CN117905700A - Washing pump and washing electric appliance with same - Google Patents

Abstract

The invention discloses a washing pump and a washing electric appliance with the same. The washing pump includes: a pump housing assembly and an impeller. An impeller accommodating cavity is formed in the pump shell component, an inner inlet channel positioned at the front end of the impeller accommodating cavity is formed in the pump shell component, the inner inlet channel comprises a first channel section and a second channel section, and the diameter of the front side first channel section is smaller than that of the rear side second channel section. The impeller comprises: a back cover plate; a hub; the inner edge of the front cover plate is bent forward to form a front end pipe, the front end pipe comprises a first pipe section and a second pipe section, the first pipe section is located in the first channel section, the second pipe section is located in the second channel section, and front sealing grooves are formed in the peripheral walls of the first pipe section and the second pipe section. According to the washing pump provided by the embodiment of the invention, a double-layer labyrinth sealing structure is formed, so that the working loss and the impeller volume loss are reduced; the balance of the running of the impeller is improved, and the abrasion is reduced. The impeller generates larger lift in a limited space.

Description

Washing pump and washing electric appliance with same

Technical Field

The invention relates to the field of fluid technical equipment, in particular to a washing pump and a washing electric appliance with the same.

Background

The washing pump is a core component of a washing electric appliance such as a dish washer, a washing machine and the like. The washing pump is responsible for the power source of the whole circulating waterway, and the performance index and the energy efficiency level of the washing pump directly influence visual feelings such as washing efficiency, energy consumption, vibration noise and the like. The impeller part is used for providing power for the fluid medium in the washing pump, the efficiency of the impeller part is comprehensively obtained by the hydraulic efficiency, the volumetric efficiency and the mechanical efficiency of the impeller, and the efficiency of the impeller part directly influences the performance index of the washing pump.

Because the outlet pressure of the impeller member is higher and the inlet pressure is lower, the pressure difference between the two causes the fluid medium to flow back from the impeller member outlet to the inlet of the impeller member through the annular gap between the front end of the impeller and the front wall of the pump body. The backflow flowing back from the annular gap merges with the main flow at the inlet, is driven by the impeller member again to flow to the outlet of the impeller member, where part of the fluid medium still flows back from the annular gap due to the existence of the inlet-outlet pressure difference.

Obviously, the existence of the backflow not only causes the dissipation of energy, but also causes larger volumetric loss of the washing pump, lower volumetric efficiency and influences the lift. Meanwhile, the backflow is generated by the pressure difference between the inlet and the outlet of the impeller part, the pressure difference between the inlet and the outlet of the impeller at different positions in the circumferential direction is changed, the pressure difference between the inlet and the outlet at the same position is also changed along with time, and the whole stress of the impeller part is unbalanced. In severe cases, the impeller may be eccentric even when rotating during operation of the washing pump, resulting in severe localized wear.

Disclosure of Invention

The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, the invention provides the washing pump which reduces the backflow of the annular gap of the fluid medium as much as possible, reduces the abrasion of the impeller and prolongs the service life.

The invention also aims at providing a washing electric appliance with the washing pump.

A washing pump according to an embodiment of the present invention includes: a pump housing assembly and an impeller. An impeller accommodating cavity is formed in the pump shell assembly, an inner inlet channel positioned at the front end of the impeller accommodating cavity is formed in the pump shell assembly, the inner inlet channel comprises a first channel section and a second channel section, the first channel section is positioned at the front side of the second channel section, and the diameter of the first channel section is smaller than that of the second channel section. The impeller includes: the rear cover plate is positioned in the impeller accommodating cavity; the hub is connected with the rear cover plate; the front cover plate is annular and is arranged around the axis of the hub, the front cover plate is positioned on the front side of the rear cover plate, the inner edge of the front cover plate is bent forwards to form a front end pipe, the front end pipe is at least partially matched in the inner inlet channel, the front end pipe comprises a first pipe section and a second pipe section, the first pipe section is positioned in the first channel section, the second pipe section is positioned in the second channel section, the outer diameter of the first pipe section is smaller than the outer diameter of the second pipe section, the outer diameter of the second pipe section is larger than the diameter of the first channel section, and front sealing grooves are formed in the peripheral walls of the first pipe section and the second pipe section; and the blade is connected between the front cover plate and the rear cover plate.

According to the washing pump provided by the embodiment of the invention, the assembly mode of the front end pipe and the inner inlet channel on the impeller forms a double-layer labyrinth sealing structure, so that on one hand, the leakage loss caused by backflow of the annular gap is reduced, the working loss is reduced, and the volume loss of the impeller is reduced; on the other hand, after the backflow is weakened, the running balance of the impeller is improved, and the abrasion is reduced. Therefore, the energy dissipation can be reduced, the volumetric efficiency of the washing pump can be improved, the drainage pressure can be increased, and the impeller can generate larger lift in a limited space.

In some embodiments, the front seal groove is an annular groove, or the front seal groove is a spiral groove.

Specifically, the front sealing groove is an annular groove, a plurality of front sealing grooves which are arranged in parallel are formed in the peripheral wall of the first pipe section, and a plurality of front sealing grooves which are arranged in parallel are formed in the peripheral wall of the second pipe section.

In some embodiments, a rear seat cavity is defined within the pump housing assembly, the rear seat cavity communicating with the rear end of the impeller receptacle; the impeller further comprises: the backseat ring is annular and surrounds the axis of wheel hub, the backseat ring is connected on the rear surface of back shroud, the backseat ring at least at the rear end cooperation in the backseat intracavity.

Specifically, a rear seal groove is formed in the peripheral wall of the rear seat ring.

Further, the back seal groove is a plurality of annular grooves, or the back seal groove is a spiral groove.

Further, the back cover plate is provided with a balance hole penetrating in the thickness direction.

Optionally, the balance hole satisfies at least one of the following conditions:

the diameter of the balance hole is 1-2mm;

The number of the balance holes is 3-6 which are arranged at intervals.

In some embodiments, a rear cover rib is provided on a rear surface of the rear cover plate, and the rear cover rib is disposed to extend radially along the impeller.

In some embodiments, the inner access passage further comprises a third passage section located on a front side of the first passage section, an end diameter of the third passage section adjacent to the first passage section being equal to or less than a front end inner diameter of the front end tube.

In some embodiments, the difference in radius of the second channel segment and the radius of the first channel segment is g1;

the difference between the radius of the first channel section and the radius of the first pipe section is g2;

the difference between the radius of the second channel section and the radius of the second pipe section is g3;

And satisfies the following: g1> g2, and g1> g3.

The washing appliance comprises the washing pump.

According to the washing electric appliance provided by the embodiment of the invention, the washing pump is high in volumetric efficiency, high in drainage pressure and sufficient in lift, and a stronger washing effect can be generated.

Additional aspects and advantages of the 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.

Drawings

The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is a cross-sectional view of a wash pump according to an embodiment of the invention;

FIG. 2 is a partial cross-sectional view of a wash pump according to an embodiment of the invention;

FIG. 3 is a side view of an impeller according to an embodiment of the present invention;

FIG. 4 is a front end view of an impeller of an embodiment of the present invention;

Fig. 5 is a structural view of a washing appliance provided with a washing pump.

Reference numerals:

Washing electric appliance A, washing pump B,

A pump housing assembly 1000,

A drainage pump casing 100,

A main pump case 200,

Impeller cavity 210,

An inner access passage 220, a first passage section 221, a second passage section 222, a third passage section 223,

A rear seat 270,

Diameter D1 of the first channel section, radius R1 of the first channel section, diameter D2 of the second channel section, radius R2 of the second channel section, rear end diameter D5 of the third channel section,

Impeller 300,

A central inlet 301, a circumferential outlet 302, a diameter D6 of the central inlet,

Hub 310, hub axis L,

A back cover plate 320,

Front cover plate 330, front end tube 331, first tube segment 3311, second tube segment 3312, front seal groove 3313, reducer 332, cone ring plate 333,

Diameter D3 of the first tube section, radius R3 of the first tube section, diameter D4 of the second tube section, radius R4 of the second tube section,

Blades 340,

A backseat ring 370, a backseat seal groove 371, a balance hole 372,

Rear end cap 400, mounting hole 409,

A drive motor 700, and a drive shaft 710.

Detailed Description

Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.

A washing pump B according to an embodiment of the present invention is described below with reference to fig. 1 to 4.

As shown in fig. 1, the washing pump B includes: a pump housing assembly 1000 and an impeller 300. An impeller receptacle 210 is formed in the pump housing assembly 1000, and an impeller 300 is disposed in the impeller receptacle 210.

Referring to fig. 1 and 2, the pump housing assembly 1000 is provided with an inner inlet passage 220 at the front end of the impeller housing 210, the inner inlet passage 220 including a first passage section 221 and a second passage section 222, the first passage section 221 being located at the front side of the second passage section 222, and a diameter D1 of the first passage section 221 being smaller than a diameter D2 of the second passage section 222.

In the present application, for convenience of description of the shape of the washing pump B, when the structural characteristics of the washing pump B are described, the reference orientation of the washing pump B is described with the axis of the washing pump B disposed in the front-rear direction and the inward channel 220 located at the front end of the impeller housing 210 as the reference orientation of the washing pump B, the reference orientation being a relative positional relationship. The structure of the impeller 300 is also described with reference to this reference orientation, in which the front cover plate 330 on the impeller 300 is the front cover plate, and the rear cover plate 320 is the rear cover plate, and reference herein to "front surface" and "rear surface" are also defined. Of course, when the actual product is assembled and used, the direction of the washing pump B can be adjusted according to the product requirement, and when the axis of the washing pump B is arranged in the left-right direction or other directions in the geographic position, the relative position relationship of the structures of the parts of the washing pump B is unchanged, so that the relative position relationship still accords with the position relationship under the reference direction.

The orientation or positional relationship shown in the drawings in the present application also corresponds to the above-described reference orientation, and thus in the description of the present application, the orientation or positional relationship indicated by the terms "front", "rear", "left", "right", "center", "upper", "lower", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. are based on the orientation or positional relationship shown in the drawings, merely for convenience of describing the present application and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus are not to be construed as limiting the present application. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present application, unless otherwise indicated, the meaning of "a plurality" is two or more.

In the present application, the axis of the impeller 300 is the axis of the washing pump B, and the axis L of the hub 10 is the axis of the impeller 300 in the impeller 300, so that the axis L of the hub 10 is disposed in the front-rear direction in the reference orientation. The inner and outer directions referred to herein mean directions toward the axis L are inward and directions away from the axis L are outward in the radial direction of the impeller 300. The inner edge of each cover plate referred to herein refers to the edge that is closer to the axis L, and the outer edge of each cover plate refers to the edge that is farther from the axis L.

Referring to fig. 3 to 4, the impeller 300 includes: hub 310, back cover plate 320, front cover plate 330 and blades 340, blades 340 being connected between front cover plate 330 and back cover plate 320.

The back cover plate 320 is positioned in the impeller housing 210, the back cover plate 320 is connected to the hub 310, and the front cover plate 330 is positioned on the front side of the back cover plate 320. The front cover plate 330 is annular and disposed about the axis L of the hub 310, the inner edge surrounding area of the front cover plate 330 being the central inlet 301 of the impeller 300, the outer edge of the front cover plate 330 and the outer edge of the rear cover plate 320 forming the circumferential outlet 302 of the impeller 300.

Wherein the inner edge of the front cover plate 330 is bent forward to form a front end tube 331, the front end tube 331 being at least partially fitted in the inner inlet passage 220. The front end pipe 331 includes a first pipe section 3311 and a second pipe section 3312, the first pipe section 3311 is located in the first channel section 221, the second pipe section 3312 is located in the second channel section 222, an outer diameter D3 of the first pipe section 3311 is smaller than an outer diameter D4 of the second pipe section 3312, an outer diameter D4 of the second pipe section 3312 is larger than a diameter D1 of the first channel section 221, and front seal grooves 3313 are formed in peripheral walls of the first pipe section 3311 and the second pipe section 3312.

In the present application, the washing pump B further includes a driving member (e.g., a driving motor 700 in fig. 1) that drives the entire impeller 300 to rotate about the axis L through the hub 310. When the impeller 300 rotates, the blades 340 push the fluid medium in the impeller 300 to rotate around the axis L, so that the fluid medium is centrifuged and is thrown radially from inside to outside. Since the central inlet 301 of the impeller 300 is located at the radially inner end of the impeller 300 and the circumferential outlet 302 of the impeller 300 is located at the radially outer end of the impeller 300, after the impeller 300 rotates, the pressure at the central inlet 301 drops and draws in more fluid medium and the pressure at the circumferential outlet 302 rises to discharge the fluid medium outwards.

Due to the continuous nature of the fluid medium, the fluid medium at the front side of the impeller 300 is continuously sucked into the impeller 300 from the central inlet 301, and the fluid medium is continuously discharged from the circumferential outlet 302, the discharged fluid medium obtains velocity energy and pressure energy, and the impeller 300 performs work on the fluid medium, so that the washing pump B has a certain lift. Here, the head refers to the increase in energy per unit weight of fluid medium from the inlet to the outlet of the pump, and the main volume is in the increase in pressure energy of the washing pump B of the present application.

It will be appreciated that the pressure at the central inlet 301 drops and the pressure at the circumferential outlet 302 rises, and that the pressure difference between the two will cause the fluid medium to flow from the circumferential outlet 302 from the front side of the front cover plate 330 towards the central inlet 301, creating an unnecessary backflow, called annular gap backflow, the direction of which is shown as p1 in fig. 2.

Since the pump housing assembly 1000 is in a stationary state when the impeller 300 rotates, a gap exists between the outer peripheral wall of the front end pipe 331 and the inner peripheral wall of the inner intake passage 220, and the existence of this gap inevitably results in the above-described backflow of the annular gap.

To reduce the occurrence of annular gap backflow, it is proposed in the present application that the diameter D1 of the front first channel section 221 is smaller than the diameter D2 of the rear second channel section 222 in the inner inlet channel 220. On the front end tube 331 of the impeller 300, the outer diameter D3 of the front first tube segment 3311 is smaller than the outer diameter D4 of the rear second tube segment 3312, and the first tube segment 3311 is located within the first channel segment 221 and the second tube segment 3312 is located within the second channel segment 222. This arrangement facilitates assembly of the impeller 300 from back to front with the inner intake passage 220.

And the outer diameter D4 of the second tube segment 3312 is larger than the diameter D1 of the first passage segment 221 so that, as can be seen from the cross section shown in fig. 2, the gap formed between the outer peripheral wall of the front end tube 331 of the impeller 300 and the inner peripheral wall of the inner intake passage 220 is zigzag in cross section. On the basis, front seal grooves 3313 are formed in the outer peripheral walls of the first pipe section 3311 and the second pipe section 3312. Thereby, a double-layered labyrinth seal is formed between the outer peripheral wall of the front end tube 331 and the inner peripheral wall of the inner inlet passage 220.

Taking fig. 2 as an example, when the fluid medium flows from the circumferential outlet 302 to the center inlet 301 in the backflow direction shown by p1, the fluid medium flows first to the gap between the outer peripheral wall of the second tube segment 3312 and the inner peripheral wall of the second passage segment 222. When the fluid medium flows into the gap c1 outside the second tube segment 3312, the fluid medium is rapidly compressed due to the volume reduction. When the flow continues, the fluid medium enters the gap c2 before the gap c1, and the volume of the gap c2 increases relative to the gap c1 to form the front seal groove 3313, so that the fluid medium rapidly expands due to the volume increase. When the flow continues, the fluid medium enters the gap c3 before the gap c2, and the fluid medium is rapidly compressed due to the volume reduction. Such that the fluid medium repeatedly undergoes the process of compression and expansion outside of the second tube segment 3312, increasing the flow resistance of the fluid medium. Also, when the fluid medium flows to the gap between the outer circumferential wall of the first tube segment 3311 and the inner circumferential wall of the first passage segment 221, the fluid medium also repeatedly undergoes the processes of compression and expansion outside the first tube segment 3311, further increasing the flow resistance of the fluid medium.

In particular, the fluid medium encounters a step when flowing forward at the junction of the first channel section 221 and the second channel section 222, so that the flow is blocked, and the flowing direction needs to be turned. The turn corresponds to the formation of a barrier where the fluid medium needs to overcome a large flow resistance from back to front, and where the fluid medium needs to overcome a large flow resistance from the barrier to front to the central inlet 301. The pressure difference between the barrier and the central inlet 301 is greatly reduced, so that the dynamic force of the fluid medium from the barrier to the central inlet 301 is greatly reduced, and the backflow of the annular gap is effectively reduced.

It will be appreciated that the annular gap backflow is more random to occur before the double labyrinth seal is provided, and therefore the backflow distribution is not uniform in the circumferential direction, which tends to unbalance the forces on the impeller 300. By reducing or even blocking the backflow of the annular gap, the stress of the impeller 300 is more balanced, and the probability of axis deflection during the operation of the impeller 300 is reduced. After the stress balance of the impeller 300 is promoted, the eccentric wear probability of the impeller 300 can be reduced, the performance reduction and damage risk caused by eccentric wear are reduced, and the service life of the impeller 300 is prolonged.

In conclusion, due to the arrangement of the double-layer labyrinth seal, on one hand, leakage loss caused by backflow of an annular gap (shown as an arrow p1 in fig. 2) is reduced, working loss is reduced, and impeller volume loss is reduced; on the other hand, after the backflow is weakened, the running balance of the impeller 300 is improved, and the abrasion is reduced. Thus, the energy dissipation can be reduced, the volumetric efficiency of the washing pump B can be improved, the drainage pressure can be increased, and the impeller 300 can generate a larger lift in a limited space.

In some embodiments, the difference between the radius R2 of the second channel segment 222 and the radius R1 of the first channel segment 221 is g1, r2=1/2×d2, r1=1/2×d1, g1=1/2×d1 (D2-D1). I.e. the step formed at the junction of the first channel segment 221 and the second channel segment 222, which step has a width g1.

Specifically, the difference between the radius R1 of the first channel segment 221 and the radius R3 of the first tube segment 3311 is g2, where r3=1/2×d3. I.e. the outer circumferential wall of the first tube segment 3311 and the inner circumferential wall of the first channel segment 221, forms a gap having a width g2, g1> g2. That is, the gap width between the outer peripheral wall of the first tube section 3311 and the inner peripheral wall of the first passage section 221 is controlled to be smaller than the step width between the first passage section 221 and the second passage section 222. By the arrangement, the volume is effectively compressed when the fluid medium enters the gap, and a large degree of energy consumption is formed.

Further, the difference between the radius R2 of the second channel segment 222 and the radius R4 of the second tube segment 3312 is g3, where r4=1/2×d4. I.e. the outer circumferential wall of the second tube segment 3312 and the inner circumferential wall of the second channel segment 222, a gap having a width g3, g1> g3. That is, the gap width between the outer peripheral wall of the second pipe section 3312 and the inner peripheral wall of the second passage section 222 is controlled to be smaller than the step width between the first passage section 221 and the second passage section 222. By the arrangement, the volume is effectively compressed when the fluid medium enters the gap, and a large degree of energy consumption is formed. And the flow direction of the fluid medium entering the gap is forward, and the step is just in front of the gap, so that the flow of the fluid medium is effectively blocked.

In the present embodiment, the outer peripheral wall of the first pipe section 3311 may be a cylindrical surface or may have a certain taper. The outer peripheral wall of the second tube segment 3312 may be cylindrical or may have a taper. The inner peripheral wall of the first channel section 221 may be cylindrical or tapered. The inner peripheral wall of the second channel segment 222 may be cylindrical or tapered.

In the present application, the shape of the front seal groove 3313 is not limited, and the front seal groove 3313 may be an annular groove, the front seal groove 3313 may be a spiral groove, and the front seal groove 3313 may be other shapes. Or the front seal groove 3313 may be an arc-shaped groove or the like.

Optionally, the first tube segment 3311 is provided with one or more front seal grooves 3313 and the second tube segment 3312 is provided with one or more front seal grooves 3313.

In some embodiments, as shown in fig. 2 and 3, the front seal groove 3313 is an annular groove, a plurality of front seal grooves 3313 are arranged in parallel on the outer peripheral wall of the first pipe section 3311, and a plurality of front seal grooves 3313 are arranged in parallel on the outer peripheral wall of the second pipe section 3312. By the arrangement, the arrangement of the front seal grooves 3313 can be compact, the number of times that the fluid medium is subjected to compression-expansion is increased, and the flow resistance is effectively increased.

Specifically, the front seal groove 3313 is circular and regular in shape, and is convenient to process.

In some embodiments, as shown in fig. 1 and 2, the inner access passage 220 further includes a third passage section 223, the third passage section 223 being located on a front side of the first passage section 221, an end diameter D5 of the third passage section 223 adjacent to the first passage section 221 being equal to or less than a front end inner diameter D6 of the front end tube 331. That is, the third passage section 223 has a diameter D5 at an end facing the impeller 300 that is smaller than the diameter D6 of the central inlet 301.

The fluid medium flows into the central inlet 301 from the third channel section 223, and the diameter D5 of the third channel section 223 at the end facing the impeller 300 is set smaller than the diameter D6 of the central inlet 301, so that the fluid medium is centralized and guided to the central inlet 301, turbulence generated at the edge of the front end of the impeller 300 is reduced, and the fluid medium loss is reduced.

In the present embodiment, the third channel section 223 faces the center inlet 301 of the impeller 300 according to the characteristics of the washing pump B, so that the fluid medium flows axially toward the impeller 300.

The shape of the third channel segment 223 in a cross section perpendicular to the axis L may be circular or nearly circular. The vertical cross-sectional shape of the third passage section 223 may or may not be the same throughout the axis L, where the vertical cross-section refers to a cross-section perpendicular to the axis L. For example, the third channel section 223 may be oval in shape at the front end and the third channel section 223 may be circular in shape at the rear end. Preferably, the vertical cross-sectional shape of the third passage section 223 is circular throughout the axis L.

Alternatively, the vertical cross-sectional dimensions of the third passage section 223 may be the same or different throughout the axis L. Further alternatively, the third channel section 223 may vary along a regular pattern when the vertical cross-sectional size varies throughout. For example, the third channel segment 223 is a straight channel. As another example, the third channel segment 223 is a tapered channel that gradually decreases in diameter from front to back. At this time, since the flow rate of the fluid medium flowing into the third passage section 223 is stable, the section of the third passage section 223 is gradually reduced backward to have an effect of accelerating the flow rate, thereby improving the acceleration of the impeller 300. For another example, the third channel segment 223 is a diverging channel with a gradually increasing diameter from front to back. Such a configuration of the third passage section 223 may act to slow the flow rate when the flow into the third passage section 223 is excessive.

In some embodiments, the pump housing assembly 1000 further includes a fairing rib disposed within the third channel section 223. It can be appreciated that the rectifying ribs can reduce the swirling flow of the fluid medium in the third channel section 223, ensure that the fluid medium can flow into the impeller 300 from the central inlet 301 of the impeller 300 along the axial direction, reduce the hydraulic loss of the fluid medium caused by the swirling flow, and improve the driving effect of the impeller 300 on the fluid medium, thereby improving the flow efficiency.

In the present application, the arrangement mode of the rectifying rib is not limited, and the structure of the rectifying rib needs to have a blocking effect on the fluid medium flowing in the radial direction of the third channel section 223, and does not generate a blocking effect on the fluid medium flowing in the axial direction of the third channel section 223. For example, the rectifying ribs are provided as cross partitions extending in the axial direction. For another example, the rectifying ribs may be cross partitions in a "well" shape or mesh partitions. Alternatively, the rectifying rib may be cross-shaped or in-line, and the rectifying rib may be in other shapes, which is not limited herein.

In some embodiments, as shown in fig. 3, the front cover plate 330 includes: a front end tube 331, a reducer tube 332, and a cone ring plate 333. The front tube 331 is extended in the front-rear direction, and the front tube orifice of the front tube 331 is the center inlet 301. The front end of the reducer 332 is connected to the rear end of the front end tube 331, and the diameter of the reducer 332 gradually increases from front to rear. The cone ring plate 333 is arranged opposite to the back cover plate 320, the inner edge of the cone ring plate 333 is connected with the back end of the reducer 332, and a circumferential outlet 302 is arranged between the outer edge of the cone ring plate 333 and the outer edge of the back cover plate 320.

The front cover 330 is tubular at the front end, e.g., the front tube 331 may be a circular tube. This facilitates control of the gap between the front cover plate 330 and the inner peripheral wall of the inner access passage 220 when assembled.

The conical ring plate 333 is shaped closer to the plate body, so that the conical ring plate is conveniently matched with the rear cover plate 320 to define the circumferential outlet 302, the circumferential outlet 302 is formed on the outer circumferential surface of the impeller 300, so that fluid medium can be discharged along the circumferential direction, and the overall acting force of the fluid medium on the impeller 300 is balanced in the circumferential direction during discharging.

The reducer 332 is provided in that it is a transition structure between the nose tube 331 and the cone-ring plate 33. By gradually increasing the diameter of the reducer 332 from front to back, the reducer 332 can guide the fluid medium to flow more smoothly, reduce the disturbance generated by the fluid medium during reversing, and reduce the flow resistance and power consumption.

Specifically, the distance between the cone ring plate 333 and the back cover plate 320 gradually decreases in the inside-to-outside direction so that the circumferential outlet 302 is formed as a constriction. So that the energy carried by the fluid medium can be converted into a greater head of water as it flows to the circumferential outlet 302 due to the elevated flow rate.

Further, the front end tube 331, the reducer 332 and the conical ring 333 are integrally formed, so that the front end tube 331, the reducer 332 and the conical ring 333 have high structural strength at the joint, relatively low internal stress, high pressure bearing capability, and difficult breakage and leakage.

In some embodiments, a back housing cavity 270 is defined within the pump housing assembly 1000 as shown in fig. 1 and 2, the back housing cavity 270 communicating with the rear end of the impeller housing 210. The provision of the rear housing 270 provides sufficient assembly space and rotational space for the hub 310 and the drive shaft 710 coupled to the hub 310, reducing unnecessary wear.

Specifically, the impeller 300 further includes: a rear ring 370, the rear ring 370 being annular and disposed about the axis L of the hub 310, the rear ring 370 being attached to the rear surface of the rear cover plate 320, the rear ring 370 fitting at least at the rear end into the rear housing 270. The provision of the back seat ring 370 enables the back seat cavity 270 to be substantially isolated from the impeller receptacle 210, reducing the flow of fluid medium discharged from the circumferential outlet 302 into the back seat cavity 270.

It will be appreciated that when the drive shaft 710 is assembled to the pump housing assembly 1000, a seal may be provided at the mounting hole 409, and the mounting hole 409 may be filled with a material such as lubricating oil. By providing the backseat ring 370 to separate the backseat cavity 270 from the impeller housing 210, the problem of leakage caused by squeezing fluid medium into the mounting hole 409 is reduced, as well as pollution.

Further, as shown in fig. 2 and 3, the peripheral wall of the backseat ring 370 is provided with a backseat groove 371, and the backseat groove 371 is provided to form a sealing structure. Thus, when the fluid medium discharged from the circumferential outlet 302 enters the gap between the outer circumferential wall of the back ring 370 and the inner circumferential wall of the back chamber 270, the fluid medium flows into the gap j1, and the fluid medium is rapidly compressed due to the volume reduction. The fluid medium flows back into the gap j2, and the fluid medium expands rapidly due to the volume increase. The fluid medium flows back into the gap j3 again, and the fluid medium is rapidly compressed due to the volume reduction. The repeated compression and expansion of the fluid medium increases the flow resistance of the fluid medium, thereby effectively reducing the flow from the circumferential outlet 302 to the fitting hole 409.

In the present embodiment, the shape of the back seal groove 371 is not limited, the back seal groove 371 may be an annular groove, the back seal groove 371 may be a spiral groove, and the back seal groove 371 may be other shapes. Or the rear seal groove 371 is an arc-shaped groove or the like.

Optionally, one or more backseal grooves 371 may be provided on the backseat ring 370.

In some embodiments, rear cover ribs (not shown) are provided on the rear surface of the rear cover plate 320, and the rear cover ribs extend radially along the impeller 300. The arrangement of the rear cover rib can further increase the stress balance of the impeller 300.

Specifically, as impeller 300 rotates, the rear shroud rib pushes the fluid medium around axis L, causing the fluid medium to be centrifuged and to be thrown radially from inside to outside. The driving of the rear cover rib enables the fluid medium to obtain speed energy and pressure energy. The energy carried by this portion of the fluid medium can also be converted to a head of water and the fluid medium exiting the circumferential outlet 302 merges, increasing the effective head of the impeller 300. That is to say, the arrangement of the rear cover rib prevents the leakage loss caused by the backflow of the flowing medium and reduces the working loss; on the other hand, the rear cover rib can do work on the fluid medium. Therefore, the arrangement of the rear cover rib can also reduce energy dissipation, improve the volumetric efficiency of the washing pump B, increase the drainage pressure and enable the impeller 300 to generate larger lift in a limited space.

When the rear cover rib is arranged on the impeller 300, the fluid medium driven by the rear cover rib to rotate can generate forward supporting force on the impeller 300, so that the stress of the impeller 300 is balanced in the circumferential direction, and the eccentric wear probability of the impeller 300 is reduced.

In some embodiments, as shown in fig. 1 and 2, the back cover 320 is provided with a balance hole 372 penetrating in a thickness direction, and the balance hole 372 is disposed adjacent to the axis L of the hub 310. The balance holes 372 are provided to facilitate the flow of fluid medium from the balance holes 372 into the impeller 300 within the back seat cavity 270.

It will be appreciated that in impeller 300, as blades 340 perform work, the flowing medium is continually flowing from the radially inner end to the radially outer end, resulting in a low pressure at the radially inner end and a high pressure at the radially outer end of impeller 300. When the pressure of the rear side of the impeller 300 is high, the fluid medium can enter the impeller 300 through the balance hole 372, and is sent to the low compression position and then is pressed out by the rotation of the blades 340. Thus, when the high-pressure fluid flows to the back of the impeller 300 from the circumferential outlet 302, the fluid can flow back into the impeller 300 through the balance hole 372, so that the extrusion to the assembly hole 407 is reduced.

The balance holes 372 help to further balance the forces on the impeller 300, and reduce wear of the impeller 300 by the support of the flowing medium.

In the present embodiment, the shape of the balance hole 372 may be a circular hole, a square hole, an irregularly shaped hole, etc., without limitation.

When the balance hole 372 is a circular hole, the diameter of the balance hole 372 is optionally 1-2mm, so that the purpose of fluid medium backflow can be achieved without excessively affecting the operation of the impeller 300.

Further alternatively, balance holes 372 are 3-6 spaced apart. The scattered arrangement ensures that the backflow can be realized, and meanwhile, too many holes on the impeller 300 are avoided, so that the structural strength of the impeller 300 is ensured.

In one embodiment, balance holes 372 are 3 to 6 in number and 1 to 2mm in size in outer diameter at the junction of front cover plate 330 and the interior of blade 340.

In some embodiments, as shown in FIG. 1, a pump housing assembly 1000 includes: a main pump housing 200 and a drainage pump housing 100. The main pump case 200 defines therein an impeller receiving chamber 210, one end of the main pump case 200 is provided with an inner inlet passage 220, the impeller receiving chamber 210 is used for mounting an impeller 300, and a central inlet 301 of the impeller 300 is disposed toward the inner inlet passage 220. The drainage pump housing 100 is for introducing a fluid medium, and is connected to the front end of the main pump housing 200.

It will be appreciated that the acceleration effect of the impeller 300 on the water flow is affected by the stability of the water flow flowing into the impeller 300, when the speed of the water flow flowing into the impeller 300 is unstable, the pressure of the water flow received by the impeller 300 at different positions is different, and the pressure difference received by the impeller 300 may generate resistance to the rotation of the impeller 300, so as to affect the acceleration effect of the impeller 300 on the water flow, and meanwhile, the pressure difference may also cause the impeller 300 to vibrate during rotation, so as to increase the noise of the rotation of the impeller 300.

A drainage structure (not shown) can be arranged in the drainage pump shell 100 to guide the fluid medium to flow to the impeller along the axial direction, so that the fluid medium flows more stably, the pressure difference received by the impeller 300 during rotation can be reduced, the driving effect of the impeller 300 on water flow is improved, the flow efficiency of the water flow in the pump shell assembly 1000 is ensured, meanwhile, the vibration generated by rotation of the impeller 300 can be reduced, and the vibration and noise generated by the operation of the pump shell assembly 1000 are reduced.

In some embodiments, wash pump B further comprises: a heater provided within the drainage pump housing 100. The water flow is thereby heated before entering the impeller 300, and the water flow is thoroughly stirred as it flows through the impeller 300, so that the water temperature is gradually uniform. The heater is arranged on the drainage pump shell 100, so that the space of the subsequent pipeline is not occupied, and the space of the drainage pump shell 100 is fully utilized. The water flow in the drainage pump shell 100 is subjected to steering, and the flow distance of the water flow is prolonged through the drainage structure, so that the water flow can fully absorb the heat of the heater, and the heat exchange rate is improved.

Further, the washing pump B further includes a driving motor 700, the driving motor 700 is mounted on the pump housing assembly 1000, and a driving shaft 710 of the driving motor 700 is connected to the impeller 300.

Still further, the pump housing assembly 1000 includes: and a rear end cap 400 disposed at the rear end of the main pump casing 200 for closing the impeller housing 210. Specifically, the rear cover 400 is provided with an assembly hole 409 to assemble the drive shaft 710. More specifically, the driving motor 700 is mounted on the rear cover 400, improving the integration.

A washing appliance a according to an embodiment of the present invention is described below with reference to fig. 1 to 5.

The washing electric appliance a is internally provided with a washing pump, and the washing pump is the washing pump B described in the above embodiment, and the structure of the washing pump B will not be described again here.

According to the washing electric appliance A provided by the embodiment of the invention, the washing pump B is arranged, so that the washing effect is improved, the energy consumption is reduced, and the vibration and the noise are reduced.

Specifically, the washing appliance a may be a dishwasher, a washing machine, or the like, or may be other devices that require a washing pump B, which is not limited herein. The washing electric appliance A has good integral washing effect and long service life.

Other constructions and operations of the dish washer and the washing machine according to the embodiments of the present invention are known to those of ordinary skill in the art, and will not be described in detail herein.

In the description herein, reference to the term "embodiment," "example," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.

Claims (12)

1. A wash pump, comprising:

the impeller comprises a pump shell assembly, wherein an impeller accommodating cavity is formed in the pump shell assembly, an inner inlet channel positioned at the front end of the impeller accommodating cavity is formed in the pump shell assembly, the inner inlet channel comprises a first channel section and a second channel section, the first channel section is positioned at the front side of the second channel section, and the diameter of the first channel section is smaller than that of the second channel section;

An impeller, the impeller comprising:

The rear cover plate is positioned in the impeller accommodating cavity;

The hub is connected with the rear cover plate;

The front cover plate is annular and is arranged around the axis of the hub, the front cover plate is positioned on the front side of the rear cover plate, the inner edge of the front cover plate is bent forwards to form a front end pipe, the front end pipe is at least partially matched in the inner inlet channel, the front end pipe comprises a first pipe section and a second pipe section, the first pipe section is positioned in the first channel section, the second pipe section is positioned in the second channel section, the outer diameter of the first pipe section is smaller than the outer diameter of the second pipe section, the outer diameter of the second pipe section is larger than the diameter of the first channel section, and front sealing grooves are formed in the peripheral walls of the first pipe section and the second pipe section;

And the blade is connected between the front cover plate and the rear cover plate.

2. The wash pump of claim 1, wherein the front seal groove is an annular groove or the front seal groove is a spiral groove.

3. The washing pump of claim 2 wherein said front seal groove is an annular groove, a plurality of said front seal grooves arranged in parallel are provided on the outer peripheral wall of said first tube section, and a plurality of said front seal grooves arranged in parallel are provided on the outer peripheral wall of said second tube section.

4. The washing pump of claim 1, wherein,

A rear seat cavity is defined in the pump shell assembly and is communicated with the rear end of the impeller accommodating cavity;

The impeller further comprises: the backseat ring is annular and surrounds the axis of wheel hub, the backseat ring is connected on the rear surface of back shroud, the backseat ring at least at the rear end cooperation in the backseat intracavity.

5. The washing pump as claimed in claim 4 wherein a rear seal groove is provided on an outer peripheral wall of the rear seat ring.

6. The wash pump of claim 5, wherein the back seal groove is a plurality of annular grooves or the back seal groove is a spiral groove.

7. The washing pump as claimed in claim 4 wherein said back cover plate is provided with a balancing hole penetrating in a thickness direction, said balancing hole being disposed adjacent to an axis of said hub.

8. The wash pump of claim 7, wherein the balance aperture satisfies at least one of the following conditions:

the diameter of the balance hole is 1-2mm;

The number of the balance holes is 3-6 which are arranged at intervals.

9. The washing pump as claimed in claim 1 wherein a rear shroud rib is provided on a rear surface of the rear shroud, the rear shroud rib extending radially from the impeller.

10. The wash pump of any of claims 1-9, wherein the inward channel further comprises a third channel segment, the third channel segment being located on a front side of the first channel segment, an end of the third channel segment adjacent the first channel segment having a diameter that is less than or equal to a front end inner diameter of the front end tube.

11. The washing pump of any one of claims 1-9 wherein the difference in radius of the second channel section and the first channel section is g1;

the difference between the radius of the first channel section and the radius of the first pipe section is g2;

the difference between the radius of the second channel section and the radius of the second pipe section is g3;

g1> g2, and g1> g3.

12. A washing appliance comprising a washing pump according to any one of claims 1-11.