve core subassembly, proportion electro-magnet and pilot valve core subassembly. Wherein, the valve body 12 is provided with a first oil port a and a second oil port B. The main spool assembly is disposed within the valve body 12 to separate the first port A and the second port B. And the proportional electromagnet 2 is connected with the valve body 12 through a threaded sleeve 1 arranged in the proportional electromagnet, one end of the threaded sleeve 1 is connected with the proportional electromagnet 2, and the other end of the threaded sleeve 1 is fixedly connected with the valve body 12. And a pilot cavity is arranged in the threaded sleeve 1, and the pilot valve core assembly is arranged in the pilot cavity of the threaded sleeve 1. As shown in fig. 1, a control chamber 11 is formed between the pilot valve core assembly and the main valve core assembly, and the opening, closing and opening size of the oil from the second oil port B to the first oil port a can be realized by adjusting the voltage of the proportional electromagnet 2 through the pilot valve core assembly.
In one embodiment, main spool assembly generally includes a main spool 10 and a valve housing 5 disposed between main spool 10 and valve body 12. A first damping hole 15 and a first damping passage 16 are provided in the middle of main spool 10. The first orifice 15 communicates with the first port a through the first orifice passage 16.
In one embodiment, as shown in fig. 1, an end (an upper end in fig. 1) of the main spool 10 close to the pilot spool assembly is a stepped truncated cone structure, which can increase the area of the control chamber 11. In addition, the lower end of the main valve core 10 is provided with an inclined plane which is matched with the valve sleeve 5 and can block the first oil port a and the second oil port B. The inclined plane can play a good sealing role and prevent oil leakage.
In one embodiment, as shown in FIG. 1, the pilot valve spool assembly consists essentially of: a feedback spool 3, a pilot spool 4, and a resilient member 6. Wherein, the feedback valve core 3 is in a shape with a large middle part and small two ends. The pilot valve core 4 is arranged inside the feedback valve core 3, and the large end of the pilot valve core 4 is propped against the inner step of the feedback valve core. The elastic member 6 is provided inside the feedback spool 3, one end (upper end in fig. 1) of the elastic member 6 abuts inside the large end of the pilot spool 4, and the other end (lower end in fig. 1) of the elastic member 6 abuts on the upper end of the stopper ring 20. The small end of pilot valve element 4 moves away from first orifice 15 of main valve element 10 under the force of resilient element 6. By controlling the voltage of the proportional electromagnet 2, the armature 21 pushes the push rod 22 to control the small end of the pilot valve element 4 to move towards the direction of closing the first damping hole 15 of the main valve element 10.
In one embodiment, a positioning sleeve 7 is arranged between the feedback valve core 3 and the screw sleeve 1. The positioning sleeve 7 is in sliding fit with the feedback valve core 3, and a first feedback cavity 8 and a second feedback cavity 9 are formed on the upper end face and the lower end face of the middle of the armature respectively.
In one embodiment, the end of the feedback spool 3 near the main spool assembly is provided with a ramp that reduces the pressure in the second feedback chamber 9 as the feedback spool 3 moves toward the interior of the proportional solenoid 2 to accommodate load changes.
In one embodiment, the positioning sleeve 7 is provided with a first through hole 13 and a second through hole 14 corresponding to the first feedback cavity 8 and the second feedback cavity 9, respectively, the threaded sleeve 1 is provided with a first communication channel 17 communicated with the first through hole 13 and the second through hole 14, the first communication channel 17 is connected with a second communication channel 18, and the second communication channel 18 is communicated with the second oil port B.
In one embodiment, the diameter of the first through hole 13 is larger than the diameter of the second through hole 14, and the annular area of the first feedback chamber 8 is equal to the annular area of the second feedback chamber 9.
In one embodiment, the first communicating channel 17 is an oblique channel, the second communicating channel 18 is a channel parallel to the first damping channel 16, and the diameter of the first communicating channel 17 and the diameter of the second communicating channel 18 are both larger than the diameter of the first damping hole 15.
In the invention, as shown in fig. 1 and fig. 2, the pressure in the second feedback cavity 9 is adjusted through a hydraulic B-type half bridge formed by the throttling action of the second through hole 14 and the second feedback cavity 9 (formed by the vertical movement of the lower end inclined plane of the feedback valve core 3 relative to the positioning sleeve 7), and the pressure difference generated by the load change of the second oil port B is transmitted to the annular area of the feedback valve core 3 (wherein, the load pressure directly acts on the first feedback cavity 8, and the pressure output by the B-type half bridge acts in the second feedback cavity 9); the feedback valve core 3 is in a shape with a large middle and two small ends, and the annular area is formed by the large end and the small end.
Fig. 3 shows the functional symbol of the normally open proportional one-way flow valve of the present invention. According to fig. 3, when oil is input from the first oil port a, the proportional electromagnet is given a maximum voltage, the armature 20 pushes the push rod 22 to drive the pilot valve element 4 to overcome the acting force of the elastic element 6 to seal the first damping hole 15, which is equivalent to a one-way valve in function, and the acting force applied to the main valve element 10 overcomes the acting force of the elastic element 6 and the acting force of the control chamber 11 to push the main valve element 10 to move upward. However, as control chamber 11 is compressed, the pressure within control chamber 11 increases, gradually bringing main spool 10 to equilibrium.
If oil enters from the second oil port B and the proportional electromagnet 2 is not electrified, the pilot valve element 4 is far away from the first damping hole 15 on the main valve element 10 under the acting force of the elastic element 6, and the main valve element 10 is in an open state under the pressure of the port B and the pressure difference of the control cavity 11; when a certain voltage is given to the proportional electromagnet 2, the proportional electromagnet 2 generates a certain suction force, the armature 21 pushes the push rod 22 to overcome the force of the elastic piece 6 and generate a certain displacement downwards, the distance between the pilot valve element 4 and the first damping hole 15 is reduced, the pressure of the control cavity 11 rises at the moment, the pressure of the second oil port B and the pressure in the control cavity 11 have a pressure difference, the pressure difference acts on the main valve element 10 (the main valve element 10 is in a step shape, and an area difference is generated), the main valve element 10 is pushed to move downwards, and the opening of the main valve element is reduced. However, as soon as main valve element 10 moves downward, the distance from pilot valve element 4 increases, causing the pressure in control chamber 11 to drop, and main valve element 10 reaches a balanced state. If the voltage applied to proportional electromagnet 2 is increased, the displacement of armature 21 increases, pilot valve element 4 is also carried along to move downward, and the opening of main valve element 10 continues to decrease until it closes.
When a certain voltage is given to the proportional electromagnet 2, the main valve element 10 has an opening, if the load is increased at this time, the force acting on the annular area of the feedback cavity is increased, the force pushes the feedback valve element 3 to move downwards, so that the overflowing area of the variable throttle 19 (formed when the inclined plane at the lower end of the feedback valve element 3 moves up and down relative to the positioning sleeve 7, refer to fig. 2) is reduced, the pressure in the second feedback cavity 9 rises, the feedback valve element 3 finally reaches a balanced state, the main valve element 10 drives the pilot valve element 4 to move downwards because of the feedback valve element 3, the distance between the first damping hole 15 and the pilot valve element 4 is reduced, and the pressure of the control cavity 11 rises, so that the opening is reduced. If the load is reduced at this time, the force acting on the annular area of the feedback valve core 3 is reduced, the feedback valve core 3 moves upwards, the pressure of the second feedback chamber 9 is reduced due to the increase of the flow area of the variable throttle 19, so that the feedback valve core 3 reaches a new balance state, and at this time, the distance between the first damping hole 15 and the pilot valve core 4 is increased, the pressure of the control chamber 11 is reduced, and the opening of the main valve core 10 is increased.
The invention is characterized in that the variable throttling is changed by introducing the pressure difference feedback to act on the feedback valve core, so that the opening of the main valve core is reduced when the pressure difference is large; when the pressure difference is small, the opening is enlarged, and then the purpose that the flow is not changed when the load is changed is achieved.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, the appended claims are intended to be construed to include preferred embodiments and all such changes and/or modifications as fall within the scope of the invention, and all such changes and/or modifications as are made to the embodiments of the present invention are intended to be covered by the scope of the invention.
Claims (7)
1. A normally open proportional one-way flow valve, comprising:
the center of the proportional electromagnet is provided with an armature in a sliding manner;
one end of the threaded sleeve is connected in the proportional electromagnet;
the valve body is connected to the other end of the threaded sleeve, and a first oil port and a second oil port are formed in one end, far away from the threaded sleeve, of the valve body;
the valve sleeve is connected in the valve body and is provided with communicated oil ports corresponding to the first oil port and the second oil port respectively;
the main valve core is movably connected in the valve sleeve, and a damping channel communicated with the first oil port is arranged in the main valve core;
the feedback valve core is arranged in the screw sleeve, a stepped through hole is formed in the feedback valve core, a feedback cavity is formed between the feedback valve core and the screw sleeve, and the feedback cavity is communicated with the second oil port;
the baffle ring is fixedly connected to the upper part of the valve sleeve, and an elastic part is arranged between the baffle ring and the feedback valve core;
the pilot valve core is arranged in the control cavity, the large end of the pilot valve core is pressed at the step of the inner hole of the feedback valve core by an elastic element, and the small end of the pilot valve core moves towards the direction far away from the damping channel of the main valve core under the action force of the elastic element;
the push rod is arranged between the feedback valve core and the armature in a sliding mode, the upper end of the push rod abuts against the lower end of the armature, the lower end of the push rod penetrates through a through hole in the upper portion of the feedback valve core and then abuts against the large end of the pilot valve core at the lower end of the feedback valve core, and the armature pushes the push rod to control the small end of the pilot valve core to move towards the direction of closing the damping channel of the main valve core by controlling the voltage of the proportional electromagnet;
a positioning sleeve is arranged between the feedback valve core and the threaded sleeve, and a feedback cavity is formed between the feedback valve core and the threaded sleeve, namely: the positioning sleeve is fixedly connected with the threaded sleeve, the feedback valve core is large in the middle and small in two sides, the feedback valve core is matched with the positioning sleeve in a sliding mode, and a first feedback cavity and a second feedback cavity are formed in the upper end and the lower end of the middle of the feedback valve core respectively;
the locating sleeve corresponds first feedback chamber and second feedback chamber and is equipped with first through-hole and second through-hole respectively, be equipped with on the swivel nut with the first intercommunication passageway of first through-hole and second through-hole intercommunication, first intercommunication passageway is connected with second intercommunication passageway, second intercommunication passageway intercommunication the second hydraulic fluid port.
2. The proportional one-way flow valve of claim 1, wherein the damping passage in the middle of the main spool includes a first damping orifice and a first damping passage in communication with the first damping orifice, the first damping orifice being in communication with the first port via the first damping passage; the diameter of the first communicating channel and the diameter of the second communicating channel are both larger than the diameter of the first orifice.
3. The proportional one-way flow valve of claim 2, wherein the diameter of the first throughbore is greater than the diameter of the second throughbore, the annular area of the first feedback chamber is equal to the annular area of the second feedback chamber; the first communicating channel is an oblique channel, and the second communicating channel is a channel parallel to the first damping channel.
4. The proportional one-way flow valve of any of claims 1-3, wherein an end of the main spool proximate the pilot spool assembly is of stepped frustoconical configuration; the lower end of the main valve core is provided with an inclined plane which is matched with the valve sleeve to seal the first oil port.
5. The proportional one-way flow valve of any of claims 1-3, wherein the control chamber is a chamber formed by the lower end of the feedback spool, the lower end of the pilot spool, the upper end of the main spool, the lower portion of the positioning sleeve, and the upper end of the valve sleeve; the upper end of the main valve core is of a step-shaped circular truncated cone structure.
6. The proportional one-way flow valve of any of claims 1 to 3, wherein the end of the feedback spool near the main spool is provided with a ramp that causes load changes to act directly on the feedback spool by changing the pressure in the feedback and control chambers as the feedback spool moves up and down.
7. The proportional one-way flow valve according to any one of claims 1 to 3, wherein when oil is fed from the second oil port and a certain voltage is applied to the proportional electromagnet, the attraction force generated by the proportional electromagnet drives the armature to overcome the acting force of the elastic member and push the pilot valve core to move downwards through the push rod, the pressure of the control chamber rises, the main valve core is pushed to move downwards under the action of the pressure difference, and the opening of the main valve core is reduced; the voltage applied to the proportional solenoid is increased and the opening of the main spool continues to decrease until it closes.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710999602.6A CN107542719B (en) | 2017-10-24 | 2017-10-24 | Normally open proportional one-way flow valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710999602.6A CN107542719B (en) | 2017-10-24 | 2017-10-24 | Normally open proportional one-way flow valve |
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| CN107542719A CN107542719A (en) | 2018-01-05 |
| CN107542719B true CN107542719B (en) | 2019-12-20 |
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| CN201710999602.6A Active CN107542719B (en) | 2017-10-24 | 2017-10-24 | Normally open proportional one-way flow valve |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112901584B (en) * | 2021-03-10 | 2023-01-06 | 潍柴动力股份有限公司 | Electromagnetic proportional valve, flow valve and hydraulic system |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101560999A (en) * | 2009-05-14 | 2009-10-21 | 浙江大学 | Large-flow quick throttle proportional valve |
| CN103511377A (en) * | 2012-06-19 | 2014-01-15 | 上海立新液压有限公司 | One-way proportional flow valve |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005006321A1 (en) * | 2005-02-11 | 2006-08-17 | Hydac Fluidtechnik Gmbh | Valve, in particular proportional pressure relief valve |
| KR102083686B1 (en) * | 2013-12-26 | 2020-03-02 | 두산인프라코어 주식회사 | Pressure peak rerief valve for excavator and system of the same |
| CN107504006B (en) * | 2017-10-19 | 2019-07-09 | 杭州富阳中亚阀业有限公司 | A kind of normally opened ratio one-way flow valves |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101560999A (en) * | 2009-05-14 | 2009-10-21 | 浙江大学 | Large-flow quick throttle proportional valve |
| CN103511377A (en) * | 2012-06-19 | 2014-01-15 | 上海立新液压有限公司 | One-way proportional flow valve |
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Effective date of registration: 20191202 Address after: 224000 Anlong Village, Bufeng Town, Yancheng Economic and Technological Development Zone, Jiangsu Province Applicant after: Jiangsu salt state Pump Manufacturing Co., Ltd. Address before: 315000 Zhejiang province Ningbo city Ningbo high tech Zone Juxian Road No. 555 building 035 room 18-1 No. 013 station Applicant before: Ningbo Wen fan electrical and Mechanical Technology Development Co., Ltd. |
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