Electronic medium pump and vehicle
By installing a stop ring between the impeller and the volute, the problem of medium backflow in the medium pump is solved, which improves efficiency, reduces noise, extends service life, and reduces production costs.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- MIND ELECTRONICS APPLIANCE CO LTD
- Filing Date
- 2025-06-16
- Publication Date
- 2026-06-12
AI Technical Summary
The assembly gap between the impeller and the volute in existing electronic media pumps causes media backflow, resulting in flow loss and reduced efficiency. At the same time, the use of wear-resistant pads and rubber sleeves increases costs and wear, affecting service life and noise.
A stop ring is installed between the impeller and the volute. The stop ring moves axially and radially within the backflow gap to form a small radial overflow gap to reduce medium backflow. The medium backflow is used to form a lubricating film to reduce friction. Combined with a simple structure, this reduces costs.
It significantly reduces media backflow, improves the working efficiency of electronic media pumps by 8%-12%, reduces noise, extends service life, and reduces production costs by 90%.
Smart Images
Figure CN224352105U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of electronic medium pump technology, and in particular to an electronic medium pump and a vehicle. Background Technology
[0002] An electronic medium pump is assembled from a volute, pump body, stator assembly, rotor assembly, impeller, etc. During the assembly process, in order to prevent friction between the impeller and the volute, a certain clearance needs to be set between them. However, the clearance will cause the medium to flow back through the clearance during the operation of the electronic medium pump, resulting in flow loss and reducing the working efficiency of the electronic medium pump. Utility Model Content
[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, one objective of the present invention is to provide an electronic medium pump that has lower flow loss, higher efficiency, lower cost, longer service life, and lower operating noise.
[0004] In a first aspect, this application proposes an electronic medium pump, comprising: a volute, an impeller, and a stop ring. The volute includes: a cover and an inlet pipe. The cover has a first side and a second side. The inlet pipe is located on the first side and includes at least a first pipe section and a second pipe section. The inner diameter of the second pipe section is smaller than the inner diameter of the first pipe section. The impeller includes an impeller body and a mating protrusion protruding from the impeller body. A first reflux gap is formed between the impeller body and the second side. A second reflux gap is formed between the mating protrusion and the second pipe section. The second reflux gap communicates with the first reflux gap. The stop ring is sleeved on the mating protrusion. The inner diameter of the stop ring is larger than the outer diameter of the mating protrusion to form a first overflow gap between the mating protrusion and the inner wall of the stop ring. The stop ring floats axially within the second reflux gap. The stop ring is adapted to push against one end face of the second pipe section facing the first pipe section and overflow through the first overflow gap.
[0005] According to the embodiment of the present application, an electronic medium pump is provided with a stop ring in the second backflow gap between the first pipe section and the mating protrusion. The stop ring can move radially and axially within the second backflow gap. The smaller first overflow gap can reduce the backflow of medium, thereby improving the hydraulic performance of the electronic medium pump. The small backflow of medium can be used for lubrication and vibration reduction, reducing the friction between the stop ring and the impeller, thereby reducing operating noise, extending service life, and improving operational reliability. At the same time, the simple structure of the stop ring can also reduce the production cost of the electronic medium pump.
[0006] According to some embodiments of this application, a first annular boss is provided on one end face of the second pipe segment facing the first pipe segment, and the stop ring is adapted to push against the first annular boss.
[0007] According to some embodiments of this application, the flatness of the first annular boss is less than or equal to 0.1 mm, and the surface roughness is less than or equal to 0.8 μm.
[0008] According to some embodiments of this application, the side wall of the first annular boss away from the mating protrusion is spaced apart from the inner wall of the first pipe section to form a receiving groove for accommodating foreign objects in the medium.
[0009] According to some embodiments of this application, the mating protrusion has an impeller inlet, the impeller body has an impeller outlet, and the inlet pipe further includes a third pipe section located at the end of the second pipe section away from the first pipe section. The inner diameter of the third pipe section is equal to the inner diameter of the impeller inlet and smaller than the inner diameter of the second pipe section.
[0010] According to some embodiments of this application, a second annular boss is formed on the outer wall surface of the mating protrusion, and the stop ring is located between the second annular boss and the first annular boss.
[0011] According to some embodiments of this application, the radial width of the second annular boss is 0.5mm-0.8mm.
[0012] According to some embodiments of this application, a mating section is further formed on the outer wall surface of the mating protrusion. The mating section is located on the side of the second annular protrusion away from the impeller body, and a first overflow gap is formed between the mating section and the stop ring.
[0013] According to some embodiments of this application, the size of the first overflow gap is 0.045mm-0.065mm.
[0014] According to some embodiments of this application, a second overflow gap is formed between the second pipe section and the mating section, and the second overflow gap communicates with the first overflow gap.
[0015] According to some embodiments of this application, the size of the second overflow gap is 0.45mm-0.65mm.
[0016] According to some embodiments of this application, the stop ring has an axial dimension of less than or equal to 0.4 mm, a radial width of 1.4 mm to 1.6 mm, a yield strength of greater than or equal to 420 MPa, and a weight of less than or equal to 0.4 g.
[0017] Secondly, this application proposes a vehicle comprising: the electronic medium pump described in the above embodiments.
[0018] Additional aspects and advantages of this invention 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 invention. Attached Figure Description
[0019] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:
[0020] Figure 1 This is a schematic diagram of an electronic medium pump according to an embodiment of this application;
[0021] Figure 2 This is a cross-sectional schematic diagram of an electronic medium pump according to an embodiment of this application;
[0022] Figure 3 This is a schematic diagram of a vortex shell according to the first embodiment of this application;
[0023] Figure 4 This is a schematic diagram of a vortex shell according to the second embodiment of this application;
[0024] Figure 5 This is a schematic diagram of an impeller according to an embodiment of this application;
[0025] Figure 6 This is a cross-sectional schematic diagram of an impeller according to an embodiment of this application;
[0026] Figure 7 This is a schematic diagram of a stop ring according to an embodiment of this application;
[0027] Figure 8 This is a cross-sectional schematic diagram of a stop ring according to an embodiment of this application;
[0028] Figure 9 This is a partially enlarged cross-sectional view of an electronic media pump according to an embodiment of this application;
[0029] Figure 10 This is a schematic diagram of the media flow path of an electronic media pump according to an embodiment of this application;
[0030] Figures 11 to 13 This is a schematic diagram showing the movement of the stop ring and the flow of the medium during the start-up process of an electronic medium pump.
[0031] Figure label:
[0032] Electro-medium pump 100,
[0033] 10 volute casing, 11 cover, 111 first side surface, 112 second side surface, 12 inlet pipe, 121 first pipe section, 122 second pipe section, 1221 first annular boss, 1222 receiving groove, 123 third pipe section.
[0034] Impeller 20, impeller body 21, impeller outlet 211, mating protrusion 22, impeller inlet 221, second annular protrusion 222, mating section 223
[0035] 30 stop ring,
[0036] First reflux gap a, second reflux gap b, first overflow gap c, second overflow gap d,
[0037] The dimensions of the first overflow gap are L1, the second overflow gap are L2, the axial dimension of the stop ring is L3, and the radial width of the stop ring is L4. Detailed Implementation
[0038] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.
[0039] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.
[0040] In this application, the reference to "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments.
[0041] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.
[0042] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.
[0043] In the embodiments of this application, the same reference numerals denote the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, width, and other dimensions of various components in the embodiments of this application shown in the accompanying drawings, as well as the overall thickness, length, width, and other dimensions of the integrated device, are merely illustrative and should not constitute any limitation on this application.
[0044] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.
[0045] In the description of this utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.
[0046] In the description of this utility model, the terms "above", "over" and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.
[0047] In this application, "multiple" means two or more (including two).
[0048] During the operation of the electronic medium pump, the medium enters the volute through the inlet pipe and then enters the impeller through the impeller inlet. The impeller rotates and pumps the medium out through the impeller outlet to the volute outlet pipe.
[0049] To avoid friction between the impeller and the volute during rotation, an assembly gap needs to be set between the impeller and the volute. However, during the operation of the electronic medium pump, the medium will flow back to the inlet pipe side through the assembly gap, resulting in flow loss (i.e., volume loss). The greater the pressure difference between the impeller's inlet and outlet, the greater the leakage backflow.
[0050] In the prior art, in order to reduce the backflow of media caused by the assembly gap between the volute and the impeller, the assembly gap needs to be minimized. However, if the assembly gap is too small, it will increase the probability of friction between the volute and the impeller, resulting in limited adjustment effect of the assembly gap. By pressing a rubber sleeve and a wear-resistant pad into the assembly gap between the impeller and the volute to seal the assembly gap, the backflow of media can be effectively improved.
[0051] In other words, a wear-resistant pad wrapped with a rubber sleeve is press-fitted into the inner cavity of the volute. During the operation of the electronic medium pump, the top of the impeller contacts the bottom surface of the wear-resistant ceramic pad and generates relative friction. The impeller is further pushed against the wear-resistant ceramic pad under the axial force to effectively prevent the medium from flowing back.
[0052] However, the impeller and wear pad wear over a long period of time, requiring sufficient lubrication and cooling. Impeller wear affects the working performance and reduces the service life of the electronic medium pump, especially when used in high-power electronic medium pumps (power exceeding 150W). When the impeller is in high-speed rotation, the wear of the impeller will be further aggravated, and the working performance and service life will be significantly reduced. At the same time, the contact surface diameter between the impeller and the wear pad is relatively large, making it difficult to ensure a perfect fit. The contact surface is prone to tilting, resulting in uneven axial force on the impeller, unbalanced rotation, and vibration noise, which affects the user experience. In addition, the cost of using the wear pad and rubber sleeve to seal the installation gap is relatively high.
[0053] Based on this, this application proposes an electronic medium pump that, by setting a stop ring, can not only reduce the backflow of the medium and reduce volumetric loss, but also has low cost and higher reliability and stability.
[0054] The following is for reference. Figures 1-13 This invention describes an electronic medium pump 100 and a vehicle according to an embodiment of the present invention.
[0055] like Figure 1 and Figure 2 As shown, this application proposes an electronic medium pump 100, including: a volute 10, an impeller 20, and a stop ring 30.
[0056] Among them, combined Figure 2 , Figure 9 and Figure 10 As shown, the vortex housing 10 includes: a cover 11 and an inlet pipe 12 (the inlet pipe 12 is integrally formed on the cover 11). The cover 11 has a first side 111 and a second side 112. The inlet pipe 12 is located on the first side 111. The inlet pipe 12 includes at least a first pipe section 121 and a second pipe section 122. The inner diameter of the second pipe section 122 is smaller than the inner diameter of the first pipe section 121. The impeller 20 includes an impeller body 21 and a mating protrusion 22 protruding from the impeller body 21. A first reflux gap a is formed between the impeller body 21 and the second side 112. A second reflux gap b is formed between the mating protrusion 22 and the second pipe section 122. The second reflux gap b communicates with the first reflux gap a.
[0057] Specifically, the axial sides of the cover 11 are a first side 111 and a second side 112, respectively. The first side 111 is provided with an inlet pipe 12 and an outlet pipe. The inlet pipe 12 is located in the axial direction of the cover 11, and the outlet pipe is located in the radial direction of the cover 11. The medium is suitable to enter through the inlet pipe 12, and after passing through the impeller inlet 221 and the impeller outlet 211 of the impeller 20, it flows out through the impeller outlet 211.
[0058] A reflux channel is formed between the first reflux gap a and the second reflux gap b. Some of the medium flowing out of the impeller outlet 211 may flow through the first reflux gap a and the second reflux gap b in sequence and flow back to the inlet pipe 12, resulting in hydraulic loss and reducing the working efficiency of the electronic medium pump 100.
[0059] Based on this, this application further provides a stop ring 30 in the second return gap b between the impeller 20 and the volute 10. The stop ring 30 is sleeved on the mating protrusion 22. The inner diameter of the stop ring 30 is larger than the outer diameter of the mating protrusion 22, so as to form a first overflow gap c between the mating protrusion 22 and the inner wall of the stop ring 30. The stop ring 30 floats axially in the second return gap b. The stop ring 30 is adapted to push against the end face of the second pipe section 122 facing the first pipe section 121 and overflow through the first overflow gap c.
[0060] In other words, the stop ring 30 is located in the second backflow gap b formed between the first pipe section 121 of the inlet pipe 12 and the mating protrusion 22 of the impeller 20, and the stop ring 30 is adapted to move axially to push against the end face of the second pipe section 122 facing the first pipe section 121 to block the second backflow gap b, thereby reducing backflow. The first overflow gap c between the stop ring 30 and the mating protrusion 22 can realize the backflow of at least part of the medium.
[0061] It is understandable that the medium pressure at the impeller outlet 211 is greater than the medium pressure at the impeller inlet 221, such as... Figure 9 and Figure 10 As shown, when the medium flows along the first return gap a and the second return gap b, the pressure will exhibit a gradient decay change, and the kinetic energy of the medium will gradually increase. This becomes the driving force that drives the stop ring 30 to overcome its own gravity and push against the end face of the second pipe section 122 facing the first pipe section 121. This generates the basic condition that the stop ring 30 can move in position and ensure contact with the end face of the second pipe section 122 facing the first pipe section 121 on the volute 10: that is, in any state, the pressure on the lower axial end face of the stop ring 30 is always greater than the pressure on the upper axial end face.
[0062] It should be noted that during the operation of the electronic medium pump 100, the stop ring 30 is... Figure 11 The first state shown, first move to Figure 12 The second state is shown, and it eventually stabilizes in the third state. After the electronic medium pump 100 is turned off, the stop ring 30 gradually moves back to the first state under its own gravity.
[0063] The first state is as follows: Figure 11 The image shows a partial view of the electronic medium pump 100 after assembly or in a non-working state. At this time, the lower end face of the stop ring 30 is located on the second annular boss 222 on the mating protrusion 22. When the electronic medium pump 100 is first turned on, the state of medium backflow is indicated by the directions of the multiple small arrows. The stop ring 30 can gradually move away from the second annular boss 222 under the pressure of the medium.
[0064] Second state: such as Figure 12 As shown, this is a partial view of the electronic medium pump 100 when it starts working. Due to the impact of the high-speed backflow of the medium and the medium pressure difference between the upper and lower end faces of the stop ring 30, the lower end face of the stop ring 30 is separated from the second annular boss 222 and moves toward the second pipe section 122. At this time, a small amount of medium flows back to the impeller inlet 221 of the impeller 20 through the second backflow gap b and the first overflow gap c.
[0065] Third state: such as Figure 13 As shown, this is a partial view of the electronic medium pump 100 when it is operating stably. The upper end face of the stop ring 30 finally contacts the end face of the second pipe section 122 facing the first pipe section 121 and remains stable. The main channel for medium return (i.e., the second return gap b) is cut off. At this time, the pressure difference between the upper and lower end faces of the stop ring 30 reaches its maximum, and the first overflow gap c becomes the only channel for medium return, controlling the return direction and return flow of the medium. Therefore, the medium return loss is minimized at this time, effectively reducing the return flow of the medium, reducing flow loss, and improving the working efficiency of the electronic medium pump 100.
[0066] The stop ring 30 can move freely axially and radially within the second overflow gap d. When the electronic medium pump 100 is working, the stop ring 30 moves axially due to the impact of the high-speed backflow of liquid and the liquid pressure difference between the upper and lower end faces. Finally, the upper end face of the stop ring 30 contacts the end face of the second pipe section 122 facing the first pipe section 121, thereby cutting off the "main backflow channel" of the medium and greatly reducing liquid backflow. At this time, the liquid pressure difference or potential energy difference between the upper and lower end faces of the stop ring 30 reaches its maximum, ensuring that the stop ring 30 is stably and reliably pushed against the end face of the second pipe section 122 facing the first pipe section 121 without detachment. This can greatly reduce flow loss, improve the pump head efficiency of the electronic medium pump 100 by 8%-12%, and effectively reduce the power consumption of the electronic medium pump 100. At the same time, the reduction in liquid leakage in this scheme is also conducive to reducing the impact of local liquid and water resistance friction in the volute 10, thereby reducing the liquid noise of the electronic water pump, especially under high flow conditions.
[0067] Furthermore, since the radial dimension of the mating clearance between the convex part 22 and the stop ring 30 is small (i.e., the first overflow clearance c), when the impeller 20 rotates at high speed, it inevitably generates high-frequency friction and collision with the stop ring 30. However, during the process of a small amount of high-pressure medium flowing back to the impeller inlet 221 through the first overflow clearance c, a lubricating film can be formed in the first overflow clearance c, which can play a lubricating role and a flow resistance and vibration reduction role. The medium pressure on the stop ring 30 in the radial direction is in a balanced state, which can realize free radial movement. Its own mass is small, and the radial contact area with the impeller 20 is also small. The rebound effect of the collision with the impeller 20 is weak. For the electronic medium pump 100 as a whole, the adverse effects can be ignored.
[0068] In other words, the setting of the stop ring 30 can improve the hydraulic performance of the electronic medium pump 100. When the electronic medium pump 100 is working, due to the presence of the stop ring 30, the medium return flow rate of the return flow channel between the volute 10 and the impeller 20 is limited by the stop ring 30. That is, the amount of medium return or leakage inside the electronic medium pump 100 depends on the size of the minimum gap of the flow channel. The radial dimension of the first overflow gap c is about one-tenth of the second return gap b. Therefore, the medium return flow rate is greatly reduced and the flow loss is significantly reduced. The pump head efficiency of the electronic medium pump 100 can be improved by 8%-12% according to simulation calculation. Actual tests show that the efficiency improvement is basically similar compared with the effect of the thrust assembly with wear-resistant pad and rubber sleeve in the prior art.
[0069] At the same time, it can also reduce the operating noise of the electronic medium pump 100. The significant reduction in the internal flow loss of the electronic medium pump 100 will reduce the impact force of the medium in the return channel (defined by the first return gap a and the second return gap b) between the impeller 20 and the volute 10, and reduce the hydraulic friction generated by the medium. The resulting medium noise is greatly reduced, especially under high flow conditions. The operating noise is significantly reduced, and the water sound is even smaller when perceived by the human ear at close range. The risk of generating vibration noise is far lower than that of the thrust structure of the wear-resistant pad and rubber sleeve in the existing technology. The effect is even more obvious under no-load conditions.
[0070] Of course, it can also reduce the cost of the electronic medium pump 100. The stop ring 30 has a simple structure, small thickness, and low weight, making it suitable for die stamping. Its dimensional accuracy is easy to guarantee, and its bulk purchase cost is low. Compared with the thrust assembly structure of the existing technology, the cost can be reduced by 90%.
[0071] The electronic medium pump 100 of this application embodiment is also more reliable. When the stop ring 30 is forgotten to be installed, the electronic medium pump 100 can still work stably. After the stop ring 30 is added, the electronic medium pump 100 can perform high-efficiency, low-energy consumption and low-noise operation. Even if the stop ring 30 is missing, it will not affect the normal operation of the electronic medium pump 100. In the prior art, if the thrust assembly is missing, the electronic medium pump 100 will malfunction, causing serious wear and failure.
[0072] In summary, the electronic medium pump 100 of this application embodiment has less internal flow loss, which can improve the efficiency of the electronic medium pump 100 by 8%-12%. The stop ring 30 can cut off the main leakage backflow path of the medium, which greatly reduces the medium flow rate and the medium pressure difference. The working noise caused by medium backflow friction and impact is also relatively reduced. At the same time, the stop ring 30 has a simple structure, small thickness and low weight, is suitable for die stamping, and the dimensional accuracy is easy to guarantee. The bulk purchase cost is low.
[0073] According to the embodiment of the present application, the electronic medium pump 100 has a stop ring 30 provided in the second backflow gap b between the first pipe section 121 and the mating protrusion 22. The stop ring 30 can move radially and axially within the second backflow gap b. The smaller first overflow gap c can reduce the backflow of the medium, thereby improving the hydraulic performance of the electronic medium pump 100. The small flow of backflow of the medium can be used to form a lubricating film in the first overflow gap c for lubrication and vibration reduction. This can reduce the friction between the stop ring 30 and the impeller 20, thereby reducing operating noise, extending the service life of the pump body, and improving operational reliability. At the same time, the simple structure of the stop ring 30 can also reduce the production cost of the electronic medium pump 100.
[0074] like Figure 4As shown, according to some embodiments of this application, a first annular boss 1221 is provided on one end face of the second pipe section 122 facing the first pipe section 121, and the stop ring 30 is adapted to push against the first annular boss 1221.
[0075] In this way, by setting the first annular boss 1221, while achieving the above-mentioned technical effects, the contact area between the stop ring 30 and the first annular boss 1221 is smaller, the friction of the stop ring 30 is less, which can extend the service life of the stop ring 30 and improve the reliability and stability of the stop ring 30 in suppressing backflow.
[0076] Of course, the structure of the vortex shell 10 in this embodiment is not limited to this. In other embodiments, such as... Figure 3 As shown, the first annular boss 1221 may not be provided on the end face of the second pipe section 122 facing the first pipe section 121. The stop ring 30 can directly push against the end face of the second pipe section 122 facing the first pipe section 121 to achieve the same technical effect. Moreover, the internal cavity structure of the vortex shell 10 is simpler, which can reduce the processing difficulty of the vortex shell 10.
[0077] However, the end face of the second pipe section 122 is in direct contact with the upper end face of the stop ring 30. Although it can still maintain stable operation, the contact area and friction area of the stop ring 30 are slightly increased, but the impact on the overall efficiency of the electronic medium pump 100 is small. This solution can also be used when the power of the electronic medium pump 100 is less than 100W and the coolant replacement frequency of the cooling system is high.
[0078] According to some embodiments of this application, the flatness of the first annular boss 1221 is less than or equal to 0.1 mm, the surface roughness is less than or equal to 0.8 μm, and the radial width of the first annular boss 1221 is less than or equal to the radial width of the stop ring 30.
[0079] Therefore, when the upper end face of the stop ring 30 contacts the first annular boss 1221 and generates sliding friction, the contact area between the first annular boss 1221, which has lower flatness and lower surface roughness, and the upper end face of the stop ring 30 is smaller. This can reduce the contact area, thereby reducing the frictional loss of the stop ring 30 and improving the service life of the electronic medium pump 100.
[0080] It should be noted that a wear-resistant coating may be applied to the upper surface of the stop ring 30, or a wear-resistant coating may be applied to the surface of the first annular boss 1221 that contacts the stop ring 30.
[0081] like Figure 4 As shown, according to some embodiments of this application, the side wall of the first annular boss 1221 away from the mating protrusion 22 is spaced apart from the inner wall of the first pipe section 121 to form a receiving groove 1222 for receiving foreign objects in the medium.
[0082] In other words, the first annular boss 1221 protrudes from the end face of the second pipe section 122 toward the first pipe section 121, and the radial dimension of the first annular boss 1221 is smaller than the width of the end face, so as to form a receiving groove 1222 on the radial outer side of the first annular boss 1221. The receiving groove 1222 can play a role in holding material. If the medium contains small particulate impurities, under the action of hydraulic pressure, these small particulate impurities can be gathered in the receiving groove 1222, without affecting the radial floating of the stop member, which can reduce the probability of the stop ring 30 getting stuck, thereby improving the working stability and reliability of the stop ring 30.
[0083] like Figure 5 and Figure 6 As shown, according to some embodiments of this application, the convex portion 22 has an impeller inlet 221, the impeller body 21 has an impeller outlet 211, and the inlet pipe 12 further includes a third pipe section 123. The third pipe section 123 is located at the end of the second pipe section 122 away from the first pipe section 121. The inner diameter of the third pipe section 123 is equal to the inner diameter of the impeller inlet 221 and smaller than the inner diameter of the second pipe section 122.
[0084] Combination Figure 2 As shown, the end of the third pipe section 123 adjacent to the second pipe section 122 has the same inner diameter as the impeller inlet 221. This reduces the probability of turbulence and eddies in the medium entering through the inlet pipe 12 and then through the third pipe section 123 to the impeller inlet 221, resulting in less flow resistance and further improving the hydraulic performance of the electronic medium pump 100.
[0085] Combination Figure 5 and Figure 6 As shown, according to some embodiments of this application, a second annular boss 222 is formed on the outer wall surface of the mating protrusion 22, and the stop ring 30 is located between the second annular boss 222 and the first annular boss 1221.
[0086] That is, the first annular boss 1221 and the second annular boss 222 are axially opposite each other, and the stop ring 30 is located between the first annular boss 1221 and the second annular boss 222. In the first state, the stop ring 30 rests on the second annular boss 222. In the second state, the stop ring 30 moves away from the second annular boss 222 and toward the first annular boss 1221. In the third state, the stop ring 30 pushes against the first annular boss 1221.
[0087] Therefore, by setting the second annular boss 222, the first annular boss 1221 and the second annular boss 222 cooperate to limit the axial movement stroke of the stop ring 30, which can ensure that the backflow suppression of the stop ring 30 is reliable and stable.
[0088] According to some embodiments of this application, the radial width of the second annular boss 222 is 0.5mm-0.8mm.
[0089] For example, the radial width of the second annular boss 222 is 0.5mm, 0.6mm, 0.7mm, 0.8mm, etc.
[0090] This makes the radial width of the second annular boss 222 more reasonable, avoiding an excessively large radial width to reduce material costs. At the same time, it ensures that the stop ring 30 has a larger contact area with the medium when it is in the first state, so that the stop ring 30 can switch from the first state to the third state. At the same time, it avoids the radial width of the second annular boss 222 being too small, so that it has a better axial limiting effect on the stop ring 30, reduces the probability of the stop ring 30 getting stuck, and improves the working stability and reliability of the stop ring 30.
[0091] Combination Figure 2 and Figure 6 As shown, according to some embodiments of this application, a mating section 223 is also formed on the outer wall surface of the mating protrusion 22. The mating section 223 is located on the side of the second annular protrusion 222 away from the impeller body 21, and a first overflow gap c is formed between the mating section 223 and the stop ring 30.
[0092] In this way, a first overflow gap c is formed between the mating section 223 and the stop ring 30, so that a small amount of medium can be returned. The returned medium can be used to separate the mating section 223 and the stop ring 30 in the circumferential direction, thereby reducing the radial friction of the stop ring 30 and reducing working noise. At the same time, the mating section 223 can achieve radial limiting of the stop ring 30, reducing the probability of the stop ring 30 dislodging, and also improving the working stability and reliability of the stop ring 30.
[0093] According to some embodiments of this application, the size of the first overflow gap c is 0.045mm-0.065mm.
[0094] It should be noted that the first overflow gap c is the minimum radial gap between the impeller 20 and the stop ring 30 to prevent jamming. Limiting it to the range of 0.045mm-0.065mm can meet the working requirements of the stop ring 30 to move freely up and down, reduce the probability of the stop ring 30 jamming, and avoid excessive backflow, so as to take into account the hydraulic performance of the electronic medium pump 100.
[0095] It should be noted that the radial dimension of the first overflow gap c should theoretically be as small as possible, but if the actual dimension is too small, it will increase the risk of jamming and friction between the stop ring 30 and the impeller 20. Once jammed, the stop ring 30 will not be able to make normal contact with the bottom surface of the boss of the volute 10, thus causing its function to fail. Therefore, setting the first overflow gap c to the above-mentioned dimension range can improve the reliability of the stop ring 30.
[0096] Combination Figure 2 as well as Figure 10 As shown, according to some embodiments of this application, a second overflow gap d is formed between the second pipe section 122 and the mating section 223, and the second overflow gap d is connected to the first overflow gap c.
[0097] The second overflow gap d has a size of 0.45mm-0.65mm.
[0098] It should be noted that the second overflow clearance d is the minimum radial clearance between the impeller 20 and the volute 10 without friction, and the radial dimension is 0.45mm-0.65mm, which is also the safety clearance dimension commonly used in the electronic medium pump 100.
[0099] This application specifies that the second overflow gap d is not less than 0.45 mm and not greater than 0.65 mm. The radial (horizontal) dimension of this gap can meet the working requirements of the stop ring 30. If the gap is too small, the pressure difference between the upper and lower end faces of the stop ring 30 will decrease, making it difficult to ensure its working stability. It may result in poor contact between the upper end face and the boss surface of the volute 10, reducing the stability of the overall performance output of the electronic medium pump 100. If the gap is too large, the pressure difference between the upper and lower end faces of the stop ring 30 will increase. On the one hand, this may cause deformation of the ring itself. On the other hand, the upper end face may contact the boss surface of the volute 10 too tightly, increasing friction and radial movement resistance. The adverse effects of collision with the impeller 20 will become more obvious, similarly causing instability in the operation of the electronic medium pump 100.
[0100] Therefore, by setting the second overflow gap d within the above-mentioned size range, this application can improve the working stability of the stop ring 30, take into account the impact of working noise, effectively reduce working noise, and at the same time reduce the probability of deformation or damage to the stop ring 30, thus extending the service life of the stop ring 30.
[0101] like Figure 7 and Figure 8 As shown, according to some embodiments of this application, the stop ring 30 has an axial dimension of less than or equal to 0.4 mm, a radial width of 1.4 mm to 1.6 mm, a yield strength of greater than or equal to 420 MPa, and a weight of less than or equal to 0.4 g.
[0102] It should be noted that the weight of the stop ring 30 itself in the medium environment needs to be lower than the pressure difference between the upper and lower end surfaces of the medium so that the stop ring 30 can make stable contact with the bottom surface of the first annular boss 1221. Therefore, the weight of the stop ring 30 should not exceed 0.4g.
[0103] Meanwhile, the stop ring 30 can be made of metal material, with a heat-treated surface and a yield strength greater than or equal to 420 MPa. This reduces the probability of deformation of the stop ring 30, thereby improving its working stability and extending its service life. The axial dimension of the stop ring 30 is limited by the distance between the first annular boss 1221 and the second annular boss 222. A more reasonable axial dimension can improve the response speed of the stop ring 30, allowing it to switch to the third state more quickly. Furthermore, the stop ring 30 has better resistance to axial deformation and higher stability.
[0104] The radial dimension of the stop ring 30 is related to the size of the first overflow gap c and the contact area between the first annular boss 1221 and the stop ring 30. A more reasonable radial dimension can make the size of the first overflow gap c more reasonable, thereby improving the backflow suppression effect. A more reasonable contact area can reduce the wear of the stop ring 30 and extend its service life.
[0105] In other words, the radial dimension of the stop ring 30 is not less than 1.4mm, which can prevent the size of the first overflow gap c from being too large, thus ensuring a stable backflow suppression effect. The radial dimension of the stop ring 30 is not greater than 1.5mm, which can prevent the contact area between the first annular boss 1221 and the stop ring 30 from being too large, thereby reducing the wear of the stop ring 30. That is, a reasonable limit on the radial dimension of the stop ring 30 can balance the backflow suppression effect and friction loss, thus extending the service life of the stop ring 30.
[0106] This application proposes a vehicle, including the electronic medium pump 100 in the above embodiments, which has the same technical effects as the above medium pump, and will not be described again here.
[0107] The electronic medium pump 100 and other vehicle components and operations according to the embodiments of this utility model are known to those skilled in the art and will not be described in detail here.
[0108] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.
[0109] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.
Claims
1. An electronic medium pump, characterized in that, include: A vortex housing (10) comprising: a cover (11) and an inlet pipe (12), the cover (11) having a first side (111) and a second side (112), the inlet pipe (12) being located on the first side (111), the inlet pipe (12) comprising at least a first pipe section (121) and a second pipe section (122), the inner diameter of the second pipe section (122) being smaller than the inner diameter of the first pipe section (121); Impeller (20), the impeller (20) includes an impeller body (21) and a mating protrusion (22) protruding from the impeller body (21), a first reflux gap (a) is formed between the impeller body (21) and the second side surface (112), and a second reflux gap (b) is formed between the mating protrusion (22) and the second pipe section (122), and the second reflux gap (b) communicates with the first reflux gap (a); A stop ring (30) is fitted onto the mating protrusion (22). The inner diameter of the stop ring (30) is larger than the outer diameter of the mating protrusion (22) to form a first overflow gap (c) between the mating protrusion (22) and the inner wall of the stop ring (30). The stop ring (30) floats axially within the second return gap (b). The stop ring (30) is adapted to push against the end face of the second pipe section (122) facing the first pipe section (121) and overflow through the first overflow gap (c).
2. The electronic dielectric pump according to claim 1, characterized in that, The second pipe section (122) has a first annular boss (1221) on one end face facing the first pipe section (121), and the stop ring (30) is adapted to push against the first annular boss (1221).
3. The electronic dielectric pump according to claim 2, characterized in that, The flatness of the first annular boss (1221) is less than or equal to 0.1 mm, and the surface roughness is less than or equal to 0.8 μm.
4. The electronic dielectric pump according to claim 2, characterized in that, The side wall of the first annular boss (1221) away from the mating protrusion (22) is spaced apart from the inner wall of the first pipe section (121) to form a receiving groove (1222) for accommodating foreign objects in the medium.
5. The electronic dielectric pump according to claim 2, characterized in that, The mating protrusion (22) has an impeller inlet (221), the impeller body (21) has an impeller outlet (211), and the inlet pipe (12) further includes a third pipe section (123), which is located at the end of the second pipe section (122) away from the first pipe section (121). The inner diameter of the third pipe section (123) is equal to the inner diameter of the impeller inlet (221) and smaller than the inner diameter of the second pipe section (122).
6. The electronic dielectric pump according to claim 5, characterized in that, A second annular boss (222) is formed on the outer wall surface of the mating protrusion (22), and the stop ring (30) is located between the second annular boss (222) and the first annular boss (1221).
7. The electronic dielectric pump according to claim 6, characterized in that, The radial width of the second annular boss (222) is 0.5mm-0.8mm.
8. The electronic dielectric pump according to claim 6, characterized in that, A mating section (223) is also formed on the outer wall surface of the mating protrusion (22). The mating section (223) is located on the side of the second annular protrusion (222) away from the impeller body (21). A first overflow gap (c) is formed between the mating section (223) and the stop ring (30).
9. The electronic dielectric pump according to claim 8, characterized in that, The size of the first overflow gap (c) is 0.045mm-0.065mm.
10. The electronic dielectric pump according to claim 8, characterized in that, A second overflow gap (d) is formed between the second pipe section (122) and the mating section (223), and the second overflow gap (d) is connected to the first overflow gap (c).
11. The electronic medium pump according to claim 10, characterized in that, The second overflow gap (d) has a size of 0.45mm-0.65mm.
12. The electronic medium pump according to any one of claims 1-11, characterized in that, The stop ring (30) has an axial dimension of less than or equal to 0.4 mm, a radial width of 1.4 mm to 1.6 mm, a yield strength of greater than or equal to 420 MPa, and a weight of less than or equal to 0.4 g.
13. A vehicle, characterized in that, include: The electronic medium pump according to any one of claims 1-12.