CN115853851B - Novel central distributing rotary reversing valve for hydrogen diaphragm compressor - Google Patents
Novel central distributing rotary reversing valve for hydrogen diaphragm compressor Download PDFInfo
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- CN115853851B CN115853851B CN202211550888.7A CN202211550888A CN115853851B CN 115853851 B CN115853851 B CN 115853851B CN 202211550888 A CN202211550888 A CN 202211550888A CN 115853851 B CN115853851 B CN 115853851B
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- 229910052739 hydrogen Inorganic materials 0.000 title claims abstract description 14
- 239000001257 hydrogen Substances 0.000 title claims abstract description 14
- 125000004435 hydrogen atom Chemical class [H]* 0.000 title claims abstract description 14
- 239000007788 liquid Substances 0.000 claims description 47
- 238000012545 processing Methods 0.000 abstract description 12
- 238000010438 heat treatment Methods 0.000 abstract description 7
- 238000012423 maintenance Methods 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 14
- 238000010586 diagram Methods 0.000 description 6
- 238000003754 machining Methods 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010892 electric spark Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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Abstract
The invention discloses a novel central flow distribution rotary reversing valve for a hydrogen diaphragm compressor, which comprises a valve body, a valve sleeve and a valve core, wherein the valve sleeve is arranged in the valve body, and the valve core is arranged in the valve sleeve; the valve sleeve is provided with a valve sleeve P flow passage and a valve sleeve T flow passage, the valve sleeve P flow passage is provided with a valve sleeve P ring groove corresponding to the valve sleeve P flow passage, and the valve sleeve T flow passage is provided with a valve sleeve T ring groove corresponding to the valve sleeve T flow passage; the valve core comprises a P channel and a T channel which are perpendicular to each other. The reversing valve structure has balanced stress, large flow gain, high reversing frequency, convenient processing and maintenance and long service life; the maximization of flow gain in zero position can be realized, energy is saved, heating is reduced, and pressure impact is reduced; the stress is balanced, the local external load of the valve sleeve is unloaded, the deformation of the part is effectively controlled, and the valve sleeve can run for a long time under high frequency and high pressure; the processing is convenient, and the precision is easy to ensure; the valve core and the valve sleeve can be taken out of the valve body independently.
Description
Technical Field
The invention relates to a rotary reversing valve, in particular to a novel central flow distribution rotary reversing valve for a hydrogen diaphragm compressor, and belongs to the technical field of hydraulic pressure.
Background
In walking hydraulic pressure and industrial hydraulic pressure, the reversing valve is a directional control valve which realizes communication, cutting off and reversing of hydraulic oil flow, pressure unloading and sequential action control by means of relative movement of a valve core and a valve body.
As the industrial hydraulic pressure increases, there is a need for high-frequency commutation of pulsating high pressure.
At present, the slide valve type reversing valve is difficult to be applied to occasions with high-frequency reversing, and the rotary reversing valve is rarely applied under the working conditions of high pulsating pressure and frequent reversing, or in the application, due to the influence of the high pulsating pressure, parts are unevenly stressed, the reliability is lower, and the service life is shorter. And secondly, the rotary reversing valve is complex in structure, high in processing difficulty, high in assembly difficulty and uncertainty, inconvenient to assemble and disassemble, and unfavorable for later maintenance. On the other hand, the working edge of the existing rotary reversing valve has limited area gradient, and the throttling and heating effects are obvious under the working condition of large flow, so that the requirements of current energy conservation and emission reduction are not met.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: the novel central flow distribution rotary reversing valve for the hydrogen diaphragm compressor solves the problems of low reliability, short service life and the like of the existing reversing valve.
The technical problems to be solved by the invention are realized by adopting the following technical scheme:
the invention provides a novel central flow distribution rotary reversing valve for a hydrogen diaphragm compressor, which comprises a valve body, a valve sleeve and a valve core, wherein,
the valve sleeve is arranged in the valve body, and the valve core is arranged in the valve sleeve;
the valve sleeve is provided with a valve sleeve P flow passage and a valve sleeve T flow passage, wherein the valve sleeve P flow passage is provided with a valve sleeve P ring groove corresponding to the valve sleeve P flow passage, and the valve sleeve T flow passage is provided with a valve sleeve T ring groove corresponding to the valve sleeve T flow passage;
the valve sleeve further comprises an A-side window, an A electrode groove corresponding to the A-side window, a B-side window and a B electrode groove corresponding to the B-side window, wherein the A-side window and the A-side electrode groove are arranged in the valve sleeve;
the valve core comprises a P channel and a T channel which are mutually perpendicular, wherein,
the P channel comprises a valve core P ring groove, and the position of the valve core P ring groove corresponds to that of a valve sleeve P ring groove of the valve sleeve;
the P channel further comprises a first P liquid passing groove and a second P liquid passing groove which are arranged on the surface of the valve core;
the T channel comprises a valve core T ring groove and a central runner hole, wherein,
the valve core T ring groove corresponds to the valve sleeve T ring groove of the valve sleeve.
As a preferable technical scheme of the invention, the T-channel further comprises a plurality of first T-channels distributed on the T-ring groove of the valve core;
the valve core is also provided with a first T-shaped liquid passing groove and a second T-shaped liquid passing groove, wherein,
the first T-shaped liquid passing groove is internally provided with a second T-shaped flow passage, and the second T-shaped liquid passing groove is internally provided with a third T-shaped flow passage.
As a preferable technical scheme of the invention, the central runner hole is a blind hole arranged in the valve core, wherein the length of the central runner hole extends to be not shorter than the third T runner;
and the opening end of the central runner hole is provided with a high-pressure plug.
As a preferable technical scheme of the invention, the valve body comprises a valve body P port, a valve body T port, a valve body A port and a valve body B port which are arranged outside the valve body, wherein,
the valve body is internally provided with a valve body P ring groove corresponding to the valve body P port, a valve body T ring groove corresponding to the valve body T port, a valve body A ring groove corresponding to the valve body A port and a valve body B ring groove corresponding to the valve body B port.
As a preferred technical scheme of the invention, the two ends of the valve sleeve are respectively provided with a first bearing hole and a second bearing hole for installing the first bearing and the second bearing, wherein,
the valve core is installed in the first bearing and the second bearing.
As a preferable technical scheme of the invention, the length and the width of the first P liquid passing groove and the second P liquid passing groove are the same as those of the electrode A groove or the electrode B groove;
the length and width of the first T-shaped liquid passing groove and the second T-shaped liquid passing groove are the same as those of the electrode A groove or the electrode B groove.
As a preferable technical scheme of the invention, the valve body is further provided with at least one first pressure relief groove and at least one second pressure relief groove.
Preferably, the valve body is provided with a first end cap and a second end cap at both ends, wherein,
a shaft seal is arranged between the first end cover and the valve core;
a first spring retainer ring is arranged between the first bearing and the second end cover,
a second spring retainer ring is arranged between the second bearing and the first end cover;
the valve body further comprises a first pressure relief channel arranged in the valve body.
Further preferably, the valve sleeve is connected with the second end cover through a fastener.
The beneficial effects of the invention are as follows: the reversing valve structure has balanced stress, large flow gain, high reversing frequency, convenient processing and maintenance and long service life; the maximization of flow gain in zero position can be realized, energy is saved, heating is reduced, and pressure impact is reduced; the stable and uniform fit clearance can be formed, the wear resistance and pollution resistance are improved, the device is suitable for higher rotating speed, and the operation reliability of the reversing valve is improved; the stress is balanced, the local external load of the valve sleeve is unloaded, the deformation of the part is effectively controlled, and the valve sleeve can run for a long time under high frequency and high pressure; the processing is convenient, and the precision is easy to ensure; the valve core and the valve sleeve can be taken out of the valve body independently.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a second schematic diagram of the structure of the present invention;
FIG. 3 is a third schematic diagram of the structure of the present invention;
FIG. 4 is a fourth schematic diagram of the structure of the present invention;
FIG. 5 is a fifth schematic diagram of the structure of the present invention;
FIG. 6 is a sixth schematic diagram of the structure of the present invention;
in the figure: 1. a first end cap; 2. a valve body; 21. a valve body P port; 211. a valve body P ring groove; 22. a valve body T port; 221. a valve body T ring groove; 23. a valve body A port; 231. a ring groove A of the valve body; 24. a valve body B port; 241. a valve body B ring groove; 25. a first pressure relief groove; 26. the second pressure relief groove; 27. a first pressure relief channel; 3. a valve sleeve; 31. a valve sleeve P flow channel; 311. a valve sleeve P ring groove; 32. a valve sleeve T flow passage; 321. a valve sleeve T ring groove; 33. a square window A; 331. an electrode groove A; 34. a B side window; 341. a B electrode groove; 4. a valve core; 41. a valve core P ring groove; 411. a first P liquid passing groove; 412. a second P liquid passing groove; 42. a valve core T ring groove; 421. a first T-channel; 422. a second T-channel; 423. a third T-channel; 431. a first T-shaped liquid passing groove; 432. a second T liquid passing groove; 44. a central flow passage hole; 5. a high-pressure plug; 6. a first bearing; 61. a first bearing hole; 7. a second end cap; 8. a fastener; 9. a first spring collar; 10. a second bearing; 101. a second bearing hole; 11. the second spring retainer ring; 12. and a shaft seal.
Detailed Description
The preferred embodiments of the present invention will be described below with reference to the accompanying drawings, it being understood that the preferred embodiments described herein are for illustration and explanation of the present invention only, and are not intended to limit the present invention.
Example 1
As shown in fig. 1-6, the embodiment provides a novel central flow distribution rotary reversing valve for a hydrogen diaphragm compressor, which comprises a valve body 2, a valve sleeve 3 and a valve core 4, wherein the valve sleeve 3 is arranged in the valve body 2, the valve core 4 is arranged in the valve sleeve 3, the special flow distribution structure of the valve sleeve 3 and the matching of the valve core 4 realize larger flow gain on the premise of realizing stress balance;
specifically, a through hole for installing the valve sleeve 3 is formed in the valve body 2, and the valve body 2 comprises a valve body P port 21, a valve body T port 22, a valve body A port 23 and a valve body B port 24 which are arranged outside the valve body 2, wherein a valve body P ring groove 211 corresponding to the valve body P port 21, a valve body T ring groove 221 corresponding to the valve body T port 22, a valve body A ring groove 231 corresponding to the valve body A port 23 and a valve body B ring groove 241 corresponding to the valve body B port 24 are arranged inside the valve body 2, so that an input and output flow channel of the valve sleeve 3 is formed together; the valve body P port 21, the valve body T port 22, the valve body A port 23 and the valve body B port 24 are connected with a hydraulic system. In another preferred embodiment of the present invention, the valve body 2 is further provided with at least one first pressure relief groove 25 and at least one second pressure relief groove 26, preferably one for each of the first pressure relief groove 25 and the second pressure relief groove 26, which serve to unload the radial pressure load at the corresponding position outside the valve sleeve 3, reduce the wear on the valve core 4, and improve the service life under high frequency and high pressure conditions.
The valve sleeve 3 is arranged in the valve body 2, and is symmetrically provided with a valve sleeve P flow channel 31 and a valve sleeve T flow channel 32, wherein the valve sleeve P flow channel 31 is provided with a valve sleeve P annular groove 311 corresponding to the valve sleeve P flow channel, the valve sleeve T flow channel 32 is provided with a valve sleeve T annular groove 321 corresponding to the valve sleeve T flow channel, and specifically, the valve sleeve P annular groove 311 corresponds to the axial position of the valve body P annular groove 211 of the valve body 2, and the valve sleeve T annular groove 321 corresponds to the axial position of the valve body T annular groove 221 of the valve body 2;
more specifically, the valve sleeve 3 further includes an a-square window 33 disposed therein, an a-electrode groove 331 corresponding to the a-square window 33, a B-square window 34, and a B-electrode groove 341 corresponding to the B-square window 34, which are symmetrically disposed, a flow channel formed by the a-square window 33 and the a-electrode groove 331 corresponds to an axial position of the valve body a-ring groove 231 of the valve body 2, a flow channel formed by the B-square window 34 and the B-electrode groove 341 corresponds to an axial position of the valve body B-ring groove 241 of the valve body 2, and the two flow channels are spatially distributed in a circumferential 90 ° staggered manner;
the valve core 4 comprises a P channel and a T channel which are mutually perpendicular and symmetrically distributed, wherein the P channel comprises a valve core P ring groove 41 and a valve sleeve P ring groove 311 (axial position) of the valve sleeve 3, the P channel further comprises a first P liquid passing groove 411 and a second P liquid passing groove 412 which are arranged on the surface of the valve core 4, and preferably, the length and the width of the first P liquid passing groove 411 and the second P liquid passing groove 412 are the same as those of the A electrode groove 331 or the B electrode groove 341; the first P liquid passing groove 411 is used for aiming at the working port A, and the second P liquid passing groove 412 is used for aiming at the working port B; the second T-channel 422 is used for the working port a, and the third T-channel 423 is used for the working port B; the first T-shaped liquid passing groove 431 is used for aiming at the working port A, and the second T-shaped liquid passing groove is used for aiming at the working port B;
t-channel, comprising a spool T-ring groove 42 and a central flow passage hole 44, wherein the spool T-ring groove 42 corresponds in position (axial position) to the valve sleeve T-ring groove 321 of the valve sleeve 3. The T channel also comprises a plurality of first T flow channels 421 distributed on the valve core T ring groove 42;
the valve core 4 is further provided with a first T-shaped liquid passing groove 431 and a second T-shaped liquid passing groove 432, wherein the first T-shaped liquid passing groove 431 is internally provided with a second T-shaped flow channel 422, the second T-shaped liquid passing groove 432 is internally provided with a third T-shaped flow channel 423, and preferably, the length and the width of the first T-shaped liquid passing groove 431 and the second T-shaped liquid passing groove 432 are the same as those of the A electrode groove 331 or the B electrode groove 341.
The central flow passage hole 44 is a blind hole formed in the valve core 4, wherein the length of the central flow passage hole 44 extends to be not shorter than the third T flow passage 423, the opening end of the central flow passage hole 44 is provided with the high-pressure plug 5, and when the valve core P ring groove 41 and the valve core T ring groove 42 are in flow distribution, under the condition of reducing flow resistance and heating, two T liquid passing grooves (a first T liquid passing groove 431 and a second T liquid passing groove 432) separated by the valve core P ring groove 41 are communicated through the valve core.
The valve housing 3 has first and second bearing holes 61 and 101 at both ends thereof for mounting the first and second bearings 6 and 10, respectively, wherein the valve core 4 is mounted in the first and second bearings 6 and 10. Specifically, when the valve sleeve 3 is installed on the valve body 2, a first end cover 1 and a second end cover 7 are installed at two ends of the valve body 2, wherein a shaft seal 12 is arranged between the first end cover 1 and the valve core 4; a first spring retainer ring 9 is arranged between the first bearing 6 and the second end cover 7, and a second spring retainer ring 11 is arranged between the second bearing 10 and the first end cover 1; the valve sleeve 3 is connected with the second end cover 7 through a fastener 8. The second bearing 10, the first bearing 6 and the valve core 4 are all arranged in the valve sleeve 3, when the reversing valve is assembled, the coaxiality of the inner circle and the outer circle of the valve sleeve 3, the coaxiality of the inner hole of the valve body 2 and the valve core of the valve sleeve and the fit clearance are not related, the interference factors of machining the fit clearance between the valve core 4 and the valve sleeve 3 are reduced, and meanwhile, the maintenance and the guarantee are more convenient. The diameter of the outer ring of the first bearing 6 is equal to the basic size of the diameter of the outer circle of the valve core 4, when the valve sleeve 3 is used for installing the bearing, a step hole is not needed to be designed again, the grinding processing of the inner hole of the valve sleeve can be realized by one-time clamping, the turning clamping is not needed, the processing difficulty is reduced, and the coaxiality of the two bearing installation holes is more easily ensured. The steps of the valve core 4 can be clamped once to realize grinding processing of the matching surfaces, so that the processing difficulty is reduced, and the coaxiality of the two bearing mounting surfaces and the matching surfaces of the valve core and the valve sleeve is ensured. The two ends of the valve core 4 are supported by bearings, under the premise that the machining precision of the valve sleeve 3 and the valve core 4 is guaranteed, the fit clearance between the valve sleeve 3 and the valve core 4 is effectively controlled, the play of the bearings is smaller than the fit clearance during design, friction-free fit of the valve core 4 and the valve sleeve 3 can be realized, the wear resistance of a key friction pair is improved, the uniformity of the clearance is guaranteed, and the service life and reliability of the whole valve are improved. The valve core 4, the second bearing 10 and the first bearing 6 are all arranged in the valve sleeve 3, so that the valve core, the second bearing 10 and the first bearing 6 can be taken as components for disassembly and assembly, when the reversing valve is installed on equipment, the valve body 2 is not required to be disassembled from the equipment, and meanwhile, the valve body 2 is not a wearing part, so that the maintenance efficiency is improved.
The valve body 2 further comprises a first pressure relief channel 27 arranged in the valve body, and the low-pressure external oil leakage can be led into the first pressure relief channel 27 of the valve body 2, so that the low-pressure unloading of the valve sleeve 3 corresponding to the outer ring is realized, and the leaked oil returns to the oil tank. The second end cap 7 is internally provided with a seal for introducing external drainage into the tank.
Specifically, when in use, an oil inlet (i.e. a valve body P port 21) on the valve body 2 and a corresponding valve body P ring groove 211 thereof, a valve sleeve P runner 31+a valve sleeve P ring groove 311 corresponding to the valve body P ring groove 211 on the valve sleeve 3, and a first P liquid passing groove 411 and a second P liquid passing groove 412 on the valve core 4 are all in a normal state, so as to jointly form an oil inlet channel P; the oil return port (namely, the valve body T port 22) on the valve body 2 and the corresponding valve body T ring groove 221 thereof, the valve sleeve T runner 32+the valve sleeve T ring groove 321 corresponding to the valve body T ring groove 221 on the valve sleeve 3, and the first T liquid passing groove 431 and the second T liquid passing groove 432 on the valve core 4 are all in a normally-open state, so that an oil return channel T is formed;
the working port A (namely, the valve body A port 23) on the valve body 2, the valve body A ring groove 231 corresponding to the valve body A port 23 and the square window 33+A electrode groove 331' on the valve sleeve 3 corresponding to the valve body A ring groove 231 are all in a normally-open state, and jointly form a working channel A; the working port B (i.e., the valve body B port 24) in the valve body 2, the valve body B ring groove 241 corresponding to the valve body B port 24, and the "B-square window 34+b electrode groove 341" in the valve housing 3 corresponding to the valve body B ring groove 241 are all in a normally open state, and together constitute the working channel B.
The valve core 4 is driven to rotate in the valve sleeve 3, and when the oil inlet channel P is communicated with the working channel A, the working channel B is communicated with the oil return channel T; conversely, when the oil inlet channel P is communicated with the working channel B, the working channel A is communicated with the oil return channel T; the width or radian of each liquid passing groove on the electrode groove 331 and the electrode groove 341 of the valve sleeve 3 and the valve core 4 is 1/8 of the part where the electrode groove is located, each time the valve core 4 rotates by 90 degrees, the reversing valve realizes one reversing, and the reversing valve belongs to a two-position four-way reversing valve in function and structure, when the valve core 4 rotates by 180 degrees, the reversing valve realizes one-cycle reversing, namely when the valve core 4 rotates by one circle, the reversing valve realizes two-cycle reversing.
The maximum utilization of the electrode grooves (the electrode groove 331A and the electrode groove 341B) and the length of the liquid passing groove in the valve sleeve 3 and the valve core 4 greatly improves the flow gain of the zero position switching position of the reversing valve, meanwhile, the P flow passage and the T flow passage of the valve sleeve 3 and the valve core 4 are both provided with annular grooves and annular hole structures, and the traditional rotary reversing valve structure is additionally provided with a throttling port, so that the scheme of the embodiment reduces throttling loss and heating. The electrode groove in the embodiment can enable the flow area of the reversing valve to be switched faster, improves the flow gain of the reversing valve, and the machining mode is preferably electric spark machining.
The valve sleeve of the traditional rotary reversing valve is internally provided with an electrode groove, meanwhile, the flow channels of P, T, A and B are of square window structures, the outside of the valve core is only provided with a liquid passing groove in the axial direction for flow distribution, and the valve core belongs to A/B and P/T simultaneous throttling, so that the flow gain is limited. In principle, the A/B and P/T can realize the reversing valve function only by one group of throttling. If P/T is the choke, A/B is the annular groove structure, traditional case structure adopts the surface to cross the cistern and join in marriage the flow, and the unnecessary additional oil return port that adds on the valve body of unnecessary, has wasted axial space, and the scheme in this embodiment adopts A/B to be the choke, and P/T is the annular groove structure, and case 4 adopts the surface to cross the cistern and join in marriage the mode that flows with the centre bore simultaneously, makes the axial space of switching-over valve obtain the maximize utilization, shortens the axial size of switching-over valve, makes valve pocket, the processing of case internal/external circle abrasive machining easier realization, axiality, cylindricity etc. easier assurance.
As another preferred embodiment of the invention, on the premise of constant rotating speed, more liquid passing grooves (even number) can be formed on the valve core 4, and meanwhile, corresponding electrode grooves are formed on the valve sleeve 3, so that higher reversing frequency can be realized, and the valve sleeve can be used for reversing occasions with more working ports.
The reversing valve in this embodiment is applied to the hydrogen diaphragm compressor, and specifically, the connection mode is a plate-type plane sealing connection mode, and the plunger pump outlet is connected to valve body P mouth, and the plunger pump oil return is connected to valve body T mouth, and two membrane heads are connected respectively to valve body a mouth and valve body B mouth, and the leakage mouth of X1 (first pressure release channel 27) and X2 in FIG. 1 is the oil tank that connects back, and main advantages that bring include: the flow gain is improved, the energy is saved, the heating is reduced, the stress is balanced, and the service life is longer.
The reversing valve structure has balanced stress, large flow gain, high reversing frequency, convenient processing and maintenance and long service life; the maximization of flow gain in zero position can be realized, energy is saved, heating is reduced, and pressure impact is reduced; the stable and uniform fit clearance can be formed, the wear resistance and pollution resistance are improved, the device is suitable for higher rotating speed, and the operation reliability of the reversing valve is improved; the stress is balanced, the local external load of the valve sleeve is unloaded, the deformation of the part is effectively controlled, and the valve sleeve can run for a long time under high frequency and high pressure; the processing is convenient, and the precision is easy to ensure; the valve core and the valve sleeve can be taken out of the valve body independently. The valve body 2, the valve sleeve 3 and the valve core 4 are of symmetrical structures, and the axial and radial stress is balanced, so that the deformation of parts under the working conditions of high pressure, pressure pulsation and the like can be effectively reduced, and the service life under the working conditions of high frequency and high pressure is prolonged.
The foregoing has shown and described the basic principles, principal features and advantages of the invention. It will be appreciated by persons skilled in the art that the present invention is not limited to the embodiments described above, but is capable of numerous variations and modifications without departing from the spirit and scope of the invention as hereinafter claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (6)
1. The novel central flow distribution rotary reversing valve for the hydrogen diaphragm compressor is characterized by comprising a valve body (2), a valve sleeve (3) and a valve core (4),
the valve sleeve (3) is arranged in the valve body (2), and the valve core (4) is arranged in the valve sleeve (3);
the valve body (2) comprises a valve body P port (21), a valve body T port (22), a valve body A port (23) and a valve body B port (24) which are arranged outside the valve body, wherein,
a valve body P ring groove (211) corresponding to the valve body P port (21), a valve body T ring groove (221) corresponding to the valve body T port (22), a valve body A ring groove (231) corresponding to the valve body A port (23) and a valve body B ring groove (241) corresponding to the valve body B port (24) are arranged in the valve body (2);
the valve body (2) is also provided with at least one first pressure relief groove (25) and at least one second pressure relief groove (26);
the valve sleeve (3) is provided with a valve sleeve P flow channel (31) and a valve sleeve T flow channel (32), wherein the valve sleeve P flow channel (31) is provided with a valve sleeve P ring groove (311) corresponding to the valve sleeve P flow channel, and the valve sleeve T flow channel (32) is provided with a valve sleeve T ring groove (321) corresponding to the valve sleeve T flow channel;
the valve sleeve (3) further comprises an A side window (33) arranged in the valve sleeve, an A electrode groove (331) corresponding to the A side window (33), a B side window (34) and a B electrode groove (341) corresponding to the B side window (34);
the valve core (4) comprises a P channel and a T channel which are mutually perpendicular, wherein,
the P channel comprises a valve core P ring groove (41) and a valve sleeve P ring groove (311) which corresponds to the valve sleeve (3) in position;
the P channel also comprises a first P liquid passing groove (411) and a second P liquid passing groove (412) which are arranged on the surface of the valve core (4);
the T channel comprises a valve core T ring groove (42) and a central runner hole (44), wherein,
the valve core T ring groove (42) corresponds to the valve sleeve T ring groove (321) of the valve sleeve (3);
the T channel further comprises a plurality of first T flow channels (421) distributed on the valve core T ring groove (42);
the valve core (4) is also provided with a first T-shaped liquid passing groove (431) and a second T-shaped liquid passing groove (432), wherein,
a second T flow channel (422) is arranged in the first T flow channel (431), and a third T flow channel (423) is arranged in the second T flow channel (432).
2. The central flow distribution rotary reversing valve for the novel hydrogen diaphragm compressor according to claim 1, wherein the central flow passage hole (44) is a blind hole formed in the valve core (4), and the length of the central flow passage hole is not shorter than that of the third T flow passage (423);
the opening end of the central runner hole (44) is provided with a high-pressure plug (5).
3. The novel hydrogen diaphragm compressor central distribution rotary reversing valve according to claim 1, wherein the two ends of the valve sleeve (3) are respectively provided with a first bearing hole (61) and a second bearing hole (101) for installing a first bearing (6) and a second bearing (10),
the valve core (4) is mounted in the first bearing (6) and the second bearing (10).
4. The novel central flow distribution rotary reversing valve for the hydrogen diaphragm compressor according to claim 1, wherein the length and the width of the first P-type liquid passing groove (411) and the second P-type liquid passing groove (412) are the same as those of the A electrode groove (331) or the B electrode groove (341);
the length and width of the first T-shaped liquid passing groove (431) and the second T-shaped liquid passing groove (432) are the same as those of the A electrode groove (331) or the B electrode groove (341).
5. A novel hydrogen diaphragm compressor center flow rotary reversing valve according to claim 3, wherein the valve body (2) is provided with a first end cover (1) and a second end cover (7) at two ends, wherein,
a shaft seal (12) is arranged between the first end cover (1) and the valve core (4);
a first spring retainer ring (9) is arranged between the first bearing (6) and the second end cover (7),
a second spring retainer ring (11) is arranged between the second bearing (10) and the first end cover (1);
the valve body (2) further comprises a first pressure relief channel (27) arranged in the valve body.
6. The novel central flow distribution rotary reversing valve for the hydrogen diaphragm compressor according to claim 5, wherein the valve sleeve (3) is connected with the second end cover (7) through a fastener (8).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211550888.7A CN115853851B (en) | 2022-12-05 | 2022-12-05 | Novel central distributing rotary reversing valve for hydrogen diaphragm compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211550888.7A CN115853851B (en) | 2022-12-05 | 2022-12-05 | Novel central distributing rotary reversing valve for hydrogen diaphragm compressor |
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| CN115853851A CN115853851A (en) | 2023-03-28 |
| CN115853851B true CN115853851B (en) | 2024-01-02 |
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| CN202211550888.7A Active CN115853851B (en) | 2022-12-05 | 2022-12-05 | Novel central distributing rotary reversing valve for hydrogen diaphragm compressor |
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|---|---|---|---|---|
| CN103075381A (en) * | 2013-01-22 | 2013-05-01 | 浙江大学 | Dual-control type four-way reversing valve |
| CN110553081A (en) * | 2019-09-29 | 2019-12-10 | 上海羿弓精密科技有限公司 | Hydraulic reversing valve and hydraulic reversing device |
| CN111963721A (en) * | 2020-09-09 | 2020-11-20 | 上海羿弓精密科技有限公司 | Fluid reversing valve and fluid reversing equipment |
| CN113153852A (en) * | 2021-03-29 | 2021-07-23 | 南京工程学院 | Direction and flow combined type high-frequency response proportional rotary valve |
| CN113483119A (en) * | 2021-06-23 | 2021-10-08 | 上海羿弓氢能科技有限公司 | Hydraulic reversing valve suitable for pulsating high-pressure and high-frequency reversing |
-
2022
- 2022-12-05 CN CN202211550888.7A patent/CN115853851B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103075381A (en) * | 2013-01-22 | 2013-05-01 | 浙江大学 | Dual-control type four-way reversing valve |
| CN110553081A (en) * | 2019-09-29 | 2019-12-10 | 上海羿弓精密科技有限公司 | Hydraulic reversing valve and hydraulic reversing device |
| CN111963721A (en) * | 2020-09-09 | 2020-11-20 | 上海羿弓精密科技有限公司 | Fluid reversing valve and fluid reversing equipment |
| CN113153852A (en) * | 2021-03-29 | 2021-07-23 | 南京工程学院 | Direction and flow combined type high-frequency response proportional rotary valve |
| CN113483119A (en) * | 2021-06-23 | 2021-10-08 | 上海羿弓氢能科技有限公司 | Hydraulic reversing valve suitable for pulsating high-pressure and high-frequency reversing |
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| CN115853851A (en) | 2023-03-28 |
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