CN112727830A - Reversing hydraulic valve - Google Patents
Reversing hydraulic valve Download PDFInfo
- Publication number
- CN112727830A CN112727830A CN202011639730.8A CN202011639730A CN112727830A CN 112727830 A CN112727830 A CN 112727830A CN 202011639730 A CN202011639730 A CN 202011639730A CN 112727830 A CN112727830 A CN 112727830A
- Authority
- CN
- China
- Prior art keywords
- oil
- axial
- valve body
- radial hole
- rotary valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0685—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
- F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/06—Construction of housing; Use of materials therefor of taps or cocks
- F16K27/065—Construction of housing; Use of materials therefor of taps or cocks with cylindrical plugs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N37/00—Equipment for transferring lubricant from one container to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
- F16N7/40—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems in a closed circulation system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N37/00—Equipment for transferring lubricant from one container to another
- F16N2037/006—Filling
Abstract
The invention discloses a reversing hydraulic valve, and belongs to the technical field of engineering machinery. The reversing valve overcomes the defects of large hydraulic power and poor reversing stability of the traditional reversing valve in the prior art. The main structure of the rotary valve comprises a valve body, wherein an oil port A, an oil port B, an oil port P and an oil port T are arranged on the valve body, a rotary valve core is arranged in the valve body and is connected with the valve body through an end cover, a bearing I and a bearing II are arranged between the rotary valve core and the valve body, a driving device is arranged on the end cover, and a driving shaft of the driving device is connected with the rotary valve core. The invention is mainly used for engineering machinery.
Description
The technical field is as follows:
the invention belongs to the technical field of engineering machinery, and particularly relates to a reversing hydraulic valve.
Background art:
in the prior art, a rotary valve realizes the cutting off of an oil way through a valve core and realizes the combined action of a left rotary oil cylinder and a right rotary oil cylinder; however, the low rotation speed (0.25r/s) causes the small clearance fit between the spool and the housing, and the high rotation speed causes direct rotational friction, oil film lubrication, and dynamic balance between the spool and the housing, which limits the high-speed operation of the rotary valve. The common reversing valve (slide valve) moves axially to close an oil way, the reversing frequency of the reversing valve used in the current hydraulic pipeline or oil cylinder pulse test is 1Hz, the reversing frequency is low, and if the reversing frequency is high, the problems of large hydraulic force, poor reversing stability and the like can be caused.
The invention content is as follows:
the technical problem to be solved by the invention is to overcome the defects of the prior art and provide a reversing hydraulic valve which can realize high-frequency opening and closing control and has simple structure and low cost.
In order to realize the purpose, the invention is realized by adopting the following technical scheme:
a reversing hydraulic valve comprises a valve body, wherein an oil port A, an oil port B, an oil port P and an oil port T are arranged on the valve body, a rotary valve core is arranged in the valve body and is connected with the valve body through an end cover, a bearing I and a bearing II are arranged between the rotary valve core and the valve body, a driving device is arranged on the end cover, and a driving shaft of the driving device is connected with the rotary valve core.
Preferably, one end of the valve body is provided with two process holes, and the process holes are provided with a static seal II and a screw plug.
Preferably, the outer side of the end cover is provided with a baffle plate, the baffle plate is connected with the end cover through a screw A, a first static seal is arranged between the valve body and the end cover, and a rotary seal is arranged between the rotary valve core and the end cover.
Preferably, the rotary valve core is provided with a first annular oil passage, a second annular oil passage and a third annular oil passage, two or more first axial oil grooves and two or more second axial oil grooves are uniformly distributed on the periphery of the rotary valve core, the first axial oil grooves and the second axial oil grooves are alternately distributed, the first annular oil passage is communicated with the first axial oil grooves, and the second annular oil passage is communicated with the second axial oil grooves.
Preferably, the bilateral symmetry of first axial oil groove is equipped with first oil groove, and the bilateral symmetry of second axial oil groove is equipped with the second oil groove.
Preferably, a first balance groove and a second balance groove are formed in the rotary valve element, and the first balance groove is communicated with the first annular oil channel through a first axial oil groove.
Preferably, the first annular oil duct is symmetrically provided with a first radial hole and a second radial hole, the third annular oil duct is symmetrically provided with a third radial hole and a sixth radial hole, the rotary valve core is internally provided with a second axial hole and a first axial hole, one end of the first annular oil duct is communicated with the third annular oil duct through the first radial hole, the first axial hole and the sixth radial hole, and the other end of the first annular oil duct is communicated with the third annular oil duct through the second radial hole, the second axial hole and the third radial hole.
Preferably, a fourth radial hole is formed in the second annular oil passage, a third axial hole and a fifth radial hole are further formed in the rotary valve core, a leakage oil passage is formed between the bearing I and the rotary seal, and the second annular oil passage is communicated with the leakage oil passage through the fourth radial hole, the third axial hole and the fifth radial hole.
Preferably, the first annular oil duct in the rotary valve core is communicated with the oil port P, the second annular oil duct is communicated with the oil port T, the oil ports a and B are distributed on the valve body, and the distribution angle between the oil ports a and B is
Distribution angle
/[ number of first axial oil grooves + number of second axial oil grooves]。
Compared with the prior art, the invention has the beneficial effects that:
1. the invention can realize high-frequency opening and closing control, solves the defect of complexity in controlling the high-frequency opening and closing axial movement of the slide valve, solves the defect of friction between the rotary valve core and the shell by connecting the rotary valve core and the valve body through a bearing, and has simple structure and low cost;
2. the bearing is lubricated through leakage of pressure oil, and the pressure oil forms a lubricating oil film between the rotary valve core and the valve body, and the axial groove pressure oil and the annular channel pressure oil can play a role in balance support of the static pressure bearing on the rotary valve core.
Description of the drawings:
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a top view of the present invention;
FIG. 3 is a front view of the present invention;
FIG. 4 is a schematic view of the rotary valve cartridge of the present invention;
FIG. 5 is a cross-sectional view A-A of FIG. 2;
FIG. 6 is a cross-sectional view taken along line B-B of FIG. 3;
FIG. 7 is a cross-sectional view (to the left) of C-C of FIG. 2;
FIG. 8 is a cross-sectional view of C-C of FIG. 2 (neutral);
FIG. 9 is a cross-sectional view (right) of C-C in FIG. 2;
FIG. 10 is a cross-sectional view of C-C of FIG. 2 (mid-right switch);
fig. 11 is a hydraulic graphic symbol of the present invention.
In the figure: 1. a valve body; 2. rotating the valve core; 3. a first bearing; 4. static sealing is carried out; 5. an end cap; 6. a screw A; 7. rotating and sealing; 8. a process plug; 9. a baffle plate; 10. a second bearing; 11. static sealing II; 12. a plug screw; 13. a screw B; 14. a drive device; 101. a fabrication hole; 201. a first annular oil passage; 202. a first axial oil groove; 203. a first oil groove; 204. a second annular oil passage; 205. a third annular oil passage; 206. a third radial hole; 207. a second axial bore; 208. a first axial bore; 209. a third axial bore; 210. a first radial bore; 211. a second radial bore; 212. a fifth radial hole; 213. a fourth radial hole; 214. an oil leakage passage; 215. a sixth radial hole; 217. a second axial oil groove; 218. a second oil groove; 219. a first balance groove; 220. a second balancing groove.
The specific implementation mode is as follows:
the invention is further illustrated by the following specific examples in combination with the accompanying drawings.
Example 1:
as shown in fig. 1-6 and 11, the reversing hydraulic valve comprises a valve body 1, wherein an oil port a, an oil port B, an oil port P and an oil port T are arranged on the valve body 1, a rotary valve core 2 is arranged in the valve body 1, the rotary valve core 2 is connected with the valve body 1 through an end cover 5, a bearing i 3 and a bearing ii 10 are arranged between the rotary valve core 2 and the valve body 1, a driving device 14 is arranged on the end cover 5, and a driving shaft of the driving device 14 is connected with the rotary valve core 2. The driving device 14 may be a motor, and may also be an electric motor.
Example 2:
a reversing hydraulic valve is characterized in that two process holes 101 are formed in one end of a valve body 1, a second static seal 11 and a plug screw 12 are mounted on the process holes 101, and the process holes 101 are used for dismounting a second bearing 10.
The outer side of the end cover 5 is provided with a baffle plate 9, the baffle plate 9 is connected with the end cover 5 through a screw A6, a static seal 4 is arranged between the valve body 1 and the end cover 5, a rotary seal 7 is arranged between the rotary valve core 2 and the end cover 5, and the valve body 1 is connected with the end cover 5 through a screw B13.
The rotary valve core 2 is provided with a first annular oil duct 201, a second annular oil duct 204 and a third annular oil duct 205, two or more first axial oil grooves 202 and two or more second axial oil grooves 217 are uniformly distributed on the periphery of the rotary valve core 2, the first axial oil grooves 202 and the second axial oil grooves 217 are alternately distributed, the first annular oil duct 201 is communicated with the first axial oil grooves 202, and the second annular oil duct 204 is communicated with the second axial oil grooves 217. At this time, the reversing hydraulic valve is in an O-shaped function.
The first oil groove 203 is symmetrically arranged on two sides of the first axial oil groove 202, the second oil groove 218 is symmetrically arranged on two sides of the second axial oil groove 217, and the reversing hydraulic valve is H-shaped in function by adding the first oil groove 203 and the second oil groove 218.
The rotary valve core 2 is provided with a first balance groove 219 and a second balance groove 220, and the first balance groove 219 is communicated with the first annular oil passage 201 through a first axial oil groove 202.
The first annular oil passage 201 is symmetrically provided with a first radial hole 210 and a second radial hole 211, the third annular oil passage 205 is symmetrically provided with a third radial hole 206 and a sixth radial hole 215, the rotary valve element 2 is internally provided with a second axial hole 207 and a first axial hole 208, one end of the first annular oil passage 201 is communicated with the third annular oil passage 205 through the first radial hole 210, the first axial hole 208 and the sixth radial hole 215, and the other end of the first annular oil passage 201 is communicated with the third annular oil passage 205 through the second radial hole 211, the second axial hole 207 and the third radial hole 206. The ends of the second axial hole 207 and the first axial hole 208 are provided with process plugs 8 to prevent leakage.
The second annular oil passage 204 is provided with a fourth radial hole 213, a third axial hole 209 and a fifth radial hole 212 are further formed in the rotary valve core 2, a leakage oil passage 214 is formed between the bearing I3 and the rotary seal 7, and the second annular oil passage 204 is communicated with the leakage oil passage 214 through the fourth radial hole 213, the third axial hole 209 and the fifth radial hole 212. Leaked oil between the first bearing 3 and the rotary seal 7 returns to the oil tank through the fifth radial hole 212, the third axial hole 209, the fourth radial hole 213, the second annular oil duct 204 and the oil port T of the valve body 1, so that the phenomenon that the leaked oil for lubricating the bearings on the two sides forms high pressure due to oil trapping is avoided.
The first annular oil duct 201 in the rotary valve core 2 is communicated with the oil port P, the second annular oil duct 204 is communicated with the oil port T, the oil ports a and B are distributed on the valve body 1, and the distribution angle between the oil ports a and B is
Distribution angle
/[ number of first axial oil grooves 202 + number of second axial oil grooves 217 ]]. The other portions are the same as in example 1.
The working principle of the invention is as follows:
pressure oil enters the first annular oil duct 201 and the first axial oil groove 202 through an oil port P of the valve body 1, part of the pressure oil enters the third annular oil duct 205 through the first radial hole 210, the second radial hole 211, the first axial hole 208, the second axial hole 207, the sixth radial hole 215 and the third radial hole 206, the pressure oil in the third annular oil duct 205 forms static pressure support, and meanwhile leaks into the second annular oil duct 204 and a leakage oil passage 214 between the bearing I3 and the rotary seal 7 through a fit clearance between the valve body 1 and the rotary valve core 2, so that a lubricating oil film between the rotary valve core 2 and the valve body 1 is formed on one hand, and lubrication is provided for the bearing I3 on the other hand; meanwhile, the pressure oil in the first annular oil passage 201 leaks to flow to the second bearing 10 on the left side through the fit clearance between the rotary valve element 2 and the valve body 1, so that lubrication is provided. And lubricating leakage oil of the second bearing 10 returns to the oil tank through the third axial hole 209, the fourth radial hole 213, the second annular oil passage 204 and the oil port T of the valve body 1.
When the rotary valve core 2 rotates a certain angle (as a left side diagram shown in fig. 7, three black filled parts are high pressure oil, and three blank parts are low pressure oil), the pressure oil is communicated with an oil port a of the valve body 1 through an oil port P of the valve body 1, the first annular oil channel 201 of the rotary valve core 2 and the first axial oil groove 202 to form P, A; at this time, the oil port B of the valve body 1 is communicated with the oil port T of the valve body 1 through the second axial oil groove 217 of the rotary valve core 2 and the second annular oil passage 204 to form B, T.
When the rotary valve core 2 rotates a certain angle (as shown in the middle bit map of fig. 8), the pressure oil is led to the oil port a of the valve body 1 through the throttling action of the oil port P of the valve body 1, the first annular oil channel 201, the first axial oil groove 202 and the first oil groove 203 of the rotary valve core 2, so that P, A intercommunication is formed; meanwhile, the pressure oil is led to the oil port A of the valve body 1 through the throttling action of the oil port P of the valve body 1, the first annular oil channel 201 of the rotary valve core 2, the first axial oil groove 202 and the first oil groove 203, so that P, B intercommunication is formed.
At this time, the oil port B of the valve body 1 is communicated with the oil port T of the valve body 1 through the second oil groove 218, the second axial oil groove 217 and the second annular oil channel 204 of the rotary valve core 2 to form B, T; meanwhile, an oil port A of the valve body 1 is communicated with an oil port T of the valve body 1 through ｃA second oil groove 218, ｃA second axial oil groove 217 and ｃA second annular oil channel 204 of the rotary valve core 2 to form B, T, so that P-A-B-T communication is formed in the middle position, and an H-type function is formed.
When the rotary valve core 2 rotates a certain angle (as shown in a right side view of fig. 9), the pressure oil is led to the oil port B of the valve body 1 through the oil port P of the valve body 1, the first annular oil passage 201 of the rotary valve core 2 and the first axial oil groove 202 to form P, B intercommunication; at this time, the oil port a of the valve body 1 is communicated with the oil port T of the valve body 1 through the second axial oil groove 217 of the rotary valve core 2 and the second annular oil passage 204 to form A, T.
As shown in fig. 10, when the rotary valve core 2 rotates one cycle, P/a communication is generated n times (B/T communication n times) (n is the number of the first axial oil grooves 202), P/a cut is generated n times (B/T cut n times), P/B communication is generated n times (a/T communication n times) (n is the number of the second axial oil grooves 217), and then a/B port is generated to output pressure oil n times; when the rotating speed of the rotary valve core 2 is changed, the on-off times of P/A/B/T can be changed, high-frequency opening and closing are realized, and the frequency is adjustable. The P/A/B/T is H-shaped, and gradually changes in the opening and closing process of the oil port, so that the impact of instantaneous opening and closing is reduced.
Claims (9)
1. The utility model provides a switching-over hydrovalve, includes valve body (1), be equipped with hydraulic fluid port A, hydraulic fluid port B, hydraulic fluid port P and hydraulic fluid port T on valve body (1), its characterized in that: the rotary valve is characterized in that a rotary valve core (2) is arranged in the valve body (1), the rotary valve core (2) is connected with the valve body (1) through an end cover (5), a first bearing (3) and a second bearing (10) are arranged between the rotary valve core (2) and the valve body (1), a driving device (14) is arranged on the end cover (5), and a driving shaft of the driving device (14) is connected with the rotary valve core (2).
2. The reversing hydraulic valve of claim 1, wherein: one end of the valve body (1) is provided with two process holes (101), and the process holes (101) are provided with a static seal II (11) and a screw plug (12).
3. The reversing hydraulic valve of claim 2, wherein: the outer side of the end cover (5) is provided with a baffle (9), the baffle (9) is connected with the end cover (5), a static seal I (4) is arranged between the valve body (1) and the end cover (5), and a rotary seal (7) is arranged between the rotary valve core (2) and the end cover (5).
4. The reversing hydraulic valve of claim 3, wherein: the oil-gas separator is characterized in that a first annular oil duct (201), a second annular oil duct (204) and a third annular oil duct (205) are arranged on the rotary valve core (2), two or more first axial oil grooves (202) and two or more second axial oil grooves (217) are uniformly distributed on the periphery of the rotary valve core (2), the first axial oil grooves (202) and the second axial oil grooves (217) are alternately distributed, the first annular oil duct (201) is communicated with the first axial oil grooves (202), and the second annular oil duct (204) is communicated with the second axial oil grooves (217).
5. The reversing hydraulic valve of claim 4, wherein: the two sides of the first axial oil groove (202) are symmetrically provided with a first oil groove (203), and the two sides of the second axial oil groove (217) are symmetrically provided with a second oil groove (218).
6. The reversing hydraulic valve of claim 4 or 5, wherein: the rotary valve core (2) is provided with a first balance groove (219) and a second balance groove (220), and the first balance groove (219) is communicated with the first annular oil duct (201) through a first axial oil groove (202).
7. The reversing hydraulic valve of claim 6, wherein: the oil cylinder is characterized in that a first radial hole (210) and a second radial hole (211) are symmetrically formed in the first annular oil duct (201), a third radial hole (206) and a sixth radial hole (215) are symmetrically formed in the third annular oil duct (205), a second axial hole (207) and a first axial hole (208) are formed in the rotary valve core (2), one end of the first annular oil duct (201) is communicated with the third annular oil duct (205) through the first radial hole (210), the first axial hole (208) and the sixth radial hole (215), and the other end of the first annular oil duct (201) is communicated with the third annular oil duct (205) through the second radial hole (211), the second axial hole (207) and the third radial hole (206).
8. The reversing hydraulic valve of claim 7, wherein: the oil leakage valve is characterized in that a fourth radial hole (213) is formed in the second annular oil duct (204), a third axial hole (209) and a fifth radial hole (212) are further formed in the rotary valve core (2), a leakage oil channel (214) is formed between the bearing I (3) and the rotary seal (7), and the second annular oil duct (204) is communicated with the leakage oil channel (214) through the fourth radial hole (213), the third axial hole (209) and the fifth radial hole (212).
9. The reversing hydraulic valve of claim 8, wherein: a first annular oil duct (201) in the rotary valve core (2) is communicated with the oil port P, a second annular oil duct (204) is communicated with the oil port T, the oil ports A and B are distributed on the valve body (1) and the distribution angle between the oil ports A and B is
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011639730.8A CN112727830A (en) | 2020-12-31 | 2020-12-31 | Reversing hydraulic valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011639730.8A CN112727830A (en) | 2020-12-31 | 2020-12-31 | Reversing hydraulic valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112727830A true CN112727830A (en) | 2021-04-30 |
Family
ID=75608993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011639730.8A Pending CN112727830A (en) | 2020-12-31 | 2020-12-31 | Reversing hydraulic valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112727830A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116447190A (en) * | 2023-06-14 | 2023-07-18 | 江苏曹工液压科技有限公司 | Hydraulic valve capable of flexibly reversing |
-
2020
- 2020-12-31 CN CN202011639730.8A patent/CN112727830A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116447190A (en) * | 2023-06-14 | 2023-07-18 | 江苏曹工液压科技有限公司 | Hydraulic valve capable of flexibly reversing |
| CN116447190B (en) * | 2023-06-14 | 2023-09-08 | 江苏曹工液压科技有限公司 | Hydraulic valve capable of flexibly reversing |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101847917B (en) | Axially-rotating equal-width curve double-stator multi-speed motor | |
| CN203784293U (en) | Mechanical sealing device | |
| CN112727830A (en) | Reversing hydraulic valve | |
| CN203978823U (en) | High-effect hydraulic full-balance floating buss | |
| CN215861047U (en) | Reversing hydraulic valve | |
| CN107795692A (en) | A kind of electric eddy current dynamometer bearing seal structure of thin oil lubricant | |
| CN111550578A (en) | Valve core and hydraulic valve comprising same | |
| CN203685562U (en) | Double-acting variable-displacement vane pump or motor | |
| CN209349960U (en) | A kind of Lathe Spindle Box primary shaft belt pulley sealing structure | |
| CN102691614B (en) | Double-stator swing hydraulic multi-speed motor | |
| CN204226620U (en) | A kind of planet carrier of integrated oil path | |
| CN202251984U (en) | Gas sealing mechanism of high-speed rotating machine | |
| CN206092973U (en) | A gaseous maze throttle regulation and control mechanism of static pressure for static and dynamic pressure type dry gas is sealed | |
| CN212899889U (en) | Valve core and hydraulic valve comprising same | |
| CN210978205U (en) | Bearing with oil groove convenient for lubrication | |
| CN207673810U (en) | The harmonic speed reducer of rigid wheel with the U-shaped tooth of bicircular arcs | |
| CN202284643U (en) | Nesting-type integrated type mechanical sealing structure | |
| CN205260306U (en) | Screw vacuum pump with move seal structure | |
| CN105386972A (en) | Screw vacuum pump of motive seal structure | |
| CN203856513U (en) | Gear shunt motor and rotating seal mechanism thereof | |
| CN220646715U (en) | Sealing structure for agricultural machinery gearbox | |
| CN214742034U (en) | High-precision high-stability long-service-life ternary rotor pump device | |
| CN116447190B (en) | Hydraulic valve capable of flexibly reversing | |
| CN109605119B (en) | Lathe headstock main shaft band pulley seal structure | |
| CN205001489U (en) | Planet carrier of integrated oil circuit |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |