CN117432653A - Impeller, washing pump and washing electric appliance with same - Google Patents

Abstract

The invention discloses an impeller, a washing pump and a washing electric appliance with the same. The impeller comprises: hub, back shroud, front shroud, blade and front shroud rib. The front surface of the front cover plate is provided with front cover ribs which extend along the radial direction of the impeller. According to the impeller provided by the embodiment of the invention, 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. And the front cover ribs are beneficial to promoting the stress balance of the impeller, reducing the eccentric wear probability of the impeller, reducing the performance reduction and damage risk caused by eccentric wear, and prolonging the service life of the impeller.

Description

Impeller, washing pump and washing electric appliance with same

Technical Field

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

Background

The washing pump is a core component of a washing appliance such as a dish washer. Taking a dish washer as an example, the dish washer is driven by electricity, uses water or mixed washing liquid as a main medium, washes and dries household tableware such as bowls, dishes, cups, spoons and the like, and can be safely operated without professional training. The dishwasher has great advantages in the aspects of releasing hands, saving energy, protecting environment, washing, sterilizing and the like.

The washing pump is a main power source of a circulating waterway in the whole dish-washing machine, and the performance index and the energy efficiency level of the washing pump directly influence the visual feelings of the dish-washing machine, such as washing efficiency, energy consumption, vibration noise and the like.

The impeller components are used for providing power for the fluid medium in the washing pump, and the lift and the running efficiency generated by the impeller components directly influence the performance index of the washing pump. The space available for installing the impeller components in the washing pump is limited, so that the impeller needs to generate a lift as large as possible in the limited space.

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 impeller of the washing pump can reduce the backflow of a fluid medium when the impeller rotates, so that the volume loss of the impeller is reduced, the lift of the washing pump is increased, the abrasion of the impeller is reduced, and the service life is prolonged.

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

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

An impeller of a washing pump according to an embodiment of the present invention includes: a hub; the rear cover plate is connected with the hub; a front cover plate which 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, an inner edge surrounding part of the front cover plate is formed into a central inlet of the impeller, and a circumferential outlet of the impeller is formed between the outer edge of the front cover plate and the outer edge of the rear cover plate; the blade is connected between the front cover plate and the rear cover plate; the front cover rib is arranged on the front surface of the front cover plate, and the front cover rib extends along the radial direction of the impeller.

According to the impeller of the washing pump, the front cover ribs are arranged on the front surface of the front cover plate and extend along the radial direction of the impeller, so that leakage loss caused by backflow of fluid medium on the front side of the front cover plate is prevented, and the front cover ribs can apply work to the front side fluid medium. 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. And the front cover ribs are beneficial to promoting the stress balance of the impeller, reducing the eccentric wear probability of the impeller, reducing the performance reduction and damage risk caused by eccentric wear, and prolonging the service life of the impeller.

In some embodiments, the front cover bead is perpendicular to the axis of the hub, or the front cover bead is disposed helically extending about the axis of the hub.

In some embodiments, the front cover plate includes: the front end pipe extends along the front-back direction, and the front end pipe orifice of the front end pipe is the central inlet; the front end of the reducing pipe is connected with the rear end of the front end pipe, and the diameter of the reducing pipe is gradually increased from front to back; the cone ring plate is arranged opposite to the rear cover plate, the inner edge of the cone ring plate is connected with the rear end of the reducer pipe, the circumferential outlet is formed between the outer edge of the cone ring plate and the outer edge of the rear cover plate, and the distance between the cone ring plate and the rear cover plate in the direction from inside to outside is gradually reduced so that the circumferential outlet is formed into a necking.

Specifically, the front cover rib is located on the front surface of the conical ring plate.

In some embodiments, the impeller of the washing pump further comprises: and the rear cover rib is arranged on the rear surface of the rear cover plate, and the rear cover rib extends along the radial direction of the impeller.

In some embodiments, the rear cover bead is perpendicular to the axis of the hub, or the rear cover bead is disposed helically extending about the axis of the hub.

Optionally, the wheel hub with the back shroud is integrated into one piece, the one end of back shroud rib with the outward flange parallel and level of back shroud, back shroud rib connects wheel hub and along keeping away from the direction setting of center import.

Further, the blades are multiple and are distributed at intervals along the circumferential direction, and the front cover ribs and the rear cover ribs are multiple and are equal to the blades in number respectively.

A washing pump according to an embodiment of the present invention includes: the impeller comprises a pump shell assembly, wherein an impeller accommodating cavity is formed in the pump shell assembly; the impeller is the impeller in the embodiment, and the impeller is arranged in the impeller accommodating cavity; the inner wall surface of the impeller containing cavity comprises a wheel rear wall surface and a wheel front wall surface, the wheel rear wall surface is located at the rear side of the rear cover plate and is spaced from the rear cover plate, and the wheel front wall surface is located at the front side of the front cover plate and is spaced from the front cover ribs.

According to the washing pump provided by the embodiment of the invention, the front cover ribs are arranged on the front surface of the impeller and extend along the radial direction of the impeller, so that leakage loss caused by backflow of fluid medium on the front side is prevented, and the front cover ribs can apply work to the front side fluid medium. Therefore, the energy dissipation can be reduced, the volumetric efficiency of the washing pump can be improved, the drainage pressure can be increased, and a larger lift can be generated. And the front cover ribs are beneficial to promoting the stress balance of the impeller, reducing the eccentric wear probability of the impeller, reducing the performance reduction and damage risk caused by eccentric wear, and prolonging the service life of the washing pump.

Specifically, the axial distance between the front cover rib and the wheel front wall surface is 1-3mm.

Further, when the impeller further comprises a rear cover rib, the rear cover rib is arranged on the rear surface of the rear cover plate, the rear wall surface of the impeller is spaced from the rear cover rib, and the axial distance between the rear cover rib and the rear wall surface of the impeller is 1-3mm.

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. And the front cover ribs are beneficial to promoting the stress balance of the impeller, reducing the eccentric wear probability of the impeller and prolonging the service life of the washing pump, so that the washing effect of the washing electric appliance can be enhanced.

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 perspective view of an impeller according to an embodiment of the present invention;

FIG. 2 is a side view of an impeller according to an embodiment of the present invention;

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

FIG. 4 is a bottom view of an impeller according to an embodiment of the invention;

FIG. 5 is a partial cross-sectional view of a wash pump according to an embodiment of the invention;

fig. 6 is a washing appliance provided with a washing pump.

Reference numerals:

impeller 300, central inlet 301, circumferential outlet 302,

Hub 310,

A back cover plate 320,

Front cover plate 330, front end tube 331, reducer tube 332, conical ring plate 333,

Blade 340, front cover rib 350, rear cover rib 360,

Pump housing assembly 400, rear wheel wall f1, front wheel wall f2, intake guide tube wall f3, impeller receptacle V1,

An axial distance d1 between the front cover rib and the wheel front wall surface, an axial distance d2 between the rear cover rib and the wheel rear wall surface, a wheel front clearance c1, a wheel rear clearance c2, an assembly hole 409,

A back flow direction p1, a front cover rib driving flow direction p2,

A washing pump 1000, a transmission shaft 110 and a washing electric appliance A.

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.

An impeller 300 of a washing pump according to an embodiment of the present invention is described below with reference to fig. 1 to 5.

As shown in fig. 1 and 2, an impeller 300 of a washing pump according to an embodiment of the present invention 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.

Rear cover plate 320 is coupled to hub 310 and front cover plate 330 is positioned on the front side of rear 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.

In the description of the present invention, it should be understood that the terms "center," "upper," "lower," "front," "rear," "top," "bottom," "inner," "outer," "axial," "radial," "circumferential," and the like indicate or are based on the orientation or positional relationship shown in the drawings, merely to facilitate description of the invention and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be configured and operated in a particular orientation, and thus should not be construed as limiting the invention.

In this application, the axis L of the hub 10 is the axis of the impeller 300, and the inner and outer directions mentioned herein refer to the directions of the impeller 300 in the radial direction, the direction approaching the axis L, and the direction away from the axis L. 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.

In the description of the structural features of the impeller 300 for convenience of description of the shape of the impeller 300, the impeller axis is disposed along the front-rear direction, and the center inlet 301 is located at the front end as a reference orientation of the impeller 300, in this reference orientation, the cover plate located at the front side on the impeller 300 is the front cover plate 330, the cover plate located at the rear side is the rear cover plate 320, and the references to "front surface" and "rear surface" herein are also defined in reference orientation. Of course, when the impeller 300 is assembled and used in actual products, the direction of the impeller 300 can be adjusted according to the needs of the products, and when the impeller axis is arranged in the left-right direction or in other directions, the positional relationship of the structures of each part of the impeller 300 still corresponds to the reference orientation, so the reference orientation will be described hereinafter.

In this application, the impeller 300 is connected to a driving member (e.g., a motor) of the washing pump 1000 through the hub 310, and the driving member drives the entire impeller 300 to rotate around 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 3 work 02, 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 1000 provided with the impeller 300 has a certain lift. Here, the head refers to the increase in energy per unit weight of fluid medium from the pump inlet to the outlet, and the main volume is in the pressure energy increase of such a wash pump 1000 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 back flow, the direction of which is shown as p1 in fig. 2.

For ease of understanding, the structure of impeller 300 in wash pump 1000 is further described herein with reference to fig. 5. In fig. 5, the impeller 300 is positioned in the pump casing assembly 400, and the front wheel wall surface f2 of the inner wall surface of the pump casing assembly 400 is positioned on the front side of the impeller 300. To avoid scraping the front wheel wall f2 when the impeller 300 rotates, the front surface of the front cover 330 is generally spaced apart from the front wheel wall f2 to form a front wheel gap c1. Typically, the pre-wheel gap c1 is also annular, and when the pressure at the circumferential outlet 302 is higher than at the central inlet 301, a portion of the fluid medium exiting the circumferential outlet 302 may flow back along the pre-wheel gap c1 to the central inlet 301.

In order to alleviate the problem of backflow, it is generally achieved by reducing the wheel front clearance c1, for example, by reducing the distance between the entire front surface of the front cover plate 330 and the wheel front wall surface f2, or by providing an annular rib on the front surface of the front cover plate 330, the annular rib being in the shape of a ring coaxial with the axis L. However, the two solutions are essentially the same, only the distance between the front side or part of the front side of the impeller 300 and the front wall surface f2 of the impeller is reduced, and the backflow cannot be completely blocked, and the existence of the backflow generates impact force to the impeller 300, so that the loss is used as a functional quantity. Moreover, if the front side of the impeller 300 is too close to the front wall f2, even if there is no backflow, the impeller 300 will deflect slightly from its axis L due to the impact of the water flow on the impeller 300 during normal operation, resulting in unnecessary friction between the impeller 300 and the pump housing assembly 400 and excessive energy loss.

To solve the above problem, it is proposed that the impeller 300 further includes a front cover rib 350, the front cover rib 350 is disposed on the front surface of the front cover plate 330, and the front cover rib 350 extends radially along the impeller 300.

Since the front cover rib 350 is no longer circular, when the impeller 300 rotates, the front cover rib 350 pushes the fluid medium in the front wheel gap c1 to rotate around the axis L, so that the fluid medium is centrifuged and flicked radially from inside to outside. The pressure at the radially inner end of the front cover bead 350 drops and draws in more fluid medium within the wheel forward gap c1, and the pressure at the radially outer end of the front cover bead 350 rises to expel fluid medium outwardly, the direction of flow being shown as p2 in fig. 2. Due to the continuous nature of the fluid medium, the fluid medium on the front side of the impeller 300 is continuously sucked into the front wheel gap c1, and the fluid medium is continuously discharged from the outer end of the front wheel gap c1, and the discharged fluid medium also obtains velocity energy and pressure energy. The energy carried by this portion of the fluid medium is 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, the arrangement of the front cover rib 350 in the present application prevents leakage loss caused by backflow in the wheel front gap c1 (as shown by arrow p1 in fig. 2), and reduces work loss; on the other hand, the front cover rib 350 can apply work to the fluid medium in the front wheel gap c1. The provision of the front shroud rib 350 thus reduces energy dissipation, increases volumetric efficiency of the washer pump 1000, increases drainage pressure, and causes the impeller 300 to generate a greater head in a limited space.

In addition, when the front cover rib 350 is provided on the impeller 300, the flow direction of the fluid medium on the front and rear surfaces of the front cover 330 is consistent when the impeller 300 rotates, and the fluid medium on the front and rear surfaces can generate backward pressure on the impeller 300 when flowing, so that the probability that the impeller 300 is attached to the front wall f2 of the impeller forwards is reduced.

The inventor group applied various types of impellers 300 to the washing pump 1000 to perform a comparative experiment, and the drain pressure of the washing pump 1000 was increased when the front cover rib 350 was provided with respect to the front cover rib 350 not provided. Some types of impellers 300 are provided with the front cover rib 350, so that the drainage pressure of the washing pump 1000 is obviously improved, even the drainage pressure can reach 2.5 times when the front cover rib 350 is not arranged, and better washing effect can be obtained.

It will be appreciated that the backflow is generated more randomly at the wheel front clearance c1 without the front shroud rib 350, and therefore the backflow is not distributed uniformly in the circumferential direction, which tends to unbalance the force of the impeller 300. By arranging the front cover rib 350, the front cover rib 350 drives the fluid medium in the front wheel gap c1 to rotate when the impeller 300 rotates, and the stirring of the front cover rib 350 is more uniform in circumferential distribution relative to the fluid medium without stirring, so that the acting force of the fluid medium in the front wheel gap c1 on the impeller 300 is more uniform in circumferential direction, and the probability of axial deflection when the impeller 300 operates is reduced.

Therefore, the scheme is also beneficial to promoting the stress balance of the impeller 300, reducing the eccentric wear probability of the impeller 300, reducing the performance reduction and damage risk caused by eccentric wear, and prolonging the service life of the impeller 300.

In this embodiment, the shape of the front cover rib 350 is not limited, and may be linear or curved.

When the front cover rib 350 is linear, the relative relationship between the front cover rib 350 and the axis L of the hub 310 may be flexibly set, and may be vertically set or alternatively set. In some embodiments, as shown in FIG. 3, the front cover bead 350 is perpendicular to the axis L of the hub 310, such that not only is the front cover bead 350 simple in construction and easy to machine, but the front cover bead 350 is radially disposed and defines a shorter flow path. In some embodiments, the front cover rib 350 extends helically around the axis L of the hub 310, and is also effective to drive the flow of fluid medium.

When the blades 340 of the impeller 300 are also spirally arranged, the spiral directions of the front shroud rib 350 and the blades 340 may be the same or opposite, which is not limited herein.

Optionally, the front cover rib 350 is integrally formed on the front cover plate 330, so that the processing procedure can be reduced, and the structural strength of the joint between the front cover rib 350 and the front cover plate 330 is high, so that the front cover rib 350 can bear a large bending moment and is not easy to break. When the front cover rib 350 is integrally formed with the front cover plate 330, the front cover rib 350 and the front cover plate 330 may be integrally formed by die casting, or the front cover rib 350 may be formed by punching on the front cover plate 330 when the front cover plate 330 is processed, which is not limited herein. Of course, the present application does not exclude that the front cover rib 350 is fixed to the front cover 330 by welding or the like.

In some embodiments, as shown in fig. 2, 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 clearance between the front cover plate 330 at the front end and the inner wall surface of the pump housing assembly 400 during assembly. Taking fig. 5 as an example, the inner wall surface of the pump housing assembly 400 includes a water inlet guide tube wall f3, the water inlet guide tube wall f3 is a tubular wall, and the front end tube 331 is inserted into a pipe formed by the water inlet guide tube wall f 3. Thus, the gap between the outer peripheral surface of the front end pipe 331 and the water inlet guide pipe wall f3 also belongs to the wheel front gap c1. By this arrangement, when the fluid medium flows into the inlet of the front wheel gap c1, the water inlet guide pipe wall f3 and the front end pipe 331 can guide the fluid medium to flow along the axial direction, so that the excessive turbulence generated when the fluid medium enters the front wheel gap c1 is reduced. The same is true of the tubular shape of the front tube 331, and the shape of the front tube 331 guides the fluid medium to flow in the axial direction, reducing excessive turbulence when entering the central inlet 301.

In addition, the provision of the front end pipe 331 can effectively control the size of the gap between the front side surface of the impeller 300 and the inner wall surface of the pump housing assembly 400. At reasonable gap sizes, the fluid medium, after entering the wheel front gap c1, exerts pressure on the front surface of the impeller 300 by the surface tension of the fluid medium.

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. In this way, 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.

Specifically, the front end tube 331 is a circular tube, the cross section of the reducer tube 332 is circular, and the cross section of the conical ring plate 333 is also circular. The cross section here refers to a cross section perpendicular to the axis L. The guiding and distributing of the flowing medium are balanced and the stress is even in all parts of the front cover plate 330 in the circumferential direction, which is beneficial to improving the rotation stability of the impeller 300.

In some embodiments, as shown in fig. 1, the front cover rib 350 is located on the front surface of the cone ring plate 333. It will be appreciated that since the front cover bead 350 is located within the wheel front gap c1, the height of the wheel front gap c1 generally needs to be controlled to a small extent, and thus the height of the front cover bead 350 is very limited. Height here refers to a dimension in a direction perpendicular to the front cover plate 330. By disposing the front cover bead 350 on the front surface of the cone ring plate 333, it is advantageous that the front cover bead 350 can sufficiently exert the driving effect by increasing the axial dimension of the front cover bead 350.

Specifically, as shown in fig. 1 and 3, the radially outer ends of the front cover ribs 350 are flush with the outer edge of the front cover plate 330, i.e., the radially outer ends of the front cover ribs 350 extend to the circumferential outlet 302, so that the flow medium in the wheel front gap c1 is still acted upon before converging with the flow medium in the impeller 300.

Further, the radially inner end of the forward cap bead 350 is disposed adjacent the reducer 332 such that the radial dimension of the forward cap bead 350 is sufficiently long to perform adequately. In addition, the radial inner end of the front cover rib 350 is close to the reducer 332, so that the flowing medium flowing into the wheel front gap c1 can be split to two sides of the front cover rib 350 as soon as possible, and the backflow possibility is reduced.

In the present application, the plurality of blades 340 are provided and the plurality of blades 340 are distributed at intervals along the circumferential direction, so that the working capacity of the impeller 300 on the flowing medium is strong, the stress of the single blade 340 is reduced, the single blade 340 is not easy to bend, and the service life is long. The blade 340 may be configured as disclosed in the prior art, and the shape and number of the blade 340 are not limited herein.

Specifically, the number of front cover ribs 350 is also plural, and the plural front cover ribs 350 are distributed at intervals along the circumferential direction, so that the working capacity of the front side of the impeller 300 for the flowing medium is also stronger, and the stress of a single front cover rib 350 is reduced, and the front cover rib 350 is not easy to bend and has long service life.

Further, the front cover ribs 350 are equal in number to the blades 340, which is advantageous for more equalizing the internal and front side stresses of the impeller 300.

In some embodiments, rear cover ribs 360 are provided on the rear surface of the rear cover plate 320, the rear cover ribs 360 extending radially along the impeller 300. The provision of the rear shroud rib 360 may further increase the force balance of the impeller 300.

Specifically, as shown in fig. 5, the impeller 300 is positioned in the pump casing assembly 400, and the rear wheel wall surface f1 of the inner wall surface of the pump casing assembly 400 is positioned at the rear side of the impeller 300. To avoid scraping against the rear wheel wall f1 during rotation of the impeller 300, the rear surface of the rear cover plate 320 is generally spaced apart from the rear wheel wall f1 to form a rear wheel gap c2. Typically, the wheel-back gap c2 is also annular, and the pressure in the wheel-back gap c2 is greater at the radially outer end than at the radially inner end, and some of the fluid medium discharged from the circumferential outlet 302 may flow centrally along the wheel-back gap c2.

Here, it is common that the driving member of the washing pump 1000 is coupled to the hub 310 through the driving shaft 110. The wheel rear wall surface f1 is provided with a fitting hole 409, and the transmission shaft 110 is located at the fitting hole 409 and at the radial center of the wheel rear clearance c2.

Because the rear cover rib 360 is no longer annular, when the impeller 300 rotates, the rear cover rib 360 pushes the fluid medium in the rear gap c2 of the impeller to rotate around the axis L, so that the fluid medium is centrifuged and is thrown radially from inside to outside. The pressure in the wheel rear clearance c2 drops and draws in more fluid medium at the radially inner end of the rear cover bead 360 and the pressure at the radially outer end of the rear cover bead 360 rises to expel fluid medium radially outwardly, which also obtains velocity 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 360 in the application prevents leakage loss caused by backflow in the rear wheel clearance c2 on one hand, and reduces work loss; on the other hand, the rear cover rib 360 can apply work to the fluid medium in the rear wheel gap c2. The provision of the rear cover rib 360 also reduces energy dissipation, improves volumetric efficiency of the washing pump 1000, increases drainage pressure, and causes the impeller 300 to generate a larger lift in a limited space.

When the rear cover rib 360 is arranged on the impeller 300, the fluid medium in the rear gap c2 of the impeller can generate forward supporting force on the impeller 300 when flowing, so that the probability that the impeller 300 is attached to the rear wall surface f1 of the impeller is reduced. The stress of the impeller 300 is balanced in the circumferential direction, and the eccentric wear probability of the impeller 300 is reduced.

In addition, when the transmission shaft 110 is assembled to the pump housing assembly 400, a sealing structure is required to be provided at the assembly hole 409, and the assembly hole 409 may be filled with a material such as lubricating oil. By providing the rear cover rib 360 such that the radially inner end pressure of the wheel rear gap c2 is lower than the radially outer end, the problem of leakage caused by extrusion of the flowing medium into the fitting hole 409 is reduced, and pollution is reduced.

In this embodiment, the shape of the rear cover rib 360 is not limited, and may be linear or curved.

When the rear cover rib 360 is linear, the relative relationship between the rear cover rib 360 and the axis L of the hub 310 may be flexibly set, may be vertically set or alternatively set, etc. In some embodiments, as shown in FIG. 4, the rear ribs 360 are perpendicular to the axis L of the hub 310, which not only simplifies the construction of the rear ribs 360 and facilitates machining, but also provides a shorter defined flow path for the rear ribs 360 in the radial direction. In some embodiments, the rear shroud rib 360 extends helically about the axis L of the hub 310 to also effectively drive the flow of fluid medium.

When the blades 340 of the impeller 300 are also spirally arranged, the spiral direction of the rear shroud rib 360 and the blades 340 may be the same or opposite, which is not limited herein.

Optionally, the rear cover rib 360 is integrally formed on the rear cover plate 320, so that the processing procedure can be reduced, and the structural strength of the joint between the rear cover rib 360 and the rear cover plate 320 is high, so that the rear cover rib 360 can bear a large bending moment and is not easy to break. When the rear cover rib 360 is integrally formed with the rear cover plate 320, the rear cover rib 360 and the rear cover plate 320 may be integrally formed by die casting, or the rear cover rib 360 may be formed by punching on the rear cover plate 320 when the rear cover plate 320 is manufactured, which is not limited herein. Of course, the present application does not exclude that the rear cover rib 360 is fixed to the rear cover 320 by welding or the like.

Further, the back plate 320 and the hub 310 are integrally formed, so that the back plate 320 and the hub 310 have high structural strength and high torque resistance at the joint.

Specifically, as shown in fig. 2 and 4, one end of the rear cover rib 360 is flush with the outer edge of the rear cover plate 320, i.e., the radially outer end of the rear cover rib 360 extends to the circumferential outlet 302, so that the flowing medium in the wheel rear clearance c2 is still subjected to work before converging with the flowing medium in the impeller 300.

Further, the other end of the rear cover rib 360 is connected to the hub 310, and the radially inner end of the rear cover rib 360 is disposed in a direction away from the central inlet 301. It will be appreciated that there is room within the pump housing assembly 400 for the hub 310, and therefore, the rear cover rib 360 is connected to the hub 310 to make full use of the space.

In this application, the arrangement of the front and rear cover ribs 350, 360 also increases the structural strength.

In this application, the rear cover rib 360 is a plurality of, and a plurality of rear cover ribs 360 are distributed along circumference at intervals, so that the acting ability of the impeller 300 rear side to the flowing medium is also stronger, and the stress of a single rear cover rib 360 is reduced, and the rear cover rib is not easy to bend and has long service life.

Further, the back shroud rib 360 is equal in number to the blades 340, which is advantageous for more balancing the internal and back side stresses of the impeller 300.

A washing pump 1000 according to an embodiment of the present invention is described below with reference to fig. 1 to 5.

As shown in fig. 5, the washing pump 1000 includes: a pump housing assembly 400 and an impeller 300. The pump housing assembly 400 has an impeller cavity V1 formed therein, the impeller 300 is disposed in the impeller cavity V1, and the impeller 300 is the impeller 300 of the foregoing embodiment, and the structure of the impeller 300 will not be described herein.

Specifically, the inner wall surface of the impeller housing V1 includes a wheel rear wall surface f1 and a wheel front wall surface f2, the wheel rear wall surface f1 being located at the rear side of the rear cover plate 320 and disposed spaced apart from the rear cover plate 320, and a wheel rear gap c2 being formed between the rear surface of the rear cover plate 320 and the wheel rear wall surface f 1. The front wheel wall f2 is annular and disposed around the axis L of the hub 310, the front wheel wall f2 being located on the front side of the front cover plate 330 and spaced apart from the front cover ribs 350, a front wheel clearance c1 being provided between the front surface of the front cover plate 330 and the front wheel wall f2.

The arrangement of the front wheel clearance c1 and the rear wheel clearance c2 can play a role in isolation, so that the impeller 300 is prevented from being contacted with the inner wall surface of the impeller accommodating cavity V1, and a safe and stable working space is provided for the impeller 300. The wear of the impeller 300 can be reduced and the service life of the impeller 300 can be prolonged.

According to the washing pump 1000 of the embodiment of the present invention, by providing the front cover rib 350 on the front surface of the impeller 300 and providing the front cover rib 350 extending in the radial direction of the impeller 300, on one hand, leakage loss caused by backflow of the fluid medium on the front side is prevented, and on the other hand, the front cover rib 350 can apply work to the front side fluid medium. Therefore, the energy dissipation can be reduced, the volumetric efficiency of the washing pump 1000 can be improved, the drainage pressure can be increased, and a larger lift can be generated. And the front cover ribs 350 are beneficial to promoting the stress balance of the impeller 300, reducing the eccentric wear probability of the impeller 300, reducing the performance reduction and damage risk caused by the eccentric wear, and prolonging the service life of the washing pump 1000.

In some embodiments, as shown in fig. 5, the axial distance d1 between the front cover bead 350 and the wheel front wall surface f2 is 1-3mm, and a reasonable clearance may prevent the front cover bead 350 from scraping against the wheel front wall surface f2. It will be appreciated that the axial distance d1 between the front shroud rib 350 and the wheel front wall f2 is set such that the flow velocity in the wheel front gap c1 is relatively high, and the surface tension of the flowing medium can exert relatively high bearing force, so as to maintain relatively high force balance effect.

In some embodiments, rear cover ribs 360 are provided on the rear surface of the rear cover plate 320, and the wheel rear wall f1 is disposed spaced apart from the rear cover ribs 360. The axial distance d2 between the rear cover rib 360 and the rear wall surface f1 of the wheel is 1-3mm, and a reasonable gap can prevent the rear cover rib 360 from scraping the rear wall surface f1 of the wheel, and meanwhile, a relatively tensile force balance effect can be maintained.

Further, when the washing pump 1000 works, the motor directly drives the impeller 300 to rotate at a high speed, the rotating speed is high, the water head is large, and the washing effect is strong.

A washing appliance a according to an embodiment of the present invention is described below with reference to fig. 1 to 6.

The washing electric appliance a is internally provided with a washing pump, which is the washing pump 1000 described in the above embodiment, and the structure of the washing pump 1000 will not be described again here.

According to the washing electric appliance A provided by the embodiment of the invention, by arranging the washing pump 1000, the washing pump 1000 has high volumetric efficiency, high drainage pressure and sufficient lift, and can generate a stronger washing effect. In addition, the front cover ribs 350 are beneficial to promoting the stress balance of the impeller 300, reducing the eccentric wear probability of the impeller 300 and prolonging the service life of the washing pump 1000, so that the washing effect of the washing electric appliance A can be enhanced.

Specifically, the washing appliance a may be a dishwasher, a washing machine, or the like, or may be other devices that require the provision of the washing pump 1000, which is not limited herein. The washing electric appliance A has good integral washing effect and long service life.

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. An impeller of a washing pump, comprising:

a hub;

the rear cover plate is connected with the hub;

a front cover plate which 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, an inner edge surrounding part of the front cover plate is formed into a central inlet of the impeller, and a circumferential outlet of the impeller is formed between the outer edge of the front cover plate and the outer edge of the rear cover plate;

the blade is connected between the front cover plate and the rear cover plate;

the front cover rib is arranged on the front surface of the front cover plate, and the front cover rib extends along the radial direction of the impeller.

2. The impeller of a washing pump according to claim 1, characterized in that the front cover ribs are perpendicular to the axis of the hub or the front cover ribs extend helically around the axis of the hub.

3. The impeller of a washing pump of claim 1, wherein the front cover plate comprises:

the front end pipe extends along the front-back direction, and the front end pipe orifice of the front end pipe is the central inlet;

the front end of the reducing pipe is connected with the rear end of the front end pipe, and the diameter of the reducing pipe is gradually increased from front to back;

the cone ring plate is arranged opposite to the rear cover plate, the inner edge of the cone ring plate is connected with the rear end of the reducer pipe, the circumferential outlet is formed between the outer edge of the cone ring plate and the outer edge of the rear cover plate, and the distance between the cone ring plate and the rear cover plate in the direction from inside to outside is gradually reduced so that the circumferential outlet is formed into a necking.

4. The impeller of the washing pump of claim 3 wherein the front cover ribs are located on the front surface of the cone-ring plate.

5. The impeller of a washing pump of any one of claims 1-4, further comprising: and the rear cover rib is arranged on the rear surface of the rear cover plate, and the rear cover rib extends along the radial direction of the impeller.

6. The impeller of a washing pump according to claim 5, wherein the rear shroud rib is perpendicular to the axis of the hub or the rear shroud rib is spirally extended around the axis of the hub.

7. The impeller of the washing pump of claim 5 wherein the hub and the back plate are integrally formed, one end of the back cover rib is flush with the outer edge of the back plate, and the back cover rib is connected to the hub and disposed in a direction away from the central inlet.

8. The impeller of the washing pump of claim 5 wherein said plurality of vanes are circumferentially spaced apart and said front shroud rib and said rear shroud rib are each a plurality of and equal to said number of vanes.

9. A wash pump, comprising:

the impeller comprises a pump shell assembly, wherein an impeller accommodating cavity is formed in the pump shell assembly;

an impeller, which is an impeller of the washing pump according to any one of claims 1-8, the impeller being provided in the impeller housing; wherein,

the inner wall surface of the impeller accommodating cavity comprises a wheel rear wall surface and a wheel front wall surface, the wheel rear wall surface is positioned at the rear side of the rear cover plate and is spaced from the rear cover plate, and the wheel front wall surface is positioned at the front side of the front cover plate and is spaced from the front cover ribs.

10. The wash pump as in claim 9 wherein the axial distance between the front cover rib and the wheel front wall is 1-3mm.

11. The washing pump of claim 9 wherein when the impeller further comprises a rear shroud rib provided on a rear surface of the rear shroud, the wheel rear wall is spaced from the rear shroud rib, and an axial distance between the rear shroud rib and the wheel rear wall is 1-3mm.

12. A washing appliance comprising a washing pump according to any one of claims 9-11.