CN210710470U - Flow control type variable amplitude balance valve - Google Patents
Flow control type variable amplitude balance valve Download PDFInfo
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- CN210710470U CN210710470U CN201921395788.5U CN201921395788U CN210710470U CN 210710470 U CN210710470 U CN 210710470U CN 201921395788 U CN201921395788 U CN 201921395788U CN 210710470 U CN210710470 U CN 210710470U
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Abstract
The utility model provides a flow control type becomes width of cloth balanced valve relates to hoisting machinery, engineering machine tool, agricultural machine hydraulic control technical field. Flow control type becomes width of cloth balanced valve includes: the valve body is internally provided with a valve cavity with two through ends; controlling a cylinder body and an end cover; a balance valve core, a control valve core and a one-way valve core; a first chamber, a second chamber, a third chamber and a fourth chamber are sequentially arranged in the valve cavity from one end close to the control cylinder body to one end close to the end cover. The utility model can make the oil stably flow in the flow control type amplitude-variable balance valve by controlling the matching and the action among the valve core, the one-way valve core, the balance valve core, the first chamber, the second chamber, the third chamber and the fourth chamber, thereby realizing the one-way function, the load keeping function and the hydraulic control throttling function, and in addition, the equidirectional amplitude-variable balance valve with the overflow function is greatly influenced by the back pressure; and fluctuations in load pressure can also affect the stability of the balance valve to the system.
Description
Technical Field
The utility model belongs to the technical field of hoisting machinery, engineering machine tool, agricultural machine hydraulic control, a flow control type becomes width of cloth balanced valve is related to.
Background
The amplitude variation of the crane means that the crane boom is driven to drop or rise through the angle change of the crane boom. The luffing mechanism can enlarge the operation range of the crane, improve the working maneuverability and improve the production efficiency; the position of the fetching device is changed to meet the requirements of lifting capacity and loading and unloading positions; the trafficability of the crane during non-working is improved.
In the luffing mechanism, a luffing balancing valve plays a crucial role. The angle of the suspension arm is changed by the action of the amplitude-variable balance valve to realize the lifting and descending of the suspension arm, the speed limit in the action process and the suspension arm to be kept at any position in the air. In the prior art, the equidirectional variable amplitude balance valve with the overflow function is widely applied. However, in the action process of the overflow equidirectional variable-amplitude balance valve, the spring is easy to fatigue damage by the precompression force of the spring, so that the balance valve is easy to fail, the oil cylinder is out of control and rapidly descends, and therefore potential safety hazards exist; in addition, the homodromous amplitude-variable balance valve with the overflow function is greatly influenced by back pressure; and fluctuations in load pressure can also affect the stability of the balance valve to the system.
Disclosure of Invention
The utility model aims at having the above-mentioned problem to current technique, provided a flow control type that security is high, stability is good becomes width of cloth balanced valve.
The purpose of the utility model can be realized by the following technical proposal: a flow control variable amplitude balanced valve comprising:
the valve body is internally provided with a valve cavity with two through ends; a first passage and a second passage respectively communicated with the valve cavity; the port B and the port A are respectively communicated with the first channel and the second channel;
the control cylinder body is inserted at one end of the valve cavity and internally provided with a control valve core and a control cavity for accommodating the control valve core;
the end cover is inserted at the other end of the valve cavity, and an end cover cavity is arranged in the end cover;
the balance valve core is inserted in the valve cavity, one side of the balance valve core, which is close to the control cylinder body, is connected with the control valve core into a whole through threads, the one-way valve core is positioned in the balance valve core, one side of the balance valve core, which is close to the end cover, is inserted in the end cover cavity, and a spring is arranged between the end cover cavity and the balance valve core;
a first chamber, a second chamber, a third chamber and a fourth chamber are sequentially arranged in the valve cavity from one end close to the control cylinder body to one end close to the end cover.
As a further improvement of the utility model, a transition plate is also arranged, and the transition plate is fixedly connected with the valve body through a screw; a transition cavity communicated with the first channel is arranged in the transition plate; the part of the screw inserted in the valve body is less than half of the whole length of the valve body.
As a further improvement of the utility model, the first chamber is formed by surrounding a valve cavity, a control valve core, a control cylinder body and a balance valve core together; the second chamber is formed by surrounding a valve cavity and a control valve core, a first through hole vertical to the axial direction of the balance valve core is formed in the one-way valve core in the second chamber, a second through hole vertical to the axial direction of the balance valve core is formed in the balance valve core, the interior of the one-way valve core is communicated with the second chamber through the first through hole and the second through hole, and the second chamber is connected with the first channel; the third chamber is formed by surrounding a balance valve core and a valve cavity; the fourth chamber is surrounded by a valve cavity, a balance valve core and an end cover, a third through hole for communicating the inside of the balance valve core with the fourth chamber is arranged on the balance valve core, and the fourth chamber is connected with the second channel.
As a further improvement, the check valve core makes the oil only flow into the second chamber from the inside of the balance valve core.
As a further improvement of the present invention, the first passage is perpendicular to the second passage, the first passage is perpendicular to the valve chamber, and the first passage is not on the same plane as the second passage.
As a further improvement, the control cylinder body is kept away from valve body one end and is set up the control mouth, and the control mouth is connected with the X mouth, is provided with first filter screen and first damping in the control mouth.
As a further improvement of the utility model, a third channel for communicating the first chamber and the fourth chamber is arranged on the valve body.
As a further improvement, the ratio of the effective stressed area of the end cover cavity to the effective stressed area of the first chamber is 1.0-1.1.
As a further improvement, the diameters of the two side balance valve cores in the second chamber are the same, and the stress area is equal.
As a further improvement of the utility model, one end of the balance valve core close to the end cover is provided with a one-way damping valve and a second damping which are connected in parallel; a second filter screen is arranged on one side, close to the second channel, of the balance valve core; the parallel one-way damping valve and the second damping are connected with the second filter screen in series. Specifically, the second damping valve is connected with the one-way damping valve in parallel, and the second damping valve is connected with the one-way damping valve in parallel and then connected with the second filter screen in series.
As a further improvement of the utility model, a first valve cavity bulge, a second valve cavity bulge and a third valve cavity bulge are arranged in the valve cavity and used for separating the first chamber, the second chamber and the third chamber; the valve rod is provided with a first valve rod bulge, a second valve rod bulge and a third valve cavity bulge which are matched with the first valve cavity bulge, the second valve cavity bulge and the third valve cavity bulge.
As a further improvement of the utility model, at least one throttling groove is arranged on the second valve rod protrusion.
As a further improvement of the utility model, the third valve cavity is protruded and the third valve rod is protruded to form a line contact.
As a further improvement of the utility model, the ratio of the effective stressed area of the end cover cavity to the effective stressed area of the first chamber is 1.0-1.1; the diameters of the balance valve cores on the two sides in the second chamber are the same, and the stress areas are the same.
Based on the technical scheme, the embodiment of the utility model provides a can produce following technological effect at least: the utility model discloses a cooperation and action between control case, check case, balanced case, first room, second room, third room, the fourth room make flowing in flow control type amplitude-varying balance valve that fluid can be stable, realized one-way function, load holding, liquid accuse throttle function, and this balanced valve does not have the overflow function, does not receive load pressure fluctuation's influence, and the influence of oil return backpressure weakens greatly. The one-way valve core enables the oil to flow into the second chamber only in one direction from the interior of the balance valve core. Therefore, the structure is compact. Through setting up the first passageway of transition chamber further extension, the part of screw grafting in the valve body is less than half length of whole valve body, has avoided the screw to insert the valve body and screw up and the problem of the valve body deformation that leads to, improves the sealed effect and the life of valve body.
Drawings
The following detailed description of embodiments of the invention is provided with reference to the accompanying drawings, in which:
fig. 1 is a structural section view of the flow control variable amplitude balance valve with one-way function.
Fig. 2 is a cross-sectional view from another perspective of fig. 1.
Fig. 3 is a cross-sectional view of a flow control type luffing balancing valve under load hold.
Fig. 4 is a sectional view of the flow control type variable amplitude balance valve under the function of hydraulic control throttling.
Fig. 5 is a hydraulic schematic diagram of the flow control type variable amplitude balance valve during the one-way function and the load maintaining.
Fig. 6 is a hydraulic schematic diagram of the flow control type variable amplitude balance valve with a hydraulic control throttling function.
Fig. 7 is a sectional view of a valve body and a transition plate of a flow control type luffing balance valve.
Fig. 8 is a schematic structural diagram of the control cylinder, the balance valve core and the end cover.
In the figure, 100, valve body; 111. a first chamber; 112. a second chamber; 113. a third chamber; 114. a fourth chamber; 115. a first through hole; 116. a second through hole; 117. a third through hole; 120. a first channel; 121. a second channel; 122. a third channel; 131. a first valve cavity bulge; 132. a second valve chamber projection; 133. a third lumen bulge; 141. a first valve stem protrusion; 142. a second stem projection; 143. a third valve stem protrusion; 144. a throttling groove; 200. controlling the cylinder body; 210. a control valve core; 220. a control chamber; 230. a control port; 231. a first filter screen; 232. a first damping; 300. an end cap; 310. an end cap cavity; 400. a balanced valve core; 410. a one-way valve core; 420. a spring; 430. a one-way damping valve; 440. a second damping; 450. a second filter screen; 500. a transition plate; 510. a transition chamber; 520. and (4) screws.
Detailed Description
The following are specific embodiments of the present invention and the accompanying drawings are used to further describe the technical solution of the present invention, but the present invention is not limited to these embodiments.
The technical solution provided by the present invention is explained in more detail with reference to fig. 1 to 8.
A flow control type luffing balance valve, as shown in fig. 1-4, 8, comprising: valve body 100, control cylinder 200, end cover 300.
A valve cavity with two through ends, a first passage 120 and a second passage 121 communicated with the valve cavity respectively are arranged in the valve body 100; a port B and a port a which are respectively communicated with the first passage 120 and the second passage 121;
the control cylinder 200 is connected to one end of the valve cavity through a thread, and a control valve core 210 and a control cavity 220 for accommodating the control valve core 210 are arranged in the control cylinder;
the end cover 300 is inserted at the other end of the valve cavity, and an end cover cavity 310 is arranged inside the end cover 300;
the balance valve core 400 is inserted in the valve cavity, one side of the balance valve core 400 close to the control cylinder body 200 is connected with the control valve core 210 into a whole through threads, the one-way valve core 410 is positioned in the balance valve core 400, one side of the balance valve core 400 close to the end cover 300 is inserted in the end cover cavity 310, and a spring 420 is arranged between the end cover cavity 310 and the balance valve core 400;
a first chamber 111, a second chamber 112, a third chamber 113 and a fourth chamber 114 are sequentially arranged in the valve cavity from one end close to the control cylinder body 200 to one end close to the end cover 300; the first chamber 111 is formed by surrounding a valve cavity, a control valve core 210, a control cylinder body 200 and a balance valve core 400 together; the second chamber 112 is formed by surrounding a valve cavity and a control valve core 210, a first through hole 115 vertical to the axial direction of the balance valve core is arranged on a one-way valve core 410 in the second chamber, a second through hole 116 vertical to the axial direction of the balance valve core is arranged on the balance valve core 400, the interior of the one-way valve core 410 is communicated with the second chamber 112 through the first through hole 115 and the second through hole 116, and the second chamber 112 is connected with the first channel 120; the third chamber 113 is formed by enclosing a balanced valve core 400 and a valve cavity; the fourth chamber 114 is surrounded by a valve chamber, a balanced valve core 400 and an end cover 300, a third through hole 117 for communicating the inside of the balanced valve core 400 and the fourth chamber 114 is arranged on the balanced valve core 400, and the fourth chamber 114 is connected with the second channel 121.
The check valve spool 410 allows oil to flow into the second chamber 112 only in one direction from within the balanced valve spool 400.
The control cylinder 200 is provided with a control port 230 at an end thereof remote from the valve body 100.
The first passage 120 and the second passage 121 are perpendicular to each other, the first passage 120 and the second passage 121 are perpendicular to the valve cavity, the first passage 120 and the second passage 121 are not on the same plane, a port B is connected with an oil inlet of the hydraulic oil cylinder, and a port A is connected with the multi-way valve.
Be provided with first filter screen 231 and first damping 232 in the control mouth 230, first filter screen 231 filters the fluid of injecting through control mouth 230, avoids impurity in the fluid to get into the balanced valve, improves the life-span of balanced valve. The first damper 232 ensures the stability of entering oil, has a filtering effect, and effectively prevents the shaking phenomenon of the initial opening of the balance valve.
The valve body 100 is provided with a third passage 122 that communicates the first chamber 111 with the fourth chamber 114. The oil between the first and fourth chambers 111 and 114 can flow through the third passage 122, so that the first and fourth chambers 111 and 114 maintain the same pressure, and the pressure oil of the first and fourth chambers 111 and 114 is all introduced from the low pressure chamber a port.
The ratio of the effective force-receiving area of the end cap cavity 310 to the effective force-receiving area of the first chamber 111 is 1.0-1.1. Specifically, the ratio of the circular area formed by the end cover cavity 310 to the annular area formed by the valve cavity in the first chamber 111 and the control valve core 210 is 1.03, and the circular area formed by the end cover cavity 310 is specifically the circular area formed by the contact position of the end cover 300 and the balance valve core 400; the annular area formed by the valve cavity in the first chamber 111 and the control valve core 210 is specifically the circular area formed by the contact position of the first valve cavity bulge 131 and the first valve rod bulge 141 minus the circular area of the control valve core 210. Since this ratio is negligible compared to the control pressure, the balanced spool 400 is not affected by the return back pressure.
The diameters of the two side balance valve cores 400 in the second chamber 112 are the same, and the stressed areas are the same. Therefore, the effective acting area acting on the balance valve body 400 is zero regardless of the change in the load, and the balance valve body 400 cannot be pushed. The balance valve is not influenced by load pressure fluctuation, and the stability of the balance valve is improved.
One end of the balance valve core 400 close to the end cover 300 is provided with a one-way damping valve 430 and a second damper 440 which are connected in parallel; a second filter screen 450 is arranged on one side of the balance valve core 400 close to the second channel 121; the parallel one-way damping valve 430 and the second damping 440 are connected in series with the second filter screen 450. The oil entering from the second channel 121 passes through the second filter screen 450, the one-way damping valve 430 and the second damper 440 which are connected in parallel, and enters the end cover cavity 310. In addition, the check damper valve 430 allows oil to flow into the head chamber 310 only in one direction from the second passage 121. The oil can flow into the end cover cavity 310 through the two passages of the one-way damping valve 430 and the second damper 440, and the oil can only flow out of the end cover cavity 310 through the passage of the second damper 440. The one-way damping valve 430 is arranged to enable oil to flow into the end cover cavity 310 rapidly and flow out of the end cover cavity 310 slowly, when the end cover cavity 310 is under pressure, the oil keeps flowing out of the end cover cavity 310 slowly under the action of the second damper 440, a flow stabilizing effect is achieved, and the situation that the amplitude-variable balance valve is too large in fluctuation and difficult to control is avoided. The one-way damping valve 430 and the second damper 440 form a parallel structure to realize the slow-opening and fast-returning functions of the balance valve.
Further, the second damper 440 is formed by connecting three dampers in series. Three dampers are connected in series, so that the flow stabilizing effect can be improved, and the amplitude-variable balance valve is more stable.
Furthermore, the spring 420 is provided with two sleeved springs, and the arrangement of the two springs further distributes the pressure, thereby improving the service life of the spring 420 and reducing the loss of the spring 420.
A first valve cavity bulge 131, a second valve cavity bulge 132 and a third valve cavity bulge 133 for separating the first chamber 111, the second chamber 112 and the third chamber 113 are arranged in the valve cavity; the valve stem is provided with a first valve stem protrusion 141, a second valve chamber protrusion 142 and a third valve stem protrusion 143 which are matched with the first valve chamber protrusion 131, the second valve chamber protrusion 132 and the third valve chamber protrusion 133.
A check ring and a seal ring are provided between the first valve chamber protrusion 131 and the first stem protrusion 141 to maintain the first chamber 111 sealed.
The second stem projection 142 is provided with a throttling groove 144, preferably four throttling grooves 144 arranged equidistantly. The throttle groove 144 serves to achieve a variable flow area effect, i.e., a one-to-one correspondence of control pressure to flow area. Specifically, as shown in fig. 8, the throttle groove 144 of the present embodiment has a structure in which the second stem protrusion 142 is obliquely cut from the side close to the end cap 300 toward the side close to the control cylinder 200 and toward the inside of the control valve body 210.
Line contact is formed between third valve chamber projection 133 and third valve stem projection 143 to form a line seal. Specifically, the diameter of the third valve rod protrusion 143 on the side close to the end cap 300 is larger than the diameter on the side close to the control cylinder 200. That is, the third valve stem protrusion 143 has a slope shape, and the third valve chamber protrusion 133 abuts against the third valve stem protrusion 143 to form a line contact.
When the balanced valve core 400 slides towards the end cover 300 side, the second valve rod protrusion 142 and the second valve rod protrusion 142 slide relatively, and the second chamber 112 is communicated with the third chamber 113 through the throttling groove 144; the third valve rod protrusion 143 and the third valve rod protrusion 143 are staggered, so that the third chamber 113 is communicated with the fourth chamber 114, and the larger the sliding distance of the balanced valve core 400 towards the end cover 300 is, the higher the communication degree between the second chamber 112, the third chamber 113 and the fourth chamber 114 is, and the effect of controlling the lifting and descending speed of the crane jib through flow control is realized.
Further, as shown in fig. 3 and 7, a transition plate 500 is further provided, and the transition plate 500 is fixedly connected with the valve body 100. A transition cavity 510 communicated with the first channel 120 is arranged in the transition plate 500, and the first channel 120 is further extended through the transition cavity 510, so that the first channel 120 can be connected with an oil inlet of the hydraulic motor.
Furthermore, a first threaded hole is formed in the valve body 100, a second threaded hole matched with the first threaded hole is formed in the transition plate 500, and a screw 520 connects the valve body 100 and the transition plate 500 through the first threaded hole and the second threaded hole.
Furthermore, as shown in fig. 7, the portion of the screw 520 inserted into the valve body 100 is less than half of the length of the integrated valve body 100, thereby avoiding the problem of deformation of the valve body 100 caused by the screw 520 inserted into the valve body 100 and tightened.
The working principle is as follows:
unidirectional function: as shown in fig. 1, 2, and 5, the oil enters from the second passage 121, passes through the third through hole 117, enters the balanced valve body 400, pushes open the check valve body 410, enters the first chamber 111 through the second through hole 116, and flows out through the first passage 120. Meanwhile, the oil entering from the second passage 121 sequentially passes through the second filter screen 450, the one-way damping valve 430 and the second damper 440 which are connected in parallel, and enters the end cover cavity 310; the oil introduced from the second passage 121 is introduced into the first chamber 111 through the process holes. Under the one-way function, the oil flows to the load, so that the angle of the crane jib is increased to realize lifting.
Load keeping: as shown in fig. 3 and 5, the oil stops entering from the second passage 121, and the check valve element 410 is closed. In the load holding state, the flow of oil in the first passage 120 and the second chamber 112 is stopped, and the high pressure is maintained, so that the crane boom is stopped in the air.
The hydraulic control throttling function: as shown in fig. 4 and 6, oil is injected into the control chamber 220 through the control port 230, and pushes the control spool 210, the check spool 410, and the balance spool 400 to move toward the end cap 300, the second spool protrusion 132 and the second spool protrusion 142 are misaligned, the third spool protrusion 143 and the third spool protrusion 143 are misaligned, the second chamber 112, the third chamber 113, and the fourth chamber 114 are communicated, and the oil in the first passage 120 flows into the second passage 121 through the second chamber 112, the third chamber 113, and the fourth chamber 114, and finally flows out. At the same time, the oil in the first chamber 111, the fourth chamber 114 and the rear cover chamber may continue to flow out through the second passage 121.
The specific embodiments described herein are merely illustrative of the spirit of the invention. Various modifications, additions and substitutions for the specific embodiments described herein may be made by those skilled in the art without departing from the spirit of the invention or exceeding the scope of the invention as defined in the accompanying claims.
Claims (9)
1. A flow control type variable amplitude balance valve, comprising:
the valve body is internally provided with a valve cavity with two through ends; a first passage and a second passage respectively communicated with the valve cavity; the port B and the port A are respectively communicated with the first channel and the second channel;
the control cylinder body is inserted at one end of the valve cavity and internally provided with a control valve core and a control cavity for accommodating the control valve core;
the end cover is inserted at the other end of the valve cavity, and an end cover cavity is arranged in the end cover;
the balance valve core is inserted in the valve cavity, one side of the balance valve core, which is close to the control cylinder body, is connected with the control valve core into a whole through threads, the one-way valve core is positioned in the balance valve core, one side of the balance valve core, which is close to the end cover, is inserted in the end cover cavity, and a spring is arranged between the end cover cavity and the balance valve core;
a first chamber, a second chamber, a third chamber and a fourth chamber are sequentially arranged in the valve cavity from one end close to the control cylinder body to one end close to the end cover;
the transition plate is fixedly connected with the valve body through a screw; a transition cavity communicated with the first channel is arranged in the transition plate; the part of the screw inserted in the valve body is less than half of the whole length of the valve body.
2. The flow control type variable amplitude balance valve as claimed in claim 1, wherein the first chamber is surrounded by a valve chamber, a control valve core, a control cylinder body and a balance valve core; the second chamber is formed by surrounding a valve cavity and a control valve core, a first through hole vertical to the axial direction of the balance valve core is formed in the one-way valve core in the second chamber, a second through hole vertical to the axial direction of the balance valve core is formed in the balance valve core, the interior of the one-way valve core is communicated with the second chamber through the first through hole and the second through hole, and the second chamber is connected with the first channel; the third chamber is formed by surrounding a balance valve core and a valve cavity; the fourth chamber is surrounded by a valve cavity, a balance valve core and an end cover, a third through hole for communicating the inside of the balance valve core with the fourth chamber is arranged on the balance valve core, and the fourth chamber is connected with the second channel.
3. The flow control variable amplitude balanced valve as recited in claim 1 wherein the check valve spool allows oil to flow only from the interior of the balanced valve spool into the second chamber.
4. The flow control type variable amplitude balance valve as claimed in claim 1, wherein a control port is provided at one end of the control cylinder body away from the valve body, the control port is connected with the port X, and a first filter screen and a first damper are provided in the control port.
5. The flow control type amplitude balance valve as claimed in claim 1, wherein the valve body is provided with a third passage communicating the first chamber with the fourth chamber.
6. The flow control type variable amplitude balance valve as claimed in claim 1, wherein one end of the balance valve core close to the end cover is provided with a one-way damping valve and a second damping which are connected in parallel; a second filter screen is arranged on one side, close to the second channel, of the balance valve core; the parallel one-way damping valve and the second damping are connected with the second filter screen in series.
7. The flow control type amplitude balance valve as claimed in claim 1, wherein a first valve chamber protrusion, a second valve chamber protrusion and a third valve chamber protrusion are arranged in the valve chamber for separating the first chamber, the second chamber and the third chamber; the valve rod is provided with a first valve rod bulge, a second valve rod bulge and a third valve cavity bulge which are matched with the first valve cavity bulge, the second valve cavity bulge and the third valve cavity bulge.
8. The flow control type variable amplitude balance valve as claimed in claim 7, wherein the second valve stem protrusion is provided with at least one throttling groove; and the third valve cavity bulge and the third valve rod bulge form line contact.
9. The flow control type variable amplitude balance valve according to claim 1, wherein the ratio of the effective force-receiving area of the end cap chamber to the effective force-receiving area of the first chamber is 1.0 to 1.1; the diameters of the balance valve cores on the two sides in the second chamber are the same, and the stress areas are the same.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921395788.5U CN210710470U (en) | 2019-08-26 | 2019-08-26 | Flow control type variable amplitude balance valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921395788.5U CN210710470U (en) | 2019-08-26 | 2019-08-26 | Flow control type variable amplitude balance valve |
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| Publication Number | Publication Date |
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| CN210710470U true CN210710470U (en) | 2020-06-09 |
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| CN201921395788.5U Active CN210710470U (en) | 2019-08-26 | 2019-08-26 | Flow control type variable amplitude balance valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112833069A (en) * | 2020-12-31 | 2021-05-25 | 沈小荣 | Intelligent hydraulic valve with liquid impurity separation function and use method thereof |
-
2019
- 2019-08-26 CN CN201921395788.5U patent/CN210710470U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112833069A (en) * | 2020-12-31 | 2021-05-25 | 沈小荣 | Intelligent hydraulic valve with liquid impurity separation function and use method thereof |
| CN112833069B (en) * | 2020-12-31 | 2023-12-08 | 沈小荣 | Intelligent hydraulic valve with liquid impurity separation function and use method thereof |
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Address after: No.98 xingyong Road, Jiangbei District, Ningbo City, Zhejiang Province Patentee after: Ningbo Yuzhou Hydraulic Equipment Co.,Ltd. Address before: No.98 xingyong Road, Jiangbei District, Ningbo City, Zhejiang Province Patentee before: NINGBO JIANGBEI YUZHOU HYDRAULIC EQUIPMENT FACTORY |
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