CN216714693U - Gear pump and vehicle - Google Patents
Gear pump and vehicle Download PDFInfo
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- CN216714693U CN216714693U CN202121467127.6U CN202121467127U CN216714693U CN 216714693 U CN216714693 U CN 216714693U CN 202121467127 U CN202121467127 U CN 202121467127U CN 216714693 U CN216714693 U CN 216714693U
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- gear pump
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Abstract
The utility model discloses a gear pump and a vehicle, wherein the gear pump comprises: a housing; gear pair, gear pair sets up in the casing, and gear pair includes: the outer rotor is in transmission connection with the inner rotor, and an accommodating cavity is defined among the outer rotor, the inner rotor and the shell; the isolating ring is arranged in the accommodating cavity and positioned between the outer rotor and the inner rotor, the isolating ring is provided with an outer ring surface and an inner ring surface, at least one end of the outer ring surface is arranged in a mode of deviating relative to the circle center of the outer rotor, and/or at least one end of the inner ring surface is arranged in a mode of deviating relative to the circle center of the inner rotor. The centre of a circle of the relative outer rotor of at least one end of outer anchor ring is skew to be set up, and/or the centre of a circle of the relative inner rotor of at least one end of interior anchor ring is skew to be set up, so, have buffer distance between outer anchor ring and the outer rotor, and/or have buffer distance between interior anchor ring and the inner rotor to can avoid the irregular collision to take place between inner rotor and outer anchor ring and the interior anchor ring better, and then cause the abnormal sound.
Description
Technical Field
The utility model relates to the technical field of vehicles, in particular to a gear pump and a vehicle.
Background
In the related technology, the gear pump is provided with a pump shell, a pump cover plate and a gear pair which is meshed with the pump cover plate, namely an inner rotor and an outer rotor, an isolation ring is arranged between the inner rotor and the outer rotor, the isolation ring divides a cavity formed between the inner rotor and the outer rotor into a pressure oil cavity and an oil suction cavity, the gear pump is provided with a tubular metal sliding sleeve, and the outer diameter of the metal sliding sleeve is matched with the inner rotor and is connected with the inner rotor in a nested mode.
However, the inner ring surface of the isolation ring is concentric with the inner rotor, namely, gaps between the inner ring surface and the addendum circle of the inner rotor are the same, the outer ring surface of the isolation ring is concentric with the outer rotor, namely, gaps between the outer ring surface and the addendum circle of the outer rotor are the same, and in order to ensure the effect of the isolation ring in isolating the oil suction cavity and the oil pressing cavity, the gaps between the isolation ring and the inner rotor and the outer rotor are small, so that the inner rotor and the outer rotor are subjected to oil pressure pulsation and input excitation fluctuation in the working process to irregularly collide with the isolation ring, and abnormal sound is caused.
In addition, the contact surface of the metal sliding sleeve and the inner rotor is in sliding friction, the friction damping is large, more oil is needed for cooling and lubricating, the oil pressure between the inner rotor and the isolating ring is large when the gear pump works, the inner rotor is subjected to the pressure of the inner ring surface to increase the friction force between the inner rotor and one side of the metal sliding sleeve, the eccentric wear phenomenon is easy to occur, the mechanical efficiency of the gear pump is greatly reduced, the metal sliding sleeve is limited by the structure, the metal sliding sleeve is thin, the hardness and the rigidity are not high, the deformation is easy to occur, in the working process of the oil pump, the inner rotor is subjected to the fluctuation of oil pressure pulsation and input excitation and is influenced by the hardness and the rigidity of the metal sliding sleeve, the inner rotor can generate obvious eccentric shake, the effect that the isolating ring separates the oil suction cavity and the oil compression cavity is poor, and the volumetric efficiency of the gear pump is reduced. In order to avoid the abnormal sound caused by the collision of the eccentric shake of the inner rotor and the isolating ring, the designed gap between the inner rotor and the isolating ring is enlarged, but the volumetric efficiency of the gear pump is further reduced.
SUMMERY OF THE UTILITY MODEL
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the utility model provides a gear pump which can better avoid irregular collision between an inner rotor and an outer rotor and between an outer ring surface and an inner ring surface to cause abnormal sound.
The utility model further provides a vehicle.
The gear pump according to the present invention comprises: a housing; a gear pair, the gear pair set up in the casing, the gear pair includes: the outer rotor is in transmission connection with the inner rotor, and an accommodating cavity is defined among the outer rotor, the inner rotor and the shell; the isolation ring is arranged in the accommodating cavity and positioned between the outer rotor and the inner rotor, the isolation ring is provided with an outer ring surface and an inner ring surface, at least one end of the outer ring surface is arranged in a manner of deviating relative to the circle center of the outer rotor, and/or at least one end of the inner ring surface is arranged in a manner of deviating relative to the circle center of the inner rotor.
According to the gear pump, at least one end of the outer ring surface is arranged in a deviating mode relative to the circle center of the outer rotor, and/or at least one end of the inner ring surface is arranged in a deviating mode relative to the circle center of the inner rotor, so that a buffer distance exists between the outer ring surface and the outer rotor, and/or a buffer distance exists between the inner ring surface and the inner rotor, and therefore irregular collision between the inner rotor and the outer rotor, and between the outer ring surface and the inner ring surface can be better avoided, and abnormal sound is further caused.
In some examples of the utility model, the outer annular surface comprises: the outer eccentric section is connected to at least one end of the outer concentric section, the outer concentric section is concentrically arranged relative to the outer rotor, and the outer eccentric section is eccentrically arranged relative to the outer rotor.
In some examples of the present invention, a clearance between the outer eccentric section and the outer rotor is a, a satisfying a relation:
wherein the radius of the outer rotor is rQThe distance between the circle center of the outer eccentric section and the circle center of the outer rotor is m, the radius of the outer eccentric section is R, and the central angle of the outer eccentric section is half of that of the outer eccentric sectionIs beta.
In some examples of the utility model, a gap between the outer concentric segment and the outer rotor is b, b satisfying the relationship: b is rQ-(R+m)。
In some examples of the utility model, the inner annular surface comprises: the inner eccentric section is connected to at least one end of the inner concentric section, the inner concentric section is concentrically arranged relative to the inner rotor, and the inner eccentric section is eccentrically arranged relative to the inner rotor.
In some examples of the utility model, the gap between the inner eccentric section and the inner rotor is c, c satisfying the relation:
the radius of the inner eccentric section is r, the distance between the circle center of the inner eccentric section and the circle center of the inner rotor is n, and the radius of the inner rotor is rpAnd half of the central angle of the inner eccentric section is gamma.
In some examples of the utility model, a gap distance between the inner concentric segment and the inner rotor is d, d satisfying the relationship: d-r-n-rp。
In some examples of the utility model, the two ends of the inner annular surface are symmetrically disposed about a central axis of the inner annular surface, and/or the two ends of the outer annular surface are symmetrically disposed about a central axis of the outer annular surface.
In some examples of the utility model, the gear pump further comprises: the bearing is arranged in the shell and is nested inside the inner rotor and in rolling friction with the inner rotor.
The vehicle according to the present invention includes: the gear pump described above.
Additional aspects and advantages of the utility model will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the utility model.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a schematic diagram of a gear pump according to an embodiment of the present invention;
FIG. 2 is a partial cross-sectional view of a gear pump according to an embodiment of the present invention;
FIG. 3 is a schematic view of the spacer ring;
FIG. 4 is a schematic view of the mating of the gear pair with the spacer ring;
FIG. 5 is an enlarged view of section E of FIG. 4;
fig. 6 is a schematic view of the structure of the pump cover plate.
Reference numerals:
a gear pump 1;
a housing 10; an accommodating chamber 11; a pressure oil chamber 110; an oil suction chamber 111; a pump housing 12;
a pump cover plate 13; a coupling hole 14; a positioning hole 15; an oil sump 16; an oil outlet 17;
an oil inlet 18; an oil return port 19; a gear pair 20; an outer rotor 21; an inner rotor 22;
a spacer ring 30; an outer annular surface 31; an outer concentric segment 310; an outer eccentric section 311;
an inner annular surface 32; an inner concentric segment 320; an inner eccentric section 321; and a bearing 40.
Detailed Description
Embodiments of the present invention will be described in detail below, the embodiments described with reference to the drawings being illustrative, and the embodiments of the present invention will be described in detail below.
A gear pump 1 according to an embodiment of the present invention is described below with reference to fig. 1 to 6.
As shown in fig. 1 and 2, a gear pump 1 according to an embodiment of the present invention includes: housing 10, gear pair 20 and spacer ring 30. Set up gear pair 20 and spacer ring 30 in casing 10, casing 10 can play the effect of protection, and casing 10 also can be with gear pair 20 and spacer ring 30 with external environment isolation, avoids the work of external environment interference gear pair 20. The gear pair 20 may compress the common oil within the gear pump 1 to form high pressure oil which is then pumped out of the housing 10. The isolating ring 30 can separate the common oil from the high-pressure oil, so that the common oil and the high-pressure oil are prevented from being mixed up, and the quality of the pumped high-pressure oil is prevented from being influenced.
As shown in fig. 1, 2 and 6, the housing 10 includes: pump casing 12 and pump apron 13 all are provided with combination hole 14 and locating hole 15 on pump casing 12 and the pump apron 13, and pump casing 12 and pump apron 13 can be fixed a position through locating hole 15 earlier, then wear to establish combination hole 14 and fix together through the fastener. The pump shell 12 and the pump cover plate 13 define a cavity, and the gear pair 20 and the isolation ring 30 are arranged in the cavity, so that the isolation and protection functions can be achieved. Pump housing 12 and pump apron 13 still are provided with oil-out 17, oil inlet 18 and oil return 19, be provided with oil groove 16 on the pump apron 13, outside ordinary fluid passes through oil inlet 18 and then gathers in oil groove 16 department behind the cavity, also gather in oil groove 16 department behind the ordinary fluid conversion high pressure fluid, oil-out 17 is linked together with the oil groove 16 of high pressure fluid gathering, high pressure fluid is got rid of through oil-out 17, and oil return 19 is linked together with oil inlet 18, the part does not reach the fluid of high pressure fluid standard and flows back to oil inlet 18 again through oil return 19, can avoid the waste of fluid like this, also can promote the quality of high pressure fluid.
As shown in fig. 1 and 2, the gear pair 20 includes: the outer rotor 21 and the inner rotor 22 are in transmission connection, the outer rotor 21 and the inner rotor 22 can be external gears, the inner rotor 22 can be internal gears, the external gears are meshed with the internal gears, when the internal gears rotate, the internal gears can drive the external gears to rotate, and the common oil is extruded through transmission between the external gears and the internal gears, so that high-pressure oil is formed and then pumped out of the shell 10. In addition, an accommodating cavity 11 is defined between the outer rotor 21, the inner rotor 22 and the housing 10, the accommodating cavity 11 can accommodate common oil and high-pressure oil, and of course, the accommodating cavity 11 is communicated with the outside through the oil outlet 17 and the oil inlet 18.
As shown in fig. 1 and 2, the isolating ring 30 is disposed in the accommodating cavity 11, and the isolating ring 30 is located between the outer rotor 21 and the inner rotor 22, so that the accommodating cavity 11 can be divided into an oil suction cavity 111 and a pressure oil cavity 110 by the isolating ring 30, external common oil is introduced into the oil suction cavity 111, the common oil is extruded to form high-pressure oil and then is stored in the pressure oil cavity 110, and then is discharged to the outside of the housing 10 through the pressure oil cavity 110, thereby preventing the common oil and the high-pressure oil from being mixed up with each other and affecting the quality of the pumped high-pressure oil.
It should be noted that, when the inner rotor 22 and the outer rotor 21 are subjected to oil pressure pulsation and input excitation fluctuation during transmission, the inner rotor 22 and the outer rotor 21 move toward one end of the outer annular surface 31 and one end of the inner annular surface 32, so that irregular collision occurs between the inner rotor 22 and the outer rotor 21 and the outer annular surface 31 and the inner annular surface 32, and then abnormal noise is caused.
As shown in fig. 1 to 4, the spacer ring 30 has an outer annular surface 31 and an inner annular surface 32, at least one end of the outer annular surface 31 is disposed offset with respect to the center of the outer rotor 21, and/or at least one end of the inner annular surface 32 is disposed offset with respect to the center of the inner rotor 22. That is, at least one end of the outer annular surface 31 is spaced apart from the outer rotor 21, and/or at least one end of the inner annular surface 32 is spaced apart from the inner rotor 22. Therefore, the outer ring surface 31 and the outer rotor 21 have a buffer distance therebetween, and/or the inner ring surface 32 and the inner rotor 22 have a buffer distance therebetween, so that irregular collision between the inner rotor 22 and the outer rotor 21 and between the outer ring surface 31 and the inner ring surface 32 can be better avoided, and then abnormal noise is caused.
As shown in fig. 3 and 4, the outer annular surface 31 includes: an outer concentric segment 310 and an outer eccentric segment 311, the outer eccentric segment 311 being connected to at least one end of the outer concentric segment 310, the outer concentric segment 310 being concentrically arranged with respect to the outer rotor 21, the outer eccentric segment 311 being eccentrically arranged with respect to the outer rotor 21. Outer eccentric section 311 is connected in the at least one end of outer concentric segment 310, and outer eccentric section 311 is eccentric settings relative outer rotor 21 in addition, and it has the distance to have the interval between outer eccentric section 311 and the outer rotor 21 like this, avoids taking place irregular collision between outer rotor 21 and the outer eccentric section 311 better, and then causes the abnormal sound. The outer concentric segment 310 is in clearance fit with the outer rotor 21, and the outer concentric segment 310 is concentrically arranged relative to the outer rotor 21, so that the arc structures of the outer concentric segment 310 and the outer rotor 21 are the same, and the fit effect between the outer concentric segment 310 and the outer rotor 21 is better.
In particular, as shown in fig. 4 and the drawingsAs shown in fig. 5, the clearance between the outer eccentric section 311 and the outer rotor 21 is a, and a satisfies the relation:
wherein the outer rotor 21 has a radius rQThe distance between the center of the outer eccentric section 311 and the center of the outer rotor 21 is m, the radius of the outer eccentric section 311 is R, and half of the central angle of the outer eccentric section 311 is β. As can be seen, the center of the outer eccentric section 311 is a, the center of the outer rotor 21 is B, and the distance between a and B is m, which can be obtained by the cosine theorem:
on the premise of ensuring that the isolating ring 30 can normally work, the larger the gap between the outer eccentric section 311 and the outer rotor 21 is, the better the effect of avoiding irregular collision between the outer rotor 21 and the outer eccentric section 311 is.
As shown in fig. 5, the clearance between the outer concentric segment 310 and the outer rotor 21 is b, and b satisfies the relation: b is rQ- (R + m). As can be seen, the clearance between the outer concentric segment 310 and the outer rotor 21 is: b is rQ- (R + m), the smaller the gap between the outer concentric section 310 and the outer rotor 21 is, the better the sealing effect between the outer concentric section 310 and the outer rotor 21 is, preferably, b is 0, that is, the outer concentric section 310 and the outer rotor 21 are in a close fit state, so that the sealing performance between the outer concentric section 310 and the outer rotor 21 is better, and the problem that the quality of the pumped high-pressure oil is affected due to the mutual confusion between the common oil and the high-pressure oil is avoided.
According to an alternative embodiment of the present invention, as shown in fig. 3 and 4, the inner annular surface 32 comprises: an inner concentric segment 320 and an inner eccentric segment 321, the inner eccentric segment 321 being connected to at least one end of the inner concentric segment 320, the inner concentric segment 320 being concentrically arranged with respect to the inner rotor 22, the inner eccentric segment 321 being eccentrically arranged with respect to the inner rotor 22. In a similar way, the inner eccentric section 321 is connected to at least one end of the inner concentric section 320, and the inner eccentric section 321 is eccentrically arranged relative to the inner rotor 22, so that a distance is reserved between the inner eccentric section 321 and the inner rotor 22, and irregular collision between the inner rotor 22 and the inner eccentric section 321 is better avoided, thereby causing abnormal noise. The inner concentric segment 320 is in clearance fit with the inner rotor 22, and the inner concentric segment 320 is concentrically arranged relative to the inner rotor 22, so that the inner concentric segment 320 and the inner rotor 22 have the same arc structure, and the fit between the inner concentric segment 320 and the inner rotor 22 is better.
Specifically, as shown in fig. 4 and 5, the gap between the inner eccentric section 321 and the inner rotor 22 is c, and c satisfies the relation:
wherein, the radius of the inner eccentric section 321 is r, the distance between the center of the inner eccentric section 321 and the center of the inner rotor 22 is n, and the radius of the inner rotor 22 is rpThe inner eccentric section 321 has a central angle of one half γ. As can be seen from the figure, the center of the inner eccentric section 321 is D, the center of the inner rotor 22 is C, and the distance between D and C is n, which can be obtained by the cosine law:
on the premise of ensuring that the isolating ring 30 can normally work, the larger the gap between the inner eccentric section 321 and the inner rotor 22 is, the better the effect of avoiding the irregular collision between the inner rotor 22 and the inner eccentric section 321 is.
Further, as shown in fig. 5, the gap distance between the inner concentric segment 320 and the inner rotor 22 is d, which satisfies the relationship: d-r-n-rp. In summary, the gap between the inner concentric segment 320 and the inner rotor 22 is: d-r-n-rpThe smaller the gap between the inner concentric segment 320 and the inner rotor 22 is, the better the sealing effect between the inner concentric segment 320 and the inner rotor 22 is, preferably, d is 0, that is, the inner concentric segment 320 and the inner rotor 22 are in a close fit state, so that the sealing performance between the inner concentric segment 320 and the inner rotor 22 is better, and the common oil and the high-pressure oil are prevented from being mixed up to affect the quality of the pumped high-pressure oil.
In addition, as shown in fig. 1-4, the two ends of the inner annular surface 32 are symmetrically disposed about the central axis of the inner annular surface 32, and/or the two ends of the outer annular surface 31 are symmetrically disposed about the central axis of the outer annular surface 31. So as to arrange. The two ends of the inner annular surface 32 and/or the outer annular surface 31 may have the same structure, the inner eccentric section 321 is connected to at least one end of the inner concentric section 320, and the outer eccentric section 311 is connected to at least one end of the outer concentric section 310, so that the two ends of the inner annular surface 32 and/or the outer annular surface 31 are both provided with the inner eccentric section 321 and/or the outer eccentric section 311, and thus irregular collision between the inner rotor 22 and the outer rotor 21 and between the outer annular surface 31 and the inner annular surface 32, which may cause abnormal noise, can be better avoided in both the oil suction chamber 111 and the oil pressing chamber 110.
Alternatively, as shown in fig. 1 and 2, the gear pump 1 further includes: the bearing 40, the bearing 40 is disposed in the housing 10, the bearing 40 is nested inside the inner rotor 22, and the bearing 40 and the inner rotor 22 are in rolling friction. The bearing 40 is disposed in the housing 10, and the bearing 40 is nested inside the inner rotor 22, and the bearing 40 can support the inner rotor 22. Rolling friction is formed between the inner rotor 22 and the bearing 40, the friction coefficient of the rolling friction is low, and the eccentric wear phenomenon between the inner rotor 22 and the bearing 40 can be avoided, so that the inner rotor 22 and the bearing 40 are easily damaged, and the mechanical efficiency of the gear pump 1 is reduced. And the bearing 40 has higher hardness and rigidity, so that the bearing 40 is not easy to deform, and the running stability of the inner rotor 22 can be ensured after the bearing 40 is nested in the inner side of the inner rotor 22. In addition, when the inner rotor 22 is subjected to oil pressure pulsation and input excitation fluctuation, the inner rotor 22 can be prevented from generating obvious eccentric shaking, so that the collision between the inner rotor 22 and the inner annular surface 32 is improved, meanwhile, the sealing performance between the inner rotor 22 and the inner annular surface 32 can be improved, and the mechanical efficiency and the volumetric efficiency of the gear pump 1 are obviously improved.
A vehicle according to an embodiment of the present invention includes: gear pump 1 as described in the previous embodiments.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the utility model and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the utility model.
In the description of the present invention, "the first feature" and "the second feature" may include one or more of the features. In the description of the present invention, "a plurality" means two or more. In the description of the present invention, the first feature being "on" or "under" the second feature may include the first and second features being in direct contact, and may also include the first and second features being in contact with each other not directly but through another feature therebetween. In the description of the utility model, "above", "over" and "above" a first feature in a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is higher in level than the second feature.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example.
While embodiments of the utility model have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the utility model, the scope of which is defined by the claims and their equivalents.
Claims (10)
1. A gear pump, comprising:
a housing;
a gear pair, the gear pair set up in the casing, the gear pair includes: the outer rotor is in transmission connection with the inner rotor, and an accommodating cavity is defined among the outer rotor, the inner rotor and the shell;
the isolation ring is arranged in the accommodating cavity and positioned between the outer rotor and the inner rotor, the isolation ring is provided with an outer ring surface and an inner ring surface, at least one end of the outer ring surface is arranged in a manner of deviating relative to the circle center of the outer rotor, and/or at least one end of the inner ring surface is arranged in a manner of deviating relative to the circle center of the inner rotor.
2. The gear pump of claim 1, wherein the outer annular surface comprises: the outer eccentric section is connected to at least one end of the outer concentric section, the outer concentric section is concentrically arranged relative to the outer rotor, and the outer eccentric section is eccentrically arranged relative to the outer rotor.
3. The gear pump of claim 2, wherein the clearance between the outer eccentric section and the outer rotor is a, a satisfying the relationship:
wherein the radius of the outer rotor is rQThe distance between the circle center of the outer eccentric section and the circle center of the outer rotor is m, the radius of the outer eccentric section is R, and half of the central angle of the outer eccentric section is beta.
4. The gear pump of claim 3, wherein the gap between the outer concentric segment and the outer rotor is b, b satisfying the relationship: b is rQ-(R+m)。
5. The gear pump of claim 1, wherein the inner annular surface comprises: the inner eccentric section is connected to at least one end of the inner concentric section, the inner concentric section is concentrically arranged relative to the inner rotor, and the inner eccentric section is eccentrically arranged relative to the inner rotor.
6. The gear pump of claim 5, wherein a gap between the inner eccentric section and the inner rotor is c, c satisfying the relationship:
the radius of the inner eccentric section is r, the distance between the circle center of the inner eccentric section and the circle center of the inner rotor is n, and the radius of the inner rotor is rpAnd half of the central angle of the inner eccentric section is gamma.
7. The gear pump of claim 6, wherein a gap distance between the inner concentric section and the inner rotor is d, d satisfying the relationship: d-r-n-rp。
8. The gear pump of claim 1, wherein the ends of the inner annular surface are symmetrically disposed about the central axis of the inner annular surface and/or the ends of the outer annular surface are symmetrically disposed about the central axis of the outer annular surface.
9. The gear pump of claim 1, further comprising: the bearing is arranged in the shell and is nested inside the inner rotor and in rolling friction with the inner rotor.
10. A vehicle, characterized by comprising: the gear pump of any one of claims 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121467127.6U CN216714693U (en) | 2021-06-29 | 2021-06-29 | Gear pump and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121467127.6U CN216714693U (en) | 2021-06-29 | 2021-06-29 | Gear pump and vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216714693U true CN216714693U (en) | 2022-06-10 |
Family
ID=81871170
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202121467127.6U Active CN216714693U (en) | 2021-06-29 | 2021-06-29 | Gear pump and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216714693U (en) |
-
2021
- 2021-06-29 CN CN202121467127.6U patent/CN216714693U/en active Active
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