Water pump inlet and outlet structure and water pump

Abstract

The utility model provides a water pump inlet and outlet water structure and water pump, wherein the double position impeller rotates in the double cavity water inlet casing, the fluid in the water inlet cavity produces the pressure difference, forms the self suction, thereby avoids the situation difficult to suck the washing liquid under the cavity state, and improves the pump liquid pressure, the size of first water outlet channel gradually increases from the water inlet, is favorable to reduce the impact of the fluid reflux in first water outlet channel and the fluid about to enter first water outlet channel, thereby reduces the loss of fluid kinetic energy, when first water outlet pipe forms the acute angle with the double cavity water inlet casing center axis through the pipeline outer wall, can cooperate with the direction of fluid being thrown out by double position impeller, reduces the energy loss of fluid impact on the pipeline outer wall, thereby improves the washing liquid pressure spouted from first water outlet pipe, under the joint action of double position impeller and water inlet cavity, first water outlet channel and water inlet, finally makes the spouting pressure of water pump improve.

Description

Technical Field

[0001] This utility model relates to the field of water pump technology, specifically to a water pump inlet / outlet structure and a water pump. Background Technology

[0002] With the development of intelligent driving technology, more and more sensing devices are being applied to automobiles, such as lidar, cameras, etc. The sensor heads of these sensing devices need to be kept clean in order to maintain their sensing function. Therefore, water pumps, as cleaning tools for these sensing devices, play a crucial role in cleaning.

[0003] For example, as shown in the Chinese utility model patent for a bidirectional high-pressure washing pump (CN117108520B), the inlet and outlet structure of this type of washing pump only includes a conventional water inlet interface and first and second connecting pipes. When there is no washing liquid in the pump for the first time or in the middle, the inlet pump must be emptied, otherwise the washing liquid cannot be pumped out, thus affecting the cleaning function. In addition, the pump's spray pressure is highly dependent on the impeller, and the inlet and outlet structure does not have a pressurization function, resulting in insufficient final spray pressure of the pump, which is difficult to meet the cleaning requirements of intelligent driving vehicles for components such as lidar and cameras. Utility Model Content

[0004] The problem to be solved by this utility model is to provide a water pump inlet and outlet structure that can pump out liquid even when the water pump cavity is empty and has a pressurization function, as well as a water pump with such a water pump inlet and outlet structure.

[0005] The technical solution adopted by this utility model to solve the above problems is: a water pump inlet and outlet structure, which includes a double-cavity inlet housing, a double-position impeller disposed in the double-cavity inlet housing, and at least one first outlet pipe connected to the double-cavity inlet housing; The dual-chamber water inlet housing has a water inlet chamber; when the dual-position impeller rotates inside the dual-chamber water inlet housing, the fluid in the water inlet chamber generates a pressure difference and increases the pump fluid pressure; The first water outlet pipe has an inlet communicating with the dual-cavity water inlet housing and a first water outlet channel extending outward from the inlet; the size of the first water outlet channel gradually increases outward from the inlet; the first water outlet pipe includes an outer wall, which is set at an acute angle to the central axis of the dual-cavity water inlet housing.

[0006] Compared with the prior art, the dual-position impeller of this utility model rotates within the dual-chamber inlet housing, generating a pressure difference in the fluid within the inlet chamber, thus creating a self-suction force. This avoids the difficulty in drawing up the washing liquid in an empty cavity state and increases the pump pressure. The size of the first outlet channel gradually increases from the inlet outwards, which helps reduce the impact between the fluid flowing back into the first outlet channel and the fluid about to enter the first outlet channel, thereby reducing the loss of fluid kinetic energy. When the first outlet pipe forms an acute angle with the central axis of the dual-chamber inlet housing through the outer wall of the pipe, it can match the direction in which the fluid is thrown out by the dual-position impeller, reducing the energy lost by the fluid impacting the outer wall of the pipe, thereby increasing the pressure of the washing liquid sprayed from the first outlet pipe. Under the combined action of the dual-position impeller and the inlet chamber, and the first outlet channel and the inlet, the pressure and kinetic energy loss along the entire flow path of the fluid are improved, increasing the pump pressure and efficiency, and ultimately increasing the pump's spray pressure.

[0007] According to one embodiment of the present invention, the dual-position impeller includes a self-priming impeller disposed in the water inlet chamber; when the self-priming impeller rotates in the water inlet chamber, the fluid in the water inlet chamber generates a pressure difference in order to obtain self-priming force.

[0008] According to one embodiment of the present invention, the water inlet chamber is configured as an inverted cone shape, and its size gradually decreases from its suction port.

[0009] According to one embodiment of the present invention, the self-priming impeller includes multiple self-priming blades, the self-priming blades are configured with curved sides, and the size of the self-priming blades gradually increases from the water inlet of the water inlet chamber.

[0010] According to one embodiment of the present invention, the dual-chamber water inlet housing has a pumping chamber; the dual-position impeller includes a pumping impeller disposed in the pumping chamber; the pumping impeller includes multiple pumping blades; the pumping blades are configured to have a flat side surface, and the size of the pumping blades gradually decreases from the blade root to the blade tip.

[0011] According to one embodiment of the present invention, the first water outlet pipe is provided as two, and is respectively located on both sides of the dual-cavity water inlet shell; The first outlet pipe includes an inner wall; the inner wall is configured to be parallel to the central axis of the dual-cavity inlet housing; The cross-section of the first water outlet channel is set as an irregular circular hole.

[0012] According to one embodiment of the present invention, it further includes a second water outlet pipe; the second water outlet pipe has a second water outlet channel communicating with the first water outlet channel; the cross-section of the second water outlet channel is set as an irregular circular hole, and the size gradually increases outward from the first water outlet channel.

[0013] The technical solution adopted by this utility model to solve the above problems is as follows: a water pump, including the aforementioned water pump inlet and outlet structure, which further includes a power module connected to the dual-position impeller, an electronic control module connected to the power module, and a self-locking sealing assembly disposed in the dual-chamber water inlet housing.

[0014] According to one embodiment of the present invention, the self-locking sealing assembly includes a shaft seal ring disposed in the pump water chamber, a support ring, a sealing microgap formed between the shaft seal ring and the support ring, and a self-locking part disposed in the sealing microgap; the self-locking part deforms when subjected to water pressure in the pump water chamber to seal the sealing microgap, thereby reducing fluid leakage in the sealing microgap.

[0015] According to one embodiment of the present invention, the self-locking part includes a groove and a flange that cooperate with each other; the shaft sealing ring includes a first force-bearing valve, and the support ring includes a second force-bearing valve; one of the groove and the flange is disposed in the first force-bearing valve, and the other is disposed in the second force-bearing valve; the second force-bearing valve deforms toward the first force-bearing valve when subjected to the water pressure of the pump chamber. Attached Figure Description

[0016] Figure 1 This is a perspective view of a water pump according to a preferred embodiment of the present invention; Figure 2 This is an exploded view of the water pump inlet and outlet structure according to a preferred embodiment of the present invention; Figure 3 This is a perspective view of a double-position impeller according to a preferred embodiment of the present invention; Figure 4 This is a bottom view of a preferred embodiment of the double-position impeller according to the present invention; Figure 5 This is a top view of a preferred embodiment of the double-position impeller according to the present invention; Figure 6 This is a cross-sectional view of the water pump inlet and outlet structure according to a preferred embodiment of the present invention. Figure 7 This is a schematic diagram illustrating the working principle of the self-locking part according to a preferred embodiment of the present invention; Figure 8 This is a perspective view of a water pump according to another preferred embodiment of the present invention; Figure 9 This is a cross-sectional view of a unidirectional water pump inlet and outlet structure according to a preferred embodiment of the present invention. Figure 10 This is a cross-sectional view of the bidirectional water pump inlet and outlet structure according to a preferred embodiment of the present invention. Figure 11 This is a cross-sectional view of the bidirectional water pump inlet and outlet structure according to a preferred embodiment of the present invention. Figure 12 This is a cross-sectional view of the bidirectional water pump inlet and outlet structure according to a preferred embodiment of the present invention. Figure 13 This is a cross-sectional schematic diagram of a bidirectional high-pressure, high-efficiency water pump according to a preferred embodiment of the present invention. In the picture: Dual-chamber water inlet housing 1; pump water chamber 11, water inlet chamber 12; Two-position impeller 2; pump impeller 21, self-priming impeller 22; pump blades 211, self-priming blades 221; Self-locking sealing assembly 3; shaft seal ring 31, support ring 32, sealing microgap 33, self-locking part 34; first force-receiving valve 311, slot 312; second force-receiving valve 321, insert post 322; groove 341, flange 342; First water outlet pipe 4; outer wall of pipe 41, inner wall of pipe 42, water inlet 43, first water outlet channel 44; Second water outlet pipe 5; Second water outlet channel 51; Power Module 6; Electronic control module 7. Detailed Implementation

[0017] Before describing any embodiment of this invention in detail, it should be understood that the invention is not limited in its application to the details of the construction and arrangement of the components set forth in the following description or illustrated in the following figures. The invention can have other embodiments and can be practiced or carried out in various ways. Furthermore, it should be understood that the wording and terminology used herein are for descriptive purposes and should not be considered limiting. The use of “comprising” or “having” and variations thereof herein is intended to cover the items set forth below and their equivalents, as well as any additional items. Unless otherwise specified or limited, the terms “installation,” “connection,” “support,” and “linkage,” and variations thereof are used broadly and cover both direct and indirect installation, connection, support, and linking. Moreover, “connection” and “linkage” are not limited to physical or mechanical connections or links.

[0018] Furthermore, firstly, in the disclosure of this utility model, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the above terms should not be construed as a limitation on this utility model. Secondly, the term "a" should be understood as "at least one" or "one or more," that is, in one embodiment, the number of an element can be one, while in another embodiment, the number of the element can be multiple. The term "a" should not be construed as a limitation on the quantity.

[0019] Those skilled in the art should understand that the embodiments of the present invention described below and shown in the accompanying drawings are merely examples and do not limit the present invention. The purpose of the present invention has been fully and effectively achieved. The function and structural principles of the present invention are shown and described in the following embodiments. Without departing from the stated principles, the implementation of the present invention may have any variations or modifications.

[0020] The embodiments of this utility model will be further described below with reference to the accompanying drawings.

[0021] Please see Figure 1-13 The diagram shows a water pump inlet and outlet structure, which includes a dual-chamber inlet housing 1 and a dual-position impeller 2 disposed in the dual-chamber inlet housing 1; the dual-chamber inlet housing 1 has a pump water chamber 11 and an inlet chamber 12 disposed below the pump water chamber 11; when the dual-position impeller 2 rotates in the dual-chamber inlet housing 1, the fluid in the inlet chamber 12 generates a pressure difference in order to obtain self-priming force and increase the pump liquid pressure.

[0022] In some embodiments, the dual-chamber inlet housing 1 refers to a housing structure comprising a pumping chamber 11 and an inlet chamber 12. It can be implemented using either a modular assembly or a single-piece molding method. The pumping chamber 11 is used to pressurize the pumping fluid, and the inlet chamber 12 is used to generate self-priming force, solving the problem of existing water pumps needing to be emptied during initial startup or when there is no fluid in the middle of operation. The dual-position impeller 2 refers to an impeller rotating within the dual-chamber inlet housing 1. It can be made of metal or plastic. Its rotation generates a pressure difference in the inlet chamber 12, creating self-priming force and simultaneously increasing the pumping fluid pressure, overcoming the deficiency of insufficient head in existing water pumps.

[0023] In actual use, the dual-position impeller 2 rotates within the dual-chamber inlet housing 1, creating a pressure difference in the fluid within the inlet chamber 12, thus generating self-priming force. This avoids the difficulty in drawing up washing liquid when the chamber is empty and increases the pump pressure. The interaction between the dual-position impeller 2 and the inlet chamber 12 improves the pressure and kinetic energy loss along the entire fluid flow path, increasing pump pressure and efficiency, ultimately leading to a higher pump discharge pressure.

[0024] Please continue reading. Figure 2-6 The water inlet chamber 12 is configured to gradually decrease in size from its suction port to the pump chamber 11; the dual-position impeller 2 includes a pump impeller 21 disposed in the pump chamber 11 and a self-priming impeller 22 disposed in the water inlet chamber 12; when the self-priming impeller 22 rotates in the water inlet chamber 12, the fluid in the water inlet chamber 12 generates a pressure difference in order to obtain a self-priming force from the suction port of the water inlet chamber 12 to the pump chamber 11.

[0025] Specifically, the tapering structure of the inlet chamber 12 causes the fluid velocity to increase along the flow channel direction under the drive of the self-priming impeller 22. Since the fluid velocity above the inlet chamber 12 is faster than the fluid velocity below it, the fluid pressure above the inlet chamber 12 is lower than the fluid pressure below it, thus creating a pressure difference. This pressure difference drives the fluid to flow from the suction port to the pump chamber 11. When the dual-chamber inlet housing 1 is in a hollow state, the air, under the action of the dual-position impeller 2, also follows the aforementioned pressure difference driving effect, thereby causing the dual-chamber inlet... Air inside the water housing 1 is automatically forced into the pump water chamber 11 and then discharged under the action of the pump impeller 21, without the need for additional purging operations as with existing water pumps. When the air inside the dual-chamber water housing 1 is completely purged, the washing liquid can be sprayed out along the path of the water inlet chamber 12 and the pump water chamber 11 under the action of the dual-position impeller 2. It is worth mentioning that, due to the cooperation between the water inlet chamber 12 and the self-priming impeller 22, the washing liquid is pressurized when flowing through the water inlet chamber 12, thereby increasing the overall spray pressure of the water pump and helping to increase the pump head.

[0026] Please continue reading. Figure 2-6 The water inlet chamber 12 is configured as an inverted cone, and the angle between the central axis of the water inlet chamber 12 and the inner wall is set to 10°-20°.

[0027] Specifically, the inverted conical structure guides the fluid towards the pump chamber 11 through a continuously contracting flow channel. The angle between the central axis and the inner wall is limited to 10°-20°, allowing the fluid to form a laminar flow state under the drive of the self-priming impeller 22. This angle range ensures that the acceleration process of the fluid in the inlet chamber 12 is smooth, avoiding the formation of eddies due to excessive angle, or the increase in flow resistance due to insufficient angle. In addition, this angle range is also beneficial for core pulling of the mold, making the manufacturing of the dual-chamber inlet housing 1 more convenient and cost-effective. The inverted conical shape matches the curved blades of the self-priming impeller 22, further optimizing the kinetic energy conversion efficiency of the fluid in the inlet chamber 12.

[0028] During operation, the inner wall of the inverted conical inlet chamber 12 maintains an angle of 10°-20° with the central axis. After entering through the suction port, the fluid flows along the conical chamber wall towards the pump chamber 11. When the self-priming impeller 22 rotates, the fluid undergoes a spiral acceleration motion along the conical inner wall under the push of the curved blades. The 10°-20° angle ensures that the fluid flow direction and the impeller rotation direction form an optimal matching angle, reducing collision losses between the fluid and the chamber wall. The gradually narrowing flow channel created by the inverted conical structure allows the fluid pressure to gradually increase during flow. Combined with the curved blade design of the self-priming impeller 22, the fluid has undergone preliminary pressurization before entering the pump chamber 11, thereby reducing load fluctuations on the pump impeller 21, reducing noise caused by pressure differences, and also facilitating secondary pressurization of the fluid within the pump chamber 11, ultimately resulting in a higher pressure of the washing liquid sprayed by the pump.

[0029] Please continue reading. Figure 2-4 The pump impeller 21 includes multiple pump blades 211; the pump blades 211 are configured with flat sides and the size of the pump blades 211 gradually decreases from the blade root to the blade tip; the self-priming impeller 22 includes multiple self-priming blades 221, the self-priming blades 221 are configured with curved sides and the size of the self-priming blades 221 gradually increases from the suction port of the water inlet chamber 12 to the pump chamber 11.

[0030] Specifically, the planar blades of the pump impeller 21 reduce turbulence at the blade tip by decreasing the blade tip size during rotation, and the planar side accelerates and compresses the fluid in a straight line, thereby improving the pressure transmission efficiency in the pump chamber 11. The curved blades of the self-priming impeller 22 are conducive to the formation of vortices, enhancing the self-priming effect. Furthermore, the size of the self-priming blades 221 gradually increases from the inlet of the water inlet chamber 12 to the pump chamber 11, which helps to increase the velocity difference of the fluid above and below the water inlet chamber 12, promotes the flow of fluid from the water inlet chamber 12 to the pump chamber 11, and further enhances the self-priming effect.

[0031] Please continue reading. Figure 8-13It further includes at least one first outlet pipe 4 connected to the dual-cavity water inlet housing 1; the first outlet pipe 4 includes an outer wall 41, which is configured to form an acute angle with the central axis of the dual-cavity water inlet housing 1.

[0032] Specifically, when the fluid is thrown out by the pump impeller 21, it will first hit the outer wall 41 of the pipe. When the first outlet pipe 4 forms an acute angle with the central axis of the double-chamber water inlet housing 1 through the outer wall 41 of the pipe, it can match the direction in which the fluid is thrown out by the pump impeller 21, reduce the energy lost by the fluid hitting the outer wall 41 of the pipe, and thus increase the pressure of the washing liquid sprayed from the first outlet pipe 4.

[0033] Please continue reading. Figure 8-9 In some embodiments, a single first outlet pipe 4 can be configured, located on one side of the dual-chamber inlet housing 1. By setting the outer wall 41 of the first outlet pipe 4 at an acute angle to the central axis of the dual-chamber inlet housing 1, the traditional design of the water pump outlet pipe being parallel to the central axis of the housing is changed. This design makes the water flow in the outlet pipe smoother and reduces energy loss when the water flow changes direction. As a result, the water pump's output efficiency is improved, and the output pressure is increased.

[0034] Please continue reading. Figure 10-12 The first water outlet pipe 4 is configured as two, and is located on both sides of the dual-cavity water inlet housing 1 respectively; the outer wall 41 of the pipe is configured to form an angle of 10°-20° with the central axis of the dual-cavity water inlet housing 1; the first water outlet pipe 4 includes an inner wall 42; the inner wall 42 of the pipe is configured to be parallel to the central axis of the dual-cavity water inlet housing 1; the first water outlet pipe 4 has a water inlet 43 communicating with the dual-cavity water inlet housing 1 and a first water outlet channel 44 extending outward from the water inlet 43; the size of the first water outlet channel 44 gradually increases outward from the water inlet 43; the cross-section of the first water outlet channel 44 is configured as an irregular circular hole; the size of the water inlet 43 in the height direction is smaller than the height of the tip of the pump blade 211.

[0035] In other embodiments, there may be two first outlet pipes 4, which are symmetrically distributed on both sides of the dual-cavity inlet housing 1 to achieve the reversing water spraying function in conjunction with the forward and reverse rotation of the dual-position impeller 2. The outer wall 41 of the pipe forms an angle of 10°-20° with the central axis, and the inner wall 42 of the pipe is set to be parallel to the central axis of the dual-cavity inlet housing 1. Under this angle setting, the first outlet pipe 4 can reduce the impact with the fluid under the angle design of the outer wall 41 of the pipe, and the first outlet pipe 4 gradually expands under the angle design of the inner wall 42 of the pipe. The expansion outlet channel reduces the fluid velocity and increases the static pressure. This structural combination makes the pumped fluid form a stable laminar flow state in the water outlet stage, significantly improving the energy conversion efficiency of the pumping system and ultimately achieving a higher head fluid output.

[0036] Furthermore, the size of the first outlet channel 44 gradually increases outward from the inlet 43, meaning the inlet 43 is the smallest in the first outlet channel 44. Traditionally, it's believed that the inlet 43, which communicates with the pump chamber 11, should be as large as possible to pump in more fluid when the pump impeller 21 rotates. However, in reality, since the pump impeller 21 pumps fluid intermittently into the inlet 43 through multiple pump blades 211, when one blade rotates to the inlet 43, fluid is pumped into the first outlet channel 44. When that blade moves away from the inlet 43, some of the unexpelled liquid in the first outlet channel 44 flows back towards the outside. When the next blade rotates to the first outlet channel 44, the next wave of fluid pumped into the first outlet channel 44 collides with this returning fluid, creating turbulence and resulting in a loss of fluid kinetic energy, causing the pump impeller 21 to vibrate. When the inlet 43... 3. When the height dimension of the pump blade 211 is smaller than the height dimension of the tip of the pump blade 211 and the size of the first outlet channel 44 gradually increases from the inlet 43 outwards, the returning fluid encounters the gradually narrowing first outlet channel 44, its return flow velocity increases and the pressure decreases. When the fluid brought by the next pump blade 211 collides with the returning fluid, the pressure difference can easily push the return flow back, thereby reducing the loss of fluid kinetic energy and reducing the vibration of the pump impeller 21. For example, when the height dimension of the inlet 43 is 1:4 compared with the height dimension of the tip of the pump blade 211, the pumping pressure of the pump blade 211 can be significantly greater than the pressure of the returning fluid, thereby making it easier to push the return flow back, thereby reducing the loss of fluid kinetic energy. Moreover, under this height ratio, the height dimension of the tip of the pump blade 211 is more reasonable, which facilitates the manufacturing of the double-position impeller 2 and the matching of its height with the pump chamber 11.

[0037] It is worth mentioning that the two first outlet pipes 4 distributed on both sides of the dual-cavity water inlet shell 1 are generally formed by the core-pulling mechanism of the mold. When the outer wall 41 of the pipe forms an angle of 10°-20° with the central axis, and the inner wall 42 of the pipe is set to be parallel to the central axis of the dual-cavity water inlet shell 1, the two first outlet pipes 4 can be pulled out by one core-pulling mechanism, avoiding the need to use two sets of core-pulling mechanisms to pull out the two first outlet pipes 4 from two directions. This reduces the manufacturing difficulty and manufacturing cost while achieving higher head fluid output.

[0038] Please continue reading. Figure 10-13 The second water outlet pipe 5 is further included; the second water outlet pipe 5 has a second water outlet channel 51 connected to the first water outlet channel 44; the cross-section of the second water outlet channel 51 is set as an irregular circular hole, and the size gradually increases outward from the first water outlet channel 44.

[0039] Specifically, based on the aforementioned first outlet channel 44, when the high-pressure fluid enters the second outlet channel 51 from the first outlet channel 44, the continuous expansion of the channel cross-section causes the flow velocity to gradually decrease, the internal kinetic energy of the fluid is further converted into static pressure energy, and the kinetic energy lost due to the collision between the fluid returning through the first outlet channel 44 and the second outlet channel 51 and the fluid entering the first outlet channel 44 is further reduced, and the vibration of the pump impeller 21 is further reduced; the conical structure of the second outlet channel 51 guides the fluid to diffuse smoothly along the central axis, reducing the boundary layer separation phenomenon.

[0040] It is worth mentioning that the cross-section of the first water outlet channel 44 and the second water outlet channel 51 is set as an irregular circular hole. The irregular circular hole can be elliptical, rectangular with rounded corners, or trapezoidal with rounded corners, etc.

[0041] Please continue reading. Figure 1-13 The water pump shown includes a power module 6 connected to the dual-position impeller 2, an electronic control module 7 connected to the power module 6, and a self-locking sealing assembly 3 disposed in the dual-chamber water inlet housing 1.

[0042] Furthermore, the self-locking sealing assembly 3 includes a shaft seal ring 31, a support ring 32, a sealing microgap 33 formed between the shaft seal ring 31 and the support ring 32, and a self-locking part 34 disposed in the sealing microgap 33; the self-locking part 34 deforms when subjected to the water pressure of the pump chamber 11 to seal the sealing microgap 33, thereby reducing fluid leakage in the sealing microgap 33.

[0043] Specifically, the self-locking sealing assembly 3 refers to a sealing structure composed of a shaft seal ring 31, a support ring 32, a sealing micro-gap 33, and a self-locking part 34. The self-locking part 34 seals the sealing micro-gap 33 by water pressure deformation, reducing fluid leakage and pressure loss within the sealing micro-gap 33. The self-locking part 34 of the self-locking sealing assembly 3 is located in the sealing micro-gap 33 between the upper support rings 32, and deforms when subjected to water pressure from the pump water chamber 11, sealing the sealing micro-gap 33 and reducing fluid leakage from the sealing micro-gap 33. This reduces the pressure loss of the fluid in the pump water chamber 11 itself, allowing the pressure of the fluid in the pump water chamber 11 to better act on the first outlet pipe 4 to eject fluid.

[0044] Please continue reading. Figure 2 , Figure 6 , Figure 7 The self-locking part 34 includes a groove 341 and a flange 342 that cooperate with each other; the shaft seal ring 31 includes a first force-bearing valve 311, and the support ring 32 includes a second force-bearing valve 321; one of the groove 341 and the flange 342 is disposed in the first force-bearing valve 311, and the other is disposed in the second force-bearing valve 321; the second force-bearing valve 321 deforms toward the first force-bearing valve 311 when subjected to the water pressure of the pump chamber 11.

[0045] In some embodiments, the mating arrangement of the groove 341 and the flange 342 can be designed as a continuous annular structure or as multiple discretely distributed independent units; the materials of the first force-receiving valve 311 and the second force-receiving valve 321 can be selected from rubber or silicone composite materials with different elastic moduli; the deformation direction of the second force-receiving valve 321 can be adjusted by changing the tilt angle between the flange 342 and the groove 341. The contact surfaces of the groove 341 and the flange 342 can be processed into a stepped or curved surface to enhance the tightness of the fit during deformation. Specifically, when the water pressure in the pump chamber 11 increases, the second force-bearing valve 321 bends towards the first force-bearing valve 311 under pressure, causing the flange 342 to embed into the groove 341, forming a mechanical interlock. As the water pressure increases, the contact area between the flange 342 and the groove 341 gradually increases until the gap is completely filled, dynamically sealing the micro-gap 33. During this process, the deformation of the second force-bearing valve 321 is positively correlated with the water pressure. The geometry of the groove 341 and the flange 342 limits the deformation amplitude, avoiding excessive compression that could lead to structural fatigue.

[0046] Through the above technical solution, the present invention achieves the automatic sealing function of the self-locking sealing assembly 3. When the water pressure in the pump water chamber 11 increases, the self-locking part 34 can automatically seal the sealing micro-gap 33, effectively reducing fluid leakage in the sealing micro-gap 33, thereby reducing the pressure loss of the fluid in the pump water chamber 11 itself. This design not only improves the sealing performance of the water pump, but also automatically adjusts the sealing degree according to changes in water pressure, thereby improving the overall efficiency and reliability of the water pump. At the same time, this self-locking structure is simple and easy to implement, easy to process and assemble, and reduces production costs.

[0047] Please continue reading. Figure 2 , Figure 6 , Figure 7 The shaft seal ring 31 has a plurality of slots 312 distributed circumferentially, and the support ring 32 includes a plurality of inserts 322 arranged circumferentially. The support ring 32 is fixed to the shaft seal ring 31 by means of the plurality of inserts 322 cooperating with the plurality of slots 312, so as to support the shaft seal ring 31.

[0048] In some embodiments, the number of slots 312 and pins 322 correspond to their circumferential distribution positions. The diameter of the pins 322 is slightly larger than the width of the slots 312. After the pins 322 are inserted into the slots 312, an interference fit is formed. The depth of the slots 312 matches the length of the pins 322, ensuring that the axial clearance of the upper support ring 32 is compressed to a preset range after the pins 322 are fully inserted. Specifically, when the insert 322 is inserted into the slot 312 under water pressure, the outer wall of the insert 322 contacts the inner wall of the slot 312, and the two are in an interference fit, which makes the assembly gap between them small and prevents fluid from leaking between them. The circumferential distribution design of the insert 322 and the slot 312 prevents the upper support ring 32 from rotating relative to each other in the circumferential direction, thus preventing the local expansion of the sealing micro-gap 33 due to rotational misalignment. The interference fit between the slot 312 and the insert 322 further restricts the radial displacement of the upper support ring 32, ensuring that the size of the sealing micro-gap 33 remains uniform in both the circumferential and radial directions, thereby reducing the pressure loss caused by fluid leakage through the sealing micro-gap 33. Through the above technical solution, the present invention achieves precise positioning and fixation of the upper support ring 32, effectively reducing the size of the sealing micro-gap 33, reducing fluid leakage from the sealing micro-gap 33, and alleviating the sealing pressure of the self-locking part 34. Furthermore, the multiple spaced inserts 322 can evenly support the shaft seal ring 31 from multiple directions to maximize its sealing function. The multiple spaced inserts 322 also ensure the shaft seal ring 31 maintains good integrity, improving its structural strength and thus enhancing the pump's sealing performance and operating efficiency. Moreover, the design of the slot 312 and inserts 322 makes the assembly process of the upper support ring 32 simpler and faster, which is beneficial for the pump's production and maintenance.

[0049] From another perspective, the shaft seal ring 31 and the support ring 32 have multiple sealing mating structures. Each sealing mating structure may have errors during manufacturing and installation. When the cumulative error of these sealing mating structures exceeds a certain value, it may cause the sealing gap 33 to expand, resulting in rapid leakage of fluid pressure. However, the self-locking part 34 can effectively prevent the expansion of the sealing gap 33 caused by the cumulative error of each link, thereby ensuring that the output pressure of the fluid does not decrease.

[0050] Thus, in the entire flow path of the fluid, in the first stage, the washing liquid is pressurized when it flows through the inlet chamber 12 through the cooperation of the inlet chamber 12 and the self-priming impeller 22. In the second stage, the self-locking part 34 can automatically seal the sealing micro gap 33, effectively reducing fluid leakage in the sealing micro gap 33, thereby reducing the pressure loss of the fluid in the pump chamber 11. In the third stage, the angle design of the outer wall 41 of the pipe can reduce the impact with the fluid. The flow velocity is gradually reduced by the continuous expansion of the cross-section of the first outlet channel 44 and the second outlet channel 51. The kinetic energy inside the fluid is converted into static pressure energy in large quantities, and the kinetic energy lost by the backflowing fluid impacting the first outlet channel 44 is reduced. Under the combined effect of the above three stages, the final pump discharge pressure is significantly increased.

[0051] In some embodiments, the power module 6 is configured as a motor, with the motor's output shaft passing through the self-locking sealing assembly 3 and connected to the dual-position impeller 2; the power module 6 may be a brushless motor or a servo motor as the drive source. The electronic control module 7 includes a control circuit board and a signal interface. The control circuit board is connected to the power input terminal of the power module 6 via wires, and the signal interface receives external control commands and converts them into motor speed adjustment signals.

[0052] It is worth mentioning that the aforementioned design ultimately increases the water pump's spray pressure. With the spray pressure meeting the usage requirements, the present invention can replace the power module 6 with a lower power, thereby saving energy and reducing the heat and noise of the power module 6.

[0053] The above description only illustrates the preferred embodiment of this utility model and should not be construed as limiting the scope of the claims. This utility model is not limited to the above embodiments, and variations in its specific structure are permitted. All changes made within the scope of the independent claims of this utility model are also within the scope of protection of this utility model.

Claims

1. A water pump inlet and outlet structure, characterized in that: It includes a dual-chamber water inlet housing (1), a dual-position impeller (2) disposed in the dual-chamber water inlet housing (1), and at least one first water outlet pipe (4) connected to the dual-chamber water inlet housing (1). The dual-chamber water inlet housing (1) has a water inlet chamber (12); when the dual-position impeller (2) rotates inside the dual-chamber water inlet housing (1), the fluid inside the water inlet chamber (12) generates a pressure difference and increases the pump fluid pressure; The first water outlet pipe (4) has an inlet (43) communicating with the dual-cavity water inlet housing (1) and a first water outlet channel (44) extending outward from the inlet (43); the size of the first water outlet channel (44) gradually increases outward from the inlet (43); the first water outlet pipe (4) includes an outer wall (41) of the pipe, which is set to form an acute angle with the central axis of the dual-cavity water inlet housing (1).

2. The water pump inlet and outlet structure according to claim 1, characterized in that: The dual-position impeller (2) includes a self-priming impeller (22) disposed in the water inlet chamber (12); when the self-priming impeller (22) rotates in the water inlet chamber (12), the fluid in the water inlet chamber (12) generates a pressure difference in order to obtain self-priming force.

3. The water pump inlet and outlet structure according to claim 2, characterized in that: The water inlet chamber (12) is configured as an inverted cone shape, and its size gradually decreases from its suction port.

4. The water pump inlet and outlet structure according to claim 2 or 3, characterized in that: The self-priming impeller (22) includes multiple self-priming blades (221), the self-priming blades (221) are configured with curved sides, and the size of the self-priming blades (221) gradually increases from the water inlet cavity (12).

5. The water pump inlet and outlet structure according to claim 1, characterized in that: The dual-chamber water inlet housing (1) has a pumping chamber (11); the dual-position impeller (2) includes a pumping impeller (21) disposed in the pumping chamber (11); the pumping impeller (21) includes multiple pumping blades (211); the pumping blades (211) are configured to have a flat side, and the size of the pumping blades (211) gradually decreases from the blade root to the blade tip.

6. The water pump inlet and outlet structure according to claim 1, characterized in that: The first water outlet pipe (4) is configured as two, and is located on both sides of the dual-cavity water inlet housing (1); The first outlet pipe (4) includes an inner wall (42); the inner wall (42) is configured to be parallel to the central axis of the dual-cavity inlet housing (1); The cross-section of the first water outlet channel (44) is set as an irregular circular hole.

7. The water pump inlet and outlet structure according to claim 6, characterized in that: It further includes a second water outlet pipe (5); the second water outlet pipe (5) has a second water outlet channel (51) connected to the first water outlet channel (44); the cross section of the second water outlet channel (51) is set as an irregular circular hole, and the size gradually increases outward from the first water outlet channel (44).

8. A water pump, comprising the water pump inlet and outlet structure according to any one of claims 1-7, characterized in that: It includes a power module (6) connected to the dual-position impeller (2), an electronic control module (7) connected to the power module (6), and a self-locking sealing assembly (3) disposed in the dual-chamber water inlet housing (1).

9. The water pump according to claim 8, characterized in that: The self-locking sealing assembly (3) includes a shaft seal ring (31) disposed in the pump water chamber (11), a support ring (32), a sealing microgap (33) formed between the shaft seal ring (31) and the support ring (32), and a self-locking part (34) disposed in the sealing microgap (33); the self-locking part (34) deforms when subjected to water pressure in the pump water chamber (11) to seal the sealing microgap (33) in order to reduce fluid leakage in the sealing microgap (33).

10. The water pump according to claim 9, characterized in that: The self-locking part (34) includes a groove (341) and a flange (342) that cooperate with each other; the shaft seal ring (31) includes a first force-bearing valve (311), and the support ring (32) includes a second force-bearing valve (321); one of the groove (341) and the flange (342) is disposed on the first force-bearing valve (311), and the other is disposed on the second force-bearing valve (321); the second force-bearing valve (321) deforms toward the first force-bearing valve (311) when subjected to water pressure from the pump chamber (11).

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