CN117905701A - 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. Comprising the following steps: the pump shell assembly comprises a main pump shell and a drainage pump shell which are sequentially arranged along the axial direction, an impeller accommodating cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller accommodating cavity is formed in one axial end of the main pump shell, the drainage pump shell is arranged at the end part of the main pump shell, a water inlet guide cavity communicated with the inner inlet channel is formed in the drainage pump shell, and the drainage pump shell is provided with a pump inlet communicated with the water inlet guide cavity; the impeller is positioned in the impeller accommodating cavity and provided with a central inlet arranged towards the inner inlet channel; the preposed functional piece is arranged in the water inlet guide cavity and comprises at least one of a heating piece and a guide piece. The washing pump is arranged in a layered manner in the axial direction, so that the washing pump is beneficial to being arranged as a large-flow pump and can bear the high pressure requirement; the stable inflow condition can be obtained, and the vibration and noise of the whole machine are reduced.

Description

Washing pump and washing electric appliance with same

Technical Field

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

Background

In people's daily life, washing electrical apparatus such as dish washer can liberate people's both hands, conveniently washs daily necessities such as tableware. The washing pump is used as a core component in the washing electric appliance and is responsible for the power source of the whole circulating waterway, and the water outlet effect of the washing pump directly influences the washing effect. With the improvement of the demands of people on life quality, the washing appliances in future life will gradually go into more families.

The conventional washing pump limited by the structure has some defects, such as insufficient flow of the washing pump, lower washing efficiency and larger vibration noise during operation, and the overall size of the washing pump is oversized if the flow is increased.

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 and the washing electric appliance with the same, and the structure of the washing pump is improved, so that the washing pump is beneficial to realizing large flow, the size is not excessively increased, the washing efficiency is improved, and the vibration and noise are reduced.

A washing pump according to an embodiment of the present invention includes: the pump shell assembly comprises a main pump shell and a drainage pump shell which are sequentially arranged along the axial direction, an impeller accommodating cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller accommodating cavity is formed in one axial end of the main pump shell, the drainage pump shell is arranged at the end part of the main pump shell, a water inlet guide cavity communicated with the inner inlet channel is formed in the drainage pump shell, and the drainage pump shell is provided with a pump inlet communicated with the water inlet guide cavity; the impeller is positioned in the impeller accommodating cavity and provided with a central inlet arranged towards the inner inlet channel; the preposed functional piece is arranged in the water inlet guide cavity and comprises at least one of a heating piece and a guide piece.

According to the washing pump provided by the embodiment of the invention, through arranging the double-layer pump shell which is sequentially arranged along the axial direction, on one hand, overlarge occupied area can be avoided, the drainage pump shell can be used for guiding water flow, strong rotational flow is reduced, and the water flow is axially guided to the central inlet of the impeller through the inner inlet channel. The device has the advantages of small change of water flow direction, short water flow path, low water flow resistance, low energy consumption and low water flow head loss, is beneficial to converting a larger pressure water head when the impeller operates, improves the operating efficiency of the washing pump, and is beneficial to the washing pump to meet the requirements of high flow rate and high pressure. When the drainage piece is arranged in the water inlet drainage cavity, the influence caused by the change of the flow area and the flow direction of the water flow is counteracted. When the water inlet guide cavity is internally provided with a heating element, the front heating is facilitated. Can be beneficial to improving the washing efficiency of the washing pump and reducing the energy consumption.

In some embodiments, an end surface of the water inlet guide cavity opposite to the inner inlet channel is a guide cavity end surface, and the front functional piece comprises a drainage piece, and the drainage piece is arranged on the guide cavity end surface.

In some embodiments, the flow guide comprises a flow guide boss extending along the axis of the impeller, the flow guide boss tapering in a direction towards the central inlet.

In some embodiments, the pre-function comprises a drainage piece comprising a drainage septum; the outer peripheral surface of the water inlet guide cavity is a guide cavity peripheral surface, and the pump suction inlet and the drainage partition plate are arranged on the guide cavity peripheral surface and are positioned on two opposite sides of the inner inlet channel.

In some embodiments, the pre-function comprises the heating element, the heating element being disposed at least partially around an axis of the impeller.

In some embodiments, the heating element comprises: a first heat pipe extending around the axis of the impeller, and a second heat pipe connected to an end of the first heat pipe remote from the pump intake.

In some embodiments, the drain pump housing forms a mounting tube on a side remote from the main pump housing, a portion of the heater is located within the mounting tube, and the power receiving end of the heater is mounted at an end of the mounting tube.

In some embodiments, the end face of the main pump casing facing the water inlet guide cavity is an auxiliary guide end face, the auxiliary guide end face is annular and is curved, and the auxiliary guide end face is gradually arranged in a protruding mode facing the water inlet guide cavity in a radial inward direction. .

In some embodiments, the main pump housing is a volute, an annular passage from the periphery of the impeller to the inner peripheral wall of the impeller accommodating cavity forms a volute chamber of the volute, the main pump housing is provided with a water outlet passage to form a diffuser pipe of the volute, and a separation part between the volute chamber and the diffuser pipe is a volute tongue; the cross-sectional area of the scroll chamber increases gradually from the scroll tongue to the diffuser in the direction of flow of water.

In some embodiments, the impeller comprises: a first cover plate; the hub is connected with the first cover plate; the second cover plate is annular and is arranged around the axis of the impeller, the surrounding part of the second cover plate is the central inlet, the second cover plate is positioned on one side of the first cover plate, which is close to the drainage pump shell, the inner edge of the second 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, and a circumferential outlet is formed between the outer edge of the second cover plate and the outer edge of the first cover plate; and the blade is connected between the second cover plate and the first cover plate.

In some embodiments, the blades extend helically around the axis of the impeller, the edges of the blades adjacent to the axis being leading edges, the distance between the leading edges and the axis increasing in a direction towards the central inlet.

In some embodiments, the axis of the impeller is disposed vertically or laterally; the main pump housing is open at one end far away from the drainage pump housing, the pump housing assembly further comprises a rear end cover, the rear end cover is connected to one end of the main pump housing far away from the drainage pump housing, and the impeller is mounted on the rear end cover.

The washing appliance comprises the washing pump.

According to the washing electric appliance provided by the embodiment of the invention, the washing pump is arranged, so that the working efficiency is improved, and the vibration and noise are reduced.

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 top view of an impeller according to an embodiment of the invention;

FIG. 5 is a simulated view of an impeller according to an embodiment of the present invention;

FIG. 6 is a schematic view of the scroll structure of an embodiment of the present invention;

FIG. 7 is a cross-sectional view of the scroll shown in FIG. 6;

fig. 8 is a structural view of a washing appliance provided with a washing pump.

Reference numerals:

Washing electric appliance A,

Washing pump 1000, pump housing assembly 1000B,

A drainage pump shell 100, a water inlet drainage cavity 110, a first drainage channel 101, a second drainage channel 102, a drainage cavity peripheral surface S1, a drainage cavity end surface S2, a second mounting port 113, a pump inlet 114, a mounting pipe 180,

Front functional piece 1000C, drainage piece 160, drainage boss 161, drainage tube 162, drainage inlet 163, drainage partition 168,

Main pump case 200, auxiliary leading end face S3,

Impeller cavity 210, volute 211, volute tongue 212,

An inner inlet passage 220,

A rear seat 270,

A water outlet channel 280,

A first mounting port 290,

Impeller 300, impeller axis L,

A central inlet 301, a circumferential outlet 302,

Hub 310, first cover plate 320, second cover plate 330, front tube 331, blades 340, leading edge 341, rear ring 370,

Rear end cap 400, mounting hole 409,

Heating element 600, first heat pipe 610, second heat pipe 620,

A driving motor 700, a driving shaft 710 and a sealing ring 810.

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.

In the description of the present invention, it should be understood that the terms "center," "vertical," "transverse," "length," "left," "right," "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 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. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.

In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.

A washing pump 1000 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

As shown in fig. 1, the washing pump 1000 includes: pump housing assembly 1000B, impeller 300, and pre-function 1000C. The pump housing assembly 1000B includes a main pump housing 200 and a drain pump housing 100 sequentially disposed in an axial direction, an impeller housing 210 is defined in the main pump housing 200, and an inner inlet passage 220 communicating with the impeller housing 210 is provided at one axial end of the main pump housing 200. The drainage pump housing 100 is installed at an end of the main pump housing 200, a water inlet guide chamber 110 communicating with the inner inlet passage 220 is formed in the drainage pump housing 100, and the drainage pump housing 100 has a pump intake port 114 communicating with the water inlet guide chamber 110. The impeller 300 is located within the impeller receptacle 210, the impeller 300 having a central inlet 301 disposed toward the inward channel 220. The pre-function 1000C is disposed within the inlet guide chamber 110, and the pre-function 1000C includes at least one of the heating element 600 and the guide 160.

In the present application, the axis L of the impeller 300 is set as the axis of the washing pump 1000 and also as the axis of the main pump casing 200. This limitation is merely for convenience in expressing the positional relationship of the components in the washing pump 1000, and is not intended to limit the washing pump 1000 and the impeller 300 and the main pump casing 200 in the washing pump 1000 to a revolution shape. Wherein the impeller 300 rotates about its axis L as it rotates. Thus, references herein to the axial direction are all in the direction of the axis L of the impeller 300. In the example of fig. 1, the axis L of the impeller 300 is arranged in the up-down direction, i.e. the wash pump 1000 is a vertical pump. Of course, the application does not exclude that in some embodiments, the axis L of the impeller 300 is arranged in a horizontal direction and the wash pump 1000 is a horizontal pump.

In the present application, it is mentioned that the pump casing assembly 1000B includes the main pump casing 200 and the drainage pump casing 100 which are sequentially disposed in the axial direction, and the pump casing assembly 1000B is formed in a double-casing structure which is stacked in the axial direction. Here, the attachment of the drainage pump casing 100 to the end of the main pump casing 200 means that the drainage pump casing 100 is attached to the end of the main pump casing 200 provided with the inner inlet passage 220, and the drainage pump casing 100 may be attached to the end face of the end of the main pump casing 200 or to the outer circumferential surface adjacent to the end face, which is not limited.

Compared with a single-shell pump structure (i.e. in the scheme in the prior art, the washing pump only comprises the main pump shell and does not comprise the drainage pump shell), the water flow is buffered in the drainage pump shell 100 after entering the washing pump 1000 by arranging the drainage pump shell 100, so that the flowing state of the water flow tends to be stable and then flows to the impeller 300 in the main pump shell 200. Just because the drainage pump shell 100 can play a role in drainage and buffering, the impeller 300 can bear the impact force of high-flow water flow when the washing pump 1000 is designed at high flow rate. And if the impeller 300 is operated and the rotation speed of the impeller 300 is changed due to unstable water flow, the change of the rotation speed may aggravate the fluctuation and even the backflow of the water flow, the drainage pump housing 100 upstream of the main pump housing 200 may provide a water flow buffer space, so that the water flow may tend to be stable in the water inlet drainage cavity 110.

In the prior art, there is also a radially telescopic pump structure, i.e. the washing pump comprises a main pump housing and a drainage pump housing, but the drainage pump housing is sleeved on the radial outer side of the main pump housing, and a water inlet drainage cavity between the main pump housing and the drainage pump housing is an annular cavity surrounding the main pump housing. After entering, the water flow generates annular flow to fill the whole annular cavity, and the water flow in the annular cavity needs to turn 180 degrees to flow into the main pump shell. The design of the annular cavity can ensure that the occupied area of the pump structure is overlarge, the kinetic energy consumed by the repeated change of the flow direction before the water flow enters the impeller is excessive, and the water flow generates stronger rotational flow under the guidance of the annular cavity. However, the water flow flowing in the rotating direction has adverse impact force on the impeller, so that the impeller is excessively worn.

Compared with the radial telescopic pump structure, the application not only reserves the drainage pump shell 100 to form buffer and guide space for water flow, but also avoids generating strong rotational flow, so that the impeller 300 can bear the impact force of the water flow with large flow when the washing pump 1000 is designed with large flow, and is beneficial to the washing pump 1000 to meet the requirements of large flow and high pressure. And the main pump shell 200 and the drainage pump shell 100 are arranged in a stacked manner along the axial direction, so that the occupied area is reduced, and the installation and the debugging are convenient.

Here, an inner inlet channel 220 is disposed at one end of the main pump housing 200 facing the drainage pump housing 100, and a central inlet 301 of the impeller 300 is disposed toward the inner inlet channel 220, the inner inlet channel 220 guides water flow to the impeller 300 along an axial direction, and the drainage pump housing 100 is also disposed along the axial direction, so that water flow enters the main pump housing 200 from the drainage pump housing 100 as a whole, the water flow direction changes little, the water flow path is short, the water flow resistance is low, the energy consumption is low, the flow speed water head loss is low, and the conversion of a larger pressure water head during the operation of the impeller 300 is facilitated, and the operation efficiency of the washing pump 1000 is improved.

In the present application, the water inlet guide cavity 110 is provided with a pre-functional element 1000C, where the pre-functional element 1000C may include a heating element 600, a guide element 160, and the pre-functional element 1000C may include both the heating element 600 and the guide element 160.

When the water inlet guide cavity 110 is provided with the drainage member 160, it is obvious that the drainage member 160 is used for guiding the water flow in the water inlet guide cavity 110 towards the inner inlet channel 220. It will be appreciated that the flow of water from the outside into the inlet guide chamber 110 suddenly increases in flow area. When the water flow in the water inlet guide chamber 110 flows into the inner inlet channel 220 again, the flow area of the water flow is suddenly reduced. The provision of the flow guide 160 helps to direct the flow of water during the flow of water so that the water automatically converges as it is directed through the flow guide 160, helping to counter the adverse effects of abrupt changes in the casing cross-section of the pump casing assembly 1000B. And there are solutions where the water flow is facing a turning problem when entering the water intake guide chamber 110. For example, when the pump intake 114 is connected to the water intake pipe, if the water intake pipe is connected to the wash pump 1000 in the axial direction, the space occupied by the wash pump 1000 is too long in the axial direction, so that the pump intake 114 is typically disposed at the side of the drainage pump housing 100, and the water flow needs to turn 90 degrees into the inner intake passage 220 when entering the drainage pump housing 100. If the water flow steering is not smooth enough, too severe rotational flow is generated, so that not only is the water flow resistance increased, but also the energy consumption is too large, and the rotational flow is too large in impact damage to the impeller, so that the service life of the impeller is reduced.

By providing the drainage 160, the water flow is smoothly diverted, turbulence generated by diversion of the water flow is reduced, the water flow is concentrated and guided towards the central inlet 301 of the impeller 300, and a stable inflow condition of the washing pump 1000 is obtained. For example, the water flows to the impeller 300 along the axial direction, so that the probability of axial deflection of the impeller 300 after being impacted by rotational flow is reduced, the abrasion to the rotation of the impeller 300 is reduced, and the service life of the impeller 300 is prolonged.

In addition, by not directly facing the center inlet 301 of the impeller 300 when the pump intake 114 is taking in water, the impact of the intake water on the impeller 300 is reduced, and the water is buffered and guided by the flow guide 160, thereby reducing wear.

Therefore, the drainage piece 160 is matched with the layout structure of the pump shell assembly 1000B, so that the working efficiency of the washing pump 1000 is improved, and vibration and noise are reduced.

When the heating element 600 is disposed in the water inlet guide chamber 110, the water flow is heated before entering the impeller 300, and the water flow is fully stirred when flowing through the impeller 300, so that the water temperature is gradually uniform. The heating element 600 is arranged in the water inlet guide cavity 110, so that the space of the subsequent pipeline is not occupied, and the space of the water inlet guide cavity 110 is fully utilized. In addition, the water flow in the water inlet guide cavity 110 is subjected to abrupt change of circulation, and can be buffered to a certain extent when passing through the heating element 600, so that the water flow can fully absorb the heat of the heating element 600, and the heat exchange rate is improved.

Therefore, whether the drainage member 160 or the heating member 600 is provided in the water inlet guide chamber 110, the washing efficiency of the washing pump 1000 can be advantageously improved, and the energy consumption can be reduced.

In some embodiments, as shown in fig. 1, the main pump casing 200 is open at an end remote from the pilot pump casing 100, and the pump casing assembly 1000B further includes a rear end cap 400, the rear end cap 400 being connected to the end of the main pump casing 200 remote from the pilot pump casing 100, and the impeller 300 being mounted on the rear end cap 400.

Specifically, the main pump casing 200 is further provided with an inner inlet channel 220, an outlet channel 280 and a first mounting port 290 which are communicated with the impeller accommodating cavity 210, and the inner inlet channel 220 and the first mounting port 290 are positioned at two axial ends of the impeller accommodating cavity 210. The rear end cap 400 is connected to the main pump housing 200 at the first mounting port 290, and the drain pump housing 100 is connected to the main pump housing 200 at the inner intake passage 220, i.e., the rear end cap 400 and the drain pump housing 100 are mounted at both axial ends of the main pump housing 200.

The drainage pump casing 100 is provided with a pump inlet 114 and a second mounting port 113 which are communicated with the water inlet guiding cavity 110, and the second mounting port 113 is covered outside the inner inlet channel 220.

In the present application, the washing pump 1000 further includes a driving member (e.g., the driving motor 700 in fig. 1) that drives the entire impeller 300 to rotate around the axis L through the hub 310. When the impeller 300 rotates, the water in the impeller 300 is pushed to rotate around the axis L, and the water is thrown from inside to outside in the radial direction under the centrifugal action. 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 water and the pressure at the circumferential outlet 302 rises to drain outwardly. 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.

Due to the continuous nature of the water flow, the water flow within the inlet guide chamber 110 is continuously drawn into the impeller 300 through the inner inlet passage 220, the central inlet 301, and the water flow is continuously discharged from the circumferential outlet 302, the discharged water flow acquires velocity energy and pressure energy, and is discharged from the outlet passage 280. The impeller 300 performs work on the water flow to provide a certain head to the washer pump 1000. Here, the head refers to the increase in energy per unit weight of water flow from the inlet to the outlet of the pump.

The novel washing pump 1000 of the application has a structure which is greatly different from the prior products, and the performance index is greatly improved.

When the washing pump 1000 is assembled, the impeller 300 may be mounted on the rear cover 400, the impeller 300 may be mounted in the impeller housing 210 through the first mounting port 290, and then the rear cover 400 may be fixedly coupled with the main pump housing 200. The components to be installed in the drainage pump housing 100 may be installed in the water intake guide chamber 110 through the second installation port 113, and then the drainage pump housing 100 and the main pump housing 200 may be fixedly connected. Thus, the washing pump 1000 is very convenient to assemble and maintain.

It should be noted that, the rear end cover 400 may be a cover plate, and the driving member is connected to the rear end cover 400; it is also possible to use a driving member fitted at the first mounting port 290 of the main pump housing 200, in which case the driving member serves as the rear cover 400.

Specifically, the outer peripheral surface of the intake guide chamber 110 is a guide chamber peripheral surface S1, and a pump intake port 114 is formed in the guide chamber peripheral surface S1.

In some embodiments, as shown in fig. 1, an end surface of the water inlet guide cavity 110 opposite to the inner inlet channel 220 is a guide cavity end surface S2, and the guide 160 is disposed on the guide cavity end surface S2. Reliably, the cavity guiding end face S2 can be a plane, so that the processing is convenient, the connection of other components is convenient, and the positioning and the installation are convenient. In some embodiments, the cavity end surface S2 is an arc surface, such as a hemispherical surface.

In some embodiments, as shown in fig. 1, the flow director 160 includes a flow directing boss 161, the flow directing boss 161 extending along the axis L of the impeller 300, the flow directing boss 161 tapering in a direction toward the central inlet 301 of the impeller 300.

To understand the function of the drainage boss 161, this is further described herein with reference to the orientation of the embodiment of FIGS. 1-2. As shown in fig. 1-2, the drainage pump housing 100 is disposed in the up-down direction, the pump intake 114 is located at the left side of the drainage pump housing 100, and the bottom of the drainage pump housing 100 is provided with a second mounting port 113 and is connected to the main pump housing 200. At this time, the drainage pump housing 100 serves to guide the water flowing from the left side downward, and to turn the water by 90 degrees.

If the drainage 160 is not provided in the drainage pump case 100, the water flows from the left and then flows toward the right segment of the drainage chamber circumferential surface S1. During the rightward flow, although a part of the water flows downward under the drive of the water pressure, a large amount of water flows generate rightward impact force on the guide cavity peripheral surface S1. The impact force of the water flow is large, and the impact force also fluctuates to a certain extent, so that large vibration and noise are generated in the whole drainage pump shell 100. And the water flow can generate a certain rotational flow when turning, the rotational flow is unfavorable for the stable operation of the impeller 300, and vibration and noise are unavoidable in the operation.

After the drainage boss 161 is arranged on the drainage cavity end face S2, multiple guiding effects can be generated for water flow steering:

First, since the drainage boss 161 tapers from top to bottom, the outer circumferential surface of the drainage boss 161 corresponds to a kind of guide surface. After a part of the water flow flowing into the pump inlet 114 directly rushes to the drainage boss 161, the drainage boss 161 can guide the part of the water flow to flow downwards, so that the water flow can flow along the drainage boss 161 to the inner inlet channel 220, and the water flow can flow into the impeller 300 in the main pump shell 200 along the axial direction.

The water flow flowing into the pump inlet 114 is largely split into two by the flow guide boss 161. A first drainage channel 101 is formed between the drainage boss 161 and the front section of the drainage cavity peripheral surface S1, and a second drainage channel 102 is formed between the drainage boss 161 and the rear section of the drainage cavity peripheral surface S1. After the partial water flow is branched forwards, the partial water flow flows rightward through the first guide channel 101. After being split rearward, a portion of the water flows rightward through the second flow guide 102. After the two streams are split, the impact force on the drainage pump housing 100 to the right is reduced. When the two water flows meet, the impact forces are opposite in direction, so that a part of the impact forces can be offset, and the impact force on the drainage pump casing 100 in the front-rear direction is small. Therefore, compared with the scheme without the drainage boss 161, the scheme of the application can greatly reduce the vibration and noise of the drainage pump shell 100.

In the process that the water flows along the first diversion channel 101 and the second diversion channel 102 from left to right respectively, the water is driven by the water pressure, the diversion boss 161 is guided, and the water is reversed by the extrusion of the backflow water, so that the water flow direction can smoothly flow from the radial direction to the axially inward channel 220.

The flow guiding boss 161 is utilized to split the water flow flowing in from the pump inlet 114 and guide the water flow to the first flow guiding channel 101 and the second flow guiding channel 102, compared with a scheme without the flow guiding boss 161, the scheme with the flow guiding boss 161 reduces the flow area of the water flow, so that the water flow flowing in from the pump inlet 114 is not rapidly slowed down to cause rapid rising of the water pressure, and the water flow impact acting force is slowed down.

Therefore, the drainage boss 161 is arranged to guide the water flow in the water inlet guide cavity 110 in a diversion way, so that the flow area of the water flow is limited, the rapid drop of the flow speed and the rapid rise of the water pressure of the water flow are avoided, and the flow condition of the water flow in the guided water flow is stable. The diversion of the single water flow is easier, and the impact force generated by the two water flows on the drainage pump shell 100 during the diversion can be partially offset. Particularly, the drainage boss 161 is surrounded by the first drainage channel 101 and the second drainage channel 102, the flowing state of the water flow in the first drainage channel 101 and the second drainage channel 102 is stable, the impact generated by the diversion of the water flow in the drainage boss 161 is buffered by the water flow in the first drainage channel 101 and the second drainage channel 102, and the impact force released outwards is reduced. Therefore, it is advantageous to reduce the overall vibration of the drainage pump casing 100 and to reduce noise.

The rotational flow generated during reversing is smaller and the flow is smoother under the guidance of the guide cavity peripheral surface S1 and the guide boss 161, so that the radial rotational flow generated during the direction conversion of the water flow is eliminated as much as possible, and the impact loss in the flow channel is reduced.

And the flow guide boss 161 smoothly guides the water flow to the main pump housing 200 with a certain flow distance before entering the main pump housing 200 to divert the water flow, and the water flow can be stabilized during the flow. The overall size of the pump housing 100 is thus not excessive, and high flow efficiency is achieved in the washer pump 1000, reducing vibration and noise during operation.

In the solution of the present application, the drainage boss 161 may be a solid block, and the drainage boss 161 may also be a hollow structure.

Optionally, the drainage boss 161 is in arc transition connection with the cavity end surface S2, which can be beneficial to guiding the water flow to smoothly and stably flow to the drainage boss 161 along the arc transition surface, and then guiding the flow of the inner inlet channel 220 through the drainage boss 161.

Specifically, the circular arc transition connection between the cavity guiding peripheral surface S1 and the cavity guiding end surface S2 is beneficial to guiding the water flow smoothly and stably along the circular arc transition surface to flow to the cavity guiding peripheral surface S1, and then guiding the water flow to the inward channel 220 through the cavity guiding peripheral surface S1.

In some embodiments, as shown in fig. 1, the drainage boss 161 is a solid of revolution, so that when the water flows along the drainage boss 161 in a rotating way, the flow is smoother, the water flow resistance is smaller, and thus, the water flow flows along the drainage boss 161 to the inward channel 220 more smoothly.

In some embodiments, as shown in FIG. 1, the cavity guiding circumferential surface S1 is a cylindrical surface. Thus, when the water flows along the guiding cavity peripheral surface S1 in a rotating way, the flowing is smoother, the water flow resistance is smaller, and the water flows along the guiding cavity peripheral surface S1 to the inward channel 220 in a smoother way.

Optionally, the end of the drainage boss 161 is a spherical cap surface protruding toward the second mounting port 113. Thus, the full-angle water flow of the ring drainage boss 161 is beneficial to gathering rapidly along the spherical crown surface towards the axis of the drainage boss 161 when flowing through the spherical crown surface, and is beneficial to restricting the water flow to flow along the axial direction.

Of course, the drainage member 160 of the present application may not be limited to the drainage boss 161, and a drainage tube 162 may be used, and the drainage tube 162 may be disposed around the axis L of the impeller 300, with the drainage tube 162 opening at one end facing the inward channel 220. Alternatively, the draft tube 162 is provided with a draft inlet 163 at a side remote from the pump intake 114, so that the two split water flows, after being joined, can enter the draft tube 162 through the draft inlet 163 and then be guided by the draft tube 162 to the inner intake passage 220. This facilitates restricting and de-swirling turbulent water flow into draft tube 162, allowing water flow to enter impeller 300 axially.

In some embodiments, as shown in FIG. 1, the drainage 160 includes a drainage partition 168. The outer peripheral surface of the intake guide chamber 110 is a guide chamber peripheral surface S1, and the pump intake 114 and the guide partition 168 are disposed on the guide chamber peripheral surface S1 and located on opposite sides of the inner intake passage 220. Therefore, the rotational flow formed when the water flows along the guide cavity peripheral surface S1 can be further weakened, and the direction of the water flow reversing and flowing along the axial direction can be promoted.

Specifically, the flow directing baffle 168 extends in a direction parallel to the axis L of the impeller 300, which further facilitates the flow reversing direction of the water flow in the axial direction. Optionally, the drainage partition 168 is disposed opposite to the pump intake 114, and the drainage partition 168 and the pump intake 114 are located at two radial ends of the drainage boss 161 and are located at the position where the two branches meet, so that the impact force of the two branches when the two branches meet can be reduced, which is beneficial for the two branches to keep in a split state and then to change direction under relative extrusion. Thus, the drainage partition 168 located at this position not only does not generate water flow resistance, but also has a stronger axial guiding effect on water flow.

Of course, the present application is not limited thereto, and there are some embodiments in which the drainage partition 168 may be plural, and plural drainage partitions 168 are circumferentially spaced apart.

In some embodiments, the pre-function 1000C includes a heating element 600, the heating element 600 being disposed at least partially around the axis L of the impeller 300. Another flow guide 160 may be constructed using the heating element 600.

In some embodiments, as shown in fig. 1, the heating element 600 and the heating element 600 of the drainage element 160 are disposed in the water inlet guide cavity 110 at the same time, and at least part of the heating element 600 is disposed around the drainage element 160, so that when water flows along the first drainage channel 101 and the second drainage channel 102, the water also flows along the heating element 600. The heating element 600 is arranged in such a way that the flow direction of the water flow can be reduced, the flow resistance of the water flow is reduced, and the heating element 600 is effectively integrated with the first diversion channel 101 and the second diversion channel 102, so that the volume of the washing pump 1000 is further reduced.

In some embodiments, the heating element 600 comprises: a first heat pipe 610 and a second heat pipe 620, the first heat pipe 610 extending around the axis L of the impeller 300, the second heat pipe 620 being connected to an end of the first heat pipe 610 remote from the pump intake 114. The first heat pipe 610 is arranged to facilitate drainage, and the second heat pipe 620 is arranged to play a role in blocking flow and guide water flow to turn along the axial direction in advance. In addition, the heating member 600 may be installed and fixed by the second heat pipe 620.

Specifically, the first heat pipes 610 are two and are arranged at intervals along the axial direction of the impeller 300, each first heat pipe 610 is disposed around the drainage 160, and the second heat pipe 620 is connected to one end of the two first heat pipes 610 away from the pump intake 114.

Thus, when water flows in from the pump inlet 114, the first heat pipe 610 can perform a certain guiding function to guide the water flow to the second heat pipe 620, so that the water flow is more smoothly turned, the water flow is favorably guided to the impeller 300 along the axial line L direction of the impeller 300, the rotational flow of the water flow is reduced, the hydraulic loss of the fluid medium caused by the rotational flow can be reduced, the driving effect of the impeller 300 on the fluid medium is improved, and the flow efficiency is improved.

In the embodiment shown in fig. 1, two first heat pipes 610 are provided, and the two first heat pipes 610 are located at the upper and lower sides of the pump intake port 114, which is equivalent to that when water flows from the pump intake port 114, the two first heat pipes 610 are clamped at the two sides of the water flow, so that the guiding effect is enhanced. The second heat pipe 620 is connected between the two first heat pipes 610, and the first heat pipes 610 more smoothly guide the water flow to the second heat pipes 620. Further, the second heat pipe 620 is an arc pipe, and opposite ends of the middle of the second heat pipe 620 protrude towards a direction away from the pump inlet 114, so that concentrated stress at the connection position of the first heat pipe 610 and the second heat pipe 620 can be reduced, and a certain buffering process is provided for diversion of water flow, so that turbulence is reduced.

In some embodiments, the drainage pump housing 100 forms a mounting tube 180 on a side remote from the main pump housing 200, with a portion of the heater 600 being located within the mounting tube 180, and the powered end of the heater 600 being mounted at the end of the mounting tube 180. The installation tube 180 is installed not only by adopting the scheme of installing the heating element 600, but also by enabling the electric connection end of the heating element 600 to avoid the impact of water flow, and the connection reliability is improved.

In some embodiments, as shown in FIG. 1, the top or side of the drainage pump housing 100 is formed with a mounting tube 180, the mounting tube 180 being located above the intake guide cavity 110 and communicating with the intake guide cavity 110.

Specifically, the heating element 600 is at least partially located within the mounting tube 180. By this arrangement, space occupation of other chambers can be reduced, the compactness of the structure can be improved, and the installation, sealing and energizing connection of the heating element 600 can be concentrated at the installation pipe 180, so that other parts of the washing pump 1000 are avoided.

Of course, the heating element 600 may be disposed on the main pump housing 200 or other locations in other embodiments of the present application, which is not limited herein. Of course, in the present application, the heating element 600 is preferably disposed on the drainage pump casing 100, and the pressure index, the efficiency index and the noise index are better.

In some embodiments, as shown in fig. 1, the end surface of the main pump housing 200 facing into the water intake guide cavity 110 is an auxiliary guide end surface S3, the auxiliary guide end surface S3 is annular and curved, and the auxiliary guide end surface S3 is gradually protruded toward the inside of the water intake guide cavity 110 in a radially inward direction.

Specifically, the auxiliary leading end surface S3 is located in the second mounting port 113. The auxiliary guiding end surface S3 is annular and curved, and the auxiliary guiding end surface S3 extends towards the water inlet guiding cavity 110 in the radial inward direction.

By the cooperation of the auxiliary leading end surface S3 and the drainage pump shell 100, the water inlet leading cavity 110 is formed into a closed cavity, so that water flow is ensured not to leak out of the drainage pump shell 100 when flowing in the water inlet leading cavity 110, and only flows to the main pump shell 200. The auxiliary guiding end surface S3 is similar to a horn shape in shape, on one hand, the water flow is promoted to gather towards the center along the auxiliary guiding end surface S3 so as to guide the water flow into the inner inlet channel 220, turbulence caused by the radial outward flow of the water flow is reduced, and the water flow is restrained to flow towards the impeller 300 along the axial direction as much as possible. On the other hand, when the water flow entering the water inlet guide cavity 110 meets the auxiliary guide end surface S3, the water flow is guided by the auxiliary guide end surface S3 to flow along the first guide channel 101 and the second guide channel 102 as much as possible, so that the water flow is guided to the main pump housing 200 along the guide 160 as much as possible. Therefore, the auxiliary guiding end surface S3 also has the function of converging the water flow, which is beneficial to weakening the radial rotational flow of the water flow and enabling the water flow to the impeller 300 along the axial direction.

Specifically, the auxiliary leading end surface S3 is similar to a conical cylindrical surface as a whole. The auxiliary leading end surface S3 may or may not be changed in the same diameter in the direction toward the leading end surface S2.

Alternatively, the vertical cross-sectional dimensions of the inner intake passage 220 may be the same or different throughout the axis L. Further alternatively, the inner intake passage 220 may vary in regular fashion when the vertical cross-sectional size varies throughout. For example, the inward channel 220 is a straight tube channel. For another example, the inward channel 220 is a tapered channel that gradually decreases in diameter in a direction toward the impeller 300. At this time, since the flow rate of the fluid medium flowing into the inner inlet passage 220 is stable, the section of the inner inlet passage 220 gradually decreases backward to increase the flow rate, thereby increasing the acceleration of the impeller 300. For another example, the inward channel 220 is a diverging channel that gradually increases in diameter in a direction toward the impeller 300. Such a structure of the inner inlet passage 220 may serve to slow down the flow rate when the flow into the inner inlet passage 220 is excessively large.

Optionally, the wash pump 1000 further includes a rectifying rib disposed within the inner intake passage 220. It can be appreciated that the rectifying ribs can reduce the swirling flow of the fluid medium in the inner inlet channel 220, 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 inner direction of the inner inlet channel 220, and does not block the fluid medium flowing in the inner direction of the inner inlet channel 220. 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. 1 and 3, the impeller 300 includes: hub 310, first cover plate 320, second cover plate 330, and blades 340.

Specifically, the first cover plate 320 is disposed adjacent to the rear end cap 400, the second cover plate 330 is disposed adjacent to the drainage pump casing 100, the blades 340 are connected between the second cover plate 330 and the first cover plate 320, and the hub 310 is connected to the first cover plate 320. The second cover plate 330 is annular and disposed around the axis L of the impeller 300, and the surrounding portion of the second cover plate 330 is the central inlet 301, with a circumferential outlet 302 formed between the outer edge of the second cover plate 330 and the outer edge of the first cover plate 320. The impeller 300 has high structural reliability and bearing capacity, and has stronger reliability under high-flow and high-pressure operation.

Further, the inner edge of the second cover plate 330 is bent forward to form a front end tube 331, and the front end tube 331 is at least partially fitted into the inner inlet passage 220.

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 differential between the two will cause fluid medium to flow from the circumferential outlet 302 from above the second cover plate 330 to the central inlet 301, creating an unwanted backflow, known as annular gap backflow.

Since the washing pump 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 inlet passage 220, and the existence of this gap inevitably generates the above-described backflow of the annular gap. In order to reduce the occurrence of backflow in the annular gap, the front end pipe 331 is at least partially matched in the inner inlet channel 220, so that the backflow path is lengthened and narrowed, and the backflow resistance is increased to reduce the backflow amount of the annular gap, thereby reducing the work loss caused by backflow.

Optionally, a front sealing groove is formed on the peripheral wall of the front end tube 331, and the front sealing groove is correspondingly formed into a sealing structure. Thus, when the fluid medium discharged from the circumferential outlet 302 flows forward along the circumferential gap, the fluid medium is compressed due to the small volume when flowing forward to the position where the front seal groove is not provided, and the fluid medium expands due to the large volume when flowing to the position where the front seal groove is provided. The repeated compression and expansion of the fluid medium increases the flow resistance of the fluid medium, thereby effectively reducing the amount of flow from the circumferential outlet 302 to the central inlet 301.

Further, as shown in fig. 1, the wash pump 1000 defines a rear housing 270 therein, the rear housing 270 communicating with a side of the impeller housing 210 remote from the inner intake passage 220. Wherein, a driving shaft 710 is disposed on the rear cover 400, and the driving shaft 710 is connected with the hub 310 of the impeller 300. 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, as shown in fig. 1 and 3, the impeller 300 further includes: the back ring 370, the back ring 370 is annular and disposed around the axis L of the impeller 300, the back ring 370 being attached to the surface of the first cover plate 320 facing the back end cap 400, the back ring 370 fitting at least at the back end into the back cavity 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 the rear cover 400 is provided with mounting holes 409. More specifically, the driving motor 700 is mounted on the rear cover 400, and the driving shaft 710 of the driving motor 700 extends into the impeller housing 210 through the assembly hole 409, thereby improving the integration level. When the drive shaft 710 is assembled to the washing pump 1000, a sealing structure is required to be provided in the assembly hole 409, and the assembly 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.

Optionally, a rear seal groove is provided on the peripheral wall of the rear seat ring 370, and the provision of the rear seal groove corresponds to forming a sealing structure. In this way, when the fluid medium discharged from the circumferential outlet 302 enters the gap between the outer circumferential wall of the backseat ring 370 and the inner circumferential wall of the backseat chamber 270, the fluid medium repeatedly undergoes the processes of compression and expansion, increasing the flow resistance of the fluid medium, thereby effectively reducing the flow from the circumferential outlet 302 to the fitting hole 409.

In some embodiments, as shown in fig. 4, the blades 340 are disposed in a helical extension about the axis L of the impeller 300, with the edge of the blades 340 adjacent the axis L being a leading edge 341, with the distance between the leading edge 341 and the axis L increasing in a direction toward the central inlet 301. Thus, as the water flows axially into the central inlet 301, the leading edges 341 of the blades 340 progressively cut the water flow so that the water flow is diverted and then flows radially outwardly under centrifugal action. Therefore, the front edge 341 is arranged in this way, so that the water inlet resistance can be greatly reduced, and the energy consumption can be reduced.

Specifically, the whole blade 340 is a curved blade, such as a twisted sheet shape in three-dimensional space, the shape of the blade 340 is more flexible, and the blade can change towards the direction which is beneficial to pressurizing water flow, so that the flow resistance is effectively reduced, and the water flow characteristic in the impeller 300 is improved and the efficiency is improved on the premise of increasing the flow.

When the blades 340 are spirally twisted, the water flow is guided well, and the hydraulic impact loss is small. Fig. 5 shows a numerical simulation of an impeller 300, which can be seen to have a very smooth flow of water in the direction of the blades 340.

In the present embodiment, the number of the blades 340 is not limited, and for example, the number of the blades 340 may be arbitrarily selected from 4 to 8.

The impeller 300 may be shaped not limited to the above, but may be of other types, such as a straight blade type, a combined blade type, a semi-open type, etc.

In some embodiments, the main pump housing 200 is a scroll, and as shown in fig. 6, an annular channel from the outer periphery of the impeller 300 to the inner peripheral wall of the impeller housing 210 forms a scroll chamber 211 of the scroll, and the water outlet channel 280 forms a diffuser pipe of the scroll, and a separation between the scroll chamber 211 and the diffuser pipe is a scroll tongue 212. The cross-sectional area of the scroll 211 increases gradually in the direction of flow from the scroll 212 to the diffuser. The cross section of the scroll 211 herein refers to the cross section of the scroll 211 passing through the axis L of the impeller 300. Thereby, the flow rate pressure of the water flow can be gradually released, and the pressure head required for the washing pump 1000 can be obtained.

In the example of fig. 6 and 7, the scroll chamber 211 formed on the main pump housing 200 has a cross section similar to a trapezoid, and the shape of the cross section gradually changes at different positions of the scroll chamber 211. Wherein, the vortex chamber 211 starts from the vortex tongue 212 and is equally divided by 8 minutes along the flow direction of the water flow, each interval is 45 degrees to obtain a section, the section marks are from 1 to 8, and the sections at each mark position of the vortex chamber 211 in fig. 6 are formed in a one-to-one correspondence in fig. 7. Three additional sections are formed in the diffuser, numbered 9 through 11, with the sections at each numbered location in the diffuser in fig. 6 being formed in a one-to-one correspondence in fig. 7. The volute structure comprises the 11 sections, the reference numerals are respectively 1-11, the section shape is gradually changed from a trapezoid to a circle, and the section area is gradually increased from 1 to 11 in proportion.

Of course, in the solution of the present application, the main pump casing 200 may not be a scroll structure, and the cross section of the impeller cavity 210 may be a uniform cross section, for example, rectangular, pear-shaped, circular, etc.

In some embodiments, the wash pump 1000 is disposed vertically, the drain pump housing 100 is connected above the main pump housing 200, the rear end cap 400 is connected below the main pump housing 200, and the pump intake 114 and the water outlet channel 280 are located on the sides of the wash pump 1000.

That is, the wash pump 1000 is of a vertical type structure, and the wash pump 1000 adopts a side-in-side-out scheme, that is, the pump intake 114 is drawn in a side-horizontal direction and is discharged laterally from the water outlet channel 280. Thus, the washing pump 1000 has higher performance stability and more reasonable space layout.

Of course, the embodiment of the present application is not limited thereto, and the washing pump 1000 may be of a horizontal type.

For example, the washing pump 1000 may have a structure of up-in-down-out or up-in-side-out.

In some embodiments, as shown in fig. 1, sealing rings 810 are further provided between the main pump housing 200 and the rear end cover 400, and between the drainage pump housing 100, respectively, to improve the sealing performance.

In one particular embodiment, the wash pump 1000 is shown in the shape shown in FIG. 1. The washing pump 1000 is of a vertical structure, and the washing pump 1000 adopts a side-in side-out scheme. The pump casing comprises a main pump casing 200, a rear end cover 400 and a drainage pump casing 100, wherein the pump casing is of an upper-lower layered structure, the upper drainage pump casing 100 and a heating part 600 are integrated, so that better heating efficiency can be obtained, and meanwhile, generated local gas can be discharged through the main pump casing 200, so that the problem of cavitation noise is solved. In the main pump case 200, the impeller 300 and the scroll structure are hydraulically designed, the impeller 300 is provided with twisted three-dimensional modeling blades 340, the scroll 211 is of unequal cross-section design, and the fluid impact loss and the fluid induced vibration are reduced.

The pressure of the washing pump 1000 can be raised by 40% compared with the existing common washing pump. The efficiency of the existing washing pump is low, and the efficiency of the washing pump 1000 can be improved by 20%. In addition, the conventional washing pump has high vibration noise, and the washing pump 1000 can buffer the problem of vibration and cavitation vibration.

Therefore, the washing pump 1000 can simultaneously meet the requirements of large flow, high pressure, high efficiency, low energy consumption, low noise, low vibration, and the like. Meanwhile, due to the compact structural design, the heating system is integrated with the heating system, so that the volume of the whole machine is further reduced.

Hereinafter, a washing appliance a according to an embodiment of the present invention will be described with reference to the accompanying drawings.

As shown in fig. 8, a washing pump is disposed in the washing appliance a, and the washing pump is the washing pump 1000 described in the foregoing embodiment, and the structure of the washing pump 1000 will not be described again.

According to the washing electric appliance A provided by the embodiment of the invention, the washing pump 1000 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 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.

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 (13)

1. A wash pump, comprising:

the pump shell assembly comprises a main pump shell and a drainage pump shell which are sequentially arranged along the axial direction, an impeller accommodating cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller accommodating cavity is formed in one axial end of the main pump shell, the drainage pump shell is arranged at the end part of the main pump shell, a water inlet guide cavity communicated with the inner inlet channel is formed in the drainage pump shell, and the drainage pump shell is provided with a pump inlet communicated with the water inlet guide cavity;

The impeller is positioned in the impeller accommodating cavity and provided with a central inlet arranged towards the inner inlet channel;

The preposed functional piece is arranged in the water inlet guide cavity and comprises at least one of a heating piece and a guide piece.

2. The washing pump as claimed in claim 1 wherein an end face of the water inlet guide chamber opposite to the inner inlet passage is a guide chamber end face, and the front functional member includes a guide member provided on the guide chamber end face.

3. The wash pump of claim 2 wherein the flow guide comprises a flow guide boss extending along the axis of the impeller, the flow guide boss tapering in a direction toward the central inlet.

4. The wash pump of claim 1, wherein the pre-function comprises a drain, the drain comprising a drain spacer;

the outer peripheral surface of the water inlet guide cavity is a guide cavity peripheral surface, and the pump suction inlet and the drainage partition plate are arranged on the guide cavity peripheral surface and are positioned on two opposite sides of the inner inlet channel.

5. The wash pump of claim 1 wherein the pre-function comprises the heating element disposed at least partially around an axis of the impeller.

6. The wash pump of claim 5 wherein the heating element comprises: a first heat pipe extending around the axis of the impeller, and a second heat pipe connected to an end of the first heat pipe remote from the pump intake.

7. The washing pump as claimed in claim 5 wherein the drain pump housing forms a mounting tube on a side remote from the main pump housing, a portion of the heater element being located within the mounting tube, the powered end of the heater element being mounted at an end of the mounting tube.

8. The washing pump as claimed in claim 1, wherein an end face of the main pump housing facing the water inlet guide chamber is an auxiliary guide end face, the auxiliary guide end face is annular and curved, and the auxiliary guide end face is gradually protruded toward the water inlet guide chamber in a radial inward direction.

9. The washing pump as claimed in claim 1 wherein said main pump housing is a scroll, an annular passage from an outer periphery of said impeller to an inner peripheral wall of said impeller housing constituting a volute chamber of said scroll, said main pump housing having a water outlet passage to constitute a diffuser of said volute, a separation of said volute chamber and said diffuser being a volute tongue;

the cross-sectional area of the scroll chamber increases gradually from the scroll tongue to the diffuser in the direction of flow of water.

10. The wash pump of claim 1, wherein the impeller comprises:

A first cover plate;

The hub is connected with the first cover plate;

The second cover plate is annular and is arranged around the axis of the impeller, the surrounding part of the second cover plate is the central inlet, the second cover plate is positioned on one side of the first cover plate, which is close to the drainage pump shell, the inner edge of the second 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, and a circumferential outlet is formed between the outer edge of the second cover plate and the outer edge of the first cover plate;

and the blade is connected between the second cover plate and the first cover plate.

11. The wash pump as in claim 10 wherein said blades extend helically about an axis of said impeller, an edge of said blades adjacent said axis being a leading edge, a distance between said leading edge and said axis increasing in a direction toward said central inlet.

12. The washing pump of any one of claims 1-11 wherein the axis of the impeller is disposed vertically or laterally;

The main pump housing is open at one end far away from the drainage pump housing, the pump housing assembly further comprises a rear end cover, the rear end cover is connected to one end of the main pump housing far away from the drainage pump housing, and the impeller is mounted on the rear end cover.

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