CN218376920U - Washing pump and have its washing electrical apparatus - Google Patents

Abstract

The utility model discloses a washing pump and have its washing electrical apparatus. The method comprises 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 cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller cavity is arranged at 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 drainage cavity communicated with the inner inlet channel is formed in the drainage pump shell, and the drainage pump shell is provided with a pump suction inlet communicated with the water inlet drainage cavity; an impeller positioned within the impeller pocket, the impeller having a central inlet disposed toward the intake passage; leading function piece, leading function piece establishes the intracavity is drawn to the water, leading function piece includes at least one in heating member and the drainage piece. The washing pumps are axially arranged in layers, so that the washing pumps are beneficial to being arranged into a large-flow pump and can bear high pressure requirements; and a smoother inflow condition can be obtained, and the vibration and noise of the whole machine are reduced.

Description

Washing pump and have its washing electrical apparatus

Technical Field

The utility model relates to a washing electrical apparatus technical field, concretely relates to washing pump and have its washing electrical apparatus.

Background

In daily life of people, washing appliances such as a dish washer and the like can liberate hands of people and facilitate cleaning of daily necessities such as tableware and the like. The washing pump is used as a core component in the washing electric appliances and is responsible for the power source of the whole circulating water path, and the water outlet effect of the washing pump directly influences the washing effect. With the demand of people on the quality of life, the washing appliances will gradually enter more families in future life.

The conventional washing pump has some disadvantages due to structural limitation, such as insufficient flow rate of the washing pump, low washing efficiency, large vibration noise during operation, and excessive size of the washing pump if the flow rate is increased.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a washing pump and have its washing electrical apparatus, through improving the structure of washing pump, the size can not increase too big when being favorable to the washing pump to realize large-traffic, and improves washing efficiency, reduces vibration and noise.

According to the utility model discloses washing pump, include: the pump shell assembly comprises a main pump shell and a drainage pump shell which are sequentially arranged along the axial direction, an impeller cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller cavity is arranged at 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 drainage cavity communicated with the inner inlet channel is formed in the drainage pump shell, and the drainage pump shell is provided with a pump suction inlet communicated with the water inlet drainage cavity; an impeller positioned within the impeller pocket, the impeller having a central inlet disposed toward the intake passage; leading function piece, leading function piece establishes the intracavity is drawn to the water, leading function piece includes at least one in heating member and the drainage piece.

According to the utility model discloses washing pump through setting up the double-deck pump case that sets gradually along the axial, can avoid area too big on the one hand, can utilize drainage pump case guide rivers again, reduces strong whirl, imports the center of impeller along the axial with rivers through the interior passageway of advancing. So set up, rivers direction change is little, and the rivers route is short, and rivers resistance is low, the energy consumption is few, and velocity of flow flood peak loss is little, changes bigger pressure flood peak when helping the impeller operation, improves washing pump operating efficiency, helps the washing pump to satisfy large-traffic, high pressure requirement. When the water inlet guide cavity is internally provided with the drainage piece, the influence caused by the change of the flow area and the flow direction of water flow can be offset. When the water inlet guide cavity is internally provided with a heating element, the prepositive heating is facilitated. Both can be favorable to improving the washing efficiency of the washing pump and reduce the energy consumption.

In some embodiments, an end face of the water inlet guide cavity opposite to the internal inlet channel is a cavity guide end face, the front functional part comprises a flow guide part, and the flow guide part is arranged on the cavity guide end face.

In some embodiments, the flow director includes a flow directing boss extending along an axis of the impeller, the flow directing boss tapering in a direction toward the central inlet.

In some embodiments, the lead feature comprises a drain, the drain comprising a drain baffle; the peripheral surface of the water inlet guide cavity is the peripheral surface of the guide cavity, and the pump suction inlet and the drainage partition plate are arranged on the peripheral surface of the guide cavity and are positioned on two opposite sides of the internal inlet channel.

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

In some embodiments, the heating element comprises: the impeller comprises a first heat pipe and a second heat pipe, wherein the first heat pipe extends around the axis of the impeller, and the second heat pipe is connected to one end, far away from the pump suction inlet, of the first heat pipe.

In some embodiments, the pump body defines a mounting tube on a side remote from the main pump body, a portion of the heating element is located within the mounting tube, and an electrical connection end of the heating element is mounted to an end of the mounting tube.

In some embodiments, an end surface of the main pump casing facing the water inlet guide cavity is an auxiliary guide end surface, the auxiliary guide end surface is annular and curved, and the auxiliary guide end surface gradually protrudes towards the inside of the water inlet guide cavity in a radially inward direction.

In some embodiments, the main pump casing is a volute, an annular passage from the outer periphery of the impeller to the inner peripheral wall of the impeller cavity forms a volute chamber of the volute, the main pump casing is provided with a water outlet passage to form a diffuser pipe of the volute, and a separation part of the volute chamber and the diffuser pipe is a volute tongue; the cross-sectional area of the vortex chamber is gradually increased from the vortex tongue to the diffuser pipe along the flowing direction of the water flow.

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, close to the drainage pump shell, of the first cover plate, 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; a blade connected between the second cover plate and the first cover plate.

In some embodiments, the vanes extend helically about an axis of the impeller, the edges of the vanes adjacent 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 shell is opened at one end far away from the drainage pump shell, the pump shell assembly further comprises a rear end cover, the rear end cover is connected to one end, far away from the drainage pump shell, of the main pump shell, and the impeller is installed on the rear end cover.

According to the utility model discloses washing electric appliance, including the washing pump of above-mentioned embodiment.

According to the utility model discloses washing electrical apparatus through setting up above-mentioned washing pump, is favorable to improving work efficiency, reduces vibration, noise.

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 above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

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

FIG. 2 is a cut-away partial view of a wash pump according to an embodiment of the present 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 present invention;

fig. 5 is a simulation diagram of an impeller according to an embodiment of the present invention;

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

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

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

Reference numerals:

a washing electric appliance A,

A washing pump 1000, a pump shell 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 suction port 114, a mounting pipe 180,

A front functional part 1000C, a drainage part 160, a drainage boss 161, a drainage tube 162, a drainage inlet 163, a drainage baffle 168,

A main pump shell 200, an auxiliary leading end surface S3,

An impeller housing 210, a volute chamber 211, a volute tongue 212,

An inner inlet channel 220,

A rear seat cavity 270,

A water outlet channel 280,

A first mounting opening 290,

An impeller 300, an axis L of the impeller,

A central inlet 301, a circumferential outlet 302,

Hub 310, first cover plate 320, second cover plate 330, front end tube 331, vanes 340, leading edge 341, aft ring 370,

A rear end cover 400, an assembly hole 409,

A heating element 600, a first heat pipe 610, a second heat pipe 620,

Drive motor 700, drive shaft 710, sealing washer 810.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "central," "vertical," "lateral," "length," "left," "right," "inner," "outer," "axial," "radial," "circumferential," and the like are used in the orientation or positional relationship indicated in the drawings for convenience in describing the present invention and to simplify the description, but are not intended to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

The following describes a washing pump 1000 according to an embodiment of the present invention with reference to the drawings.

As shown in fig. 1, the washing pump 1000 includes: pump casing assembly 1000B, impeller 300, and forward function 1000C. The pump casing assembly 1000B comprises a main pump casing 200 and a drainage pump casing 100 which are sequentially arranged along the axial direction, wherein an impeller accommodating cavity 210 is defined in the main pump casing 200, and an inner inlet passage 220 communicated with the impeller accommodating cavity 210 is arranged at one axial end of the main pump casing 200. The drainage pump casing 100 is installed at the end of the main pump casing 200, a water inlet drainage chamber 110 communicated with the inner inlet passage 220 is formed in the drainage pump casing 100, and the drainage pump casing 100 has a pump inlet port 114 communicated with the water inlet drainage chamber 110. Located within the impeller cavity 210 is an impeller 300, the impeller 300 having a central inlet 301 disposed towards the inlet passage 220. A pre-functional member 1000C is provided in the water introduction chamber 110, and the pre-functional member 1000C includes at least one of the heating member 600 and the drainage member 160.

In the present application, the axis L of the impeller 300 is defined as the axis of the washing pump 1000 and the axis of the main pump casing 200. Such a limitation is only for convenience of expressing the orientation of the components in the washing pump 1000, and is not to limit the washing pump 1000, the impeller 300 in the washing pump 1000, and the main pump housing 200 to be in a rotary body shape. Wherein the impeller 300 rotates about its axis L when rotating. Therefore, the axial directions mentioned herein all refer to directions along 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 washing pump 1000 is a vertical pump. Of course, the present application does not exclude the solution in which the axis L of the impeller 300 is arranged in a horizontal direction, and the washing pump 1000 is a horizontal pump.

The pump casing assembly 1000B referred to in this application includes the main pump casing 200 and the suction pump casing 100 which are sequentially arranged 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 fact that the drain pump casing 100 is installed at the end of the main pump casing 200 means that the drain pump casing 100 is installed at the end of the main pump casing 200 where the inner passage 220 is provided, and the drain pump casing 100 may be installed on the end surface of the end of the main pump casing 200 or on the outer circumferential surface adjacent to the end surface, which is not limited herein.

Compare in single shell pump structure (namely among the scheme of prior art, the washing pump only includes main pump case and does not have the drainage pump case), this application makes rivers earlier get into the buffering in drainage pump case 100 after getting into washing pump 1000 through setting up drainage pump case 100, is favorable to rivers flow state to tend to stabilize impeller 300 in flowing to main pump case 200 again. The drainage pump casing 100 can play a drainage buffering role, which is helpful for the impeller 300 to bear the impact force of the large flow of water when the washing pump 1000 is designed for large flow. And if the impeller 300 runs and the water flow state is unstable, so that the rotating speed of the impeller 300 changes, the rotation speed change can aggravate the water flow fluctuation and even the reverse flow, and the drainage pump shell 100 at the upstream of the main pump shell 200 can provide a water flow buffering space, so that the water flow can tend to be stable in the water inlet guide cavity 110.

In the prior art, the washing pump also has a radially-nested pump structure, namely, the washing pump comprises a main pump shell and a drainage pump shell, the drainage pump shell is sleeved on the radial outer side of the main pump shell, and a water inlet drainage cavity between the main pump shell and the drainage pump shell is an annular cavity surrounding the main pump shell. After entering, the water flow generates circular 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 flow direction change for many times before the water flow enters the impeller is too much, and the water flow generates stronger rotational flow under the guidance of the annular cavity. However, the water flow in the direction of rotation has an adverse impact force on the impeller, which causes excessive wear of the impeller.

Compared with the radial nested pump structure, the drainage pump shell 100 is reserved in the application, a buffering and guiding space for water flow is formed, strong rotational flow is avoided, the impeller 300 can bear large-flow water flow impact force when the washing pump 1000 is designed in a large flow mode, and the washing pump 1000 can meet the requirements of large flow and high pressure. And main pump case 200 and drainage pump case 100 set up along axial range upon range of, help reducing area, easy to assemble, debug.

Here, an inner inlet passage 220 is arranged at one end of the main pump housing 200 facing the drainage pump housing 100, a central inlet 301 of the impeller 300 is arranged facing the inner inlet passage 220, the inner inlet passage 220 guides water flow to the impeller 300 along the axial direction, in addition, the drainage pump housing 100 is also arranged along the axial direction, the water flow enters the main pump housing 200 from the drainage pump housing 100 as a whole, the change of the water flow direction is small, the water flow path is short, the water flow resistance is low, the energy consumption is low, the loss of the flow speed water head is small, the impeller 300 can be converted into a larger pressure water head when in operation, and the operation efficiency of the washing pump 1000 is improved.

In the present application, a front functional component 1000C is disposed in the water inlet guiding cavity 110, the front functional component 1000C may include the heating component 600 and may also include the drainage component 160, and the front functional component 1000C may also include both the heating component 600 and the drainage component 160.

When the water inlet guide chamber 110 is provided with the flow guide member 160, it is obvious that the flow guide member 160 is used for guiding the water flow in the water inlet guide chamber 110 toward the water inlet passage 220. It can be understood that the water flow enters the water introducing chamber 110 from the outside, and the flow area of the water flow is suddenly increased. When the water flow in the inlet guide chamber 110 flows into the inner inlet passage 220 again, the flow area of the water flow is suddenly reduced. The flow guide 160 helps to guide the flow direction of the water flow during the flow process of the water flow, so that the water flow is automatically converged when guided by the flow guide 160, and helps to resist the adverse effect caused by the sudden change of the cross section of the shell of the pump shell assembly 1000B. There are also solutions where the water flow is also subject to diversion problems as it enters the water intake chamber 110. For example, when the pump inlet 114 is connected to the water inlet pipeline, if the water inlet pipeline is axially connected to the washing pump 1000, the space occupied by the washing pump 1000 is too long in the axial direction, so that the pump inlet 114 is usually disposed on the side of the drainage pump casing 100, and the water flow needs to turn 90 degrees into the inlet passage 220 when entering the drainage pump casing 100. If the water flow turns to smoothly inadequately, the over-violent rotational flow is generated, the water flow resistance is increased, the energy consumption is overlarge, the rotational flow has overlarge impact damage to the impeller, and the service life of the impeller is shortened.

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

In addition, when water enters the pump suction port 114, the water does not need to directly face the central inlet 301 of the impeller 300, the impact of the water entering on the impeller 300 is reduced, the water is guided by the drainage piece 160 in a buffering mode, and the abrasion is reduced.

Therefore, the layout structure of the drainage member 160 and the pump shell assembly 1000B is utilized in the scheme of the application, so that the working efficiency of the washing pump 1000 is improved, and vibration and noise are reduced.

When the water inlet guide cavity 110 is internally provided with the heating element 600, 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. And the rivers lead the intracavity 110 into water and experience the circulation change sudden change, and can obtain certain buffering when the heating member 600, can let rivers fully absorb the heat of heating member 600, improve the heat exchange rate.

Therefore, no matter the drainage member 160 or the heating member 600 is disposed in the water inlet drainage chamber 110, it is possible to improve the washing efficiency of the washing pump 1000 and reduce the power consumption.

In some embodiments, as shown in fig. 1, the main pump casing 200 is open at an end remote from the discharge pump casing 100, the casing assembly 1000B further comprises a back cover 400, the back cover 400 is attached to the end of the main pump casing 200 remote from the discharge pump casing 100, and the impeller 300 is mounted on the back cover 400.

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

The drainage pump shell 100 is provided with a pump suction port 114 and a second mounting port 113 which are communicated with the water inlet drainage cavity 110, and the second mounting port 113 covers the inner inlet channel 220.

In this application, the washing pump 1000 further includes a driving member (e.g., a driving motor 700 in fig. 1) for driving the whole impeller 300 to rotate around the axis L via 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 along 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 decreases and more water is sucked in, and the pressure at the circumferential outlet 302 increases to discharge water to the outside. The inward-outward direction mentioned herein means a direction close to the axis L is inward and a direction away from the axis L is outward in the radial direction of the impeller 300. The inner edge of each cover plate referred to herein refers to the edge closer to the axis L and the outer edge of each cover plate refers to the edge farther from the axis L.

Due to the continuous nature of the water flow, the water flow in the inlet guide chamber 110 is continuously sucked into the impeller 300 through the inlet passage 220 and the central inlet 301, and the water flow is continuously discharged from the circumferential outlet 302, and the discharged water flow obtains velocity energy and pressure energy and is discharged from the outlet passage 280. The impeller 300 applies work to the water flow, so that the washing pump 1000 has a certain lift. Here, the head refers to the energy gain 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 that of the existing product, 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 receiving cavity 210 through the first mounting port 290, and then the rear cover 400 may be fixedly coupled to the main pump case 200. The components to be loaded into the drain pump housing 100 may be loaded into the inlet guide chamber 110 through the second mounting port 113, and then the drain pump housing 100 may be fixedly coupled to the main pump housing 200. Thus, the washing pump 1000 is very convenient to assemble and maintain.

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

Specifically, the outer peripheral surface of the inlet water guide chamber 110 is a guide chamber peripheral surface S1, and a pump suction port 114 is formed on 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 cavity guide end surface S2, and the drainage member 160 is disposed on the cavity guide end surface S2. Reliably, the cavity leading end surface S2 can be a plane, so that the processing is convenient, other parts can be conveniently connected, and the positioning and the installation are convenient. In the scheme that does not exclude, the end surface S2 of the leading cavity is an arc surface, such as a hemispherical surface.

In some embodiments, as shown in fig. 1, the flow guide 160 includes a flow guide boss 161, the flow guide boss 161 extends along the axis L of the impeller 300, and the flow guide boss 161 tapers in a direction toward the central inlet 301 of the impeller 300.

To understand the function of the drainage bosses 161, further description is provided herein with reference to the orientation of the embodiment of fig. 1-2. As shown in fig. 1 to 2, the drainage pump casing 100 is disposed in the up-down direction, the pump suction port 114 is located at the left side of the drainage pump casing 100, and the bottom of the drainage pump casing 100 is provided with the second mounting port 113 and connected to the main pump casing 200. At this time, the drain pump case 100 serves to guide the water flow flowing in from the left side downward, turning the water flow by 90 degrees.

If the drainage pump case 100 is not provided with the drainage member 160, the water flows into the drainage pump case from the left and then flows to the right section of the peripheral surface S1 of the drainage chamber. In the process of flowing to the right, although part of water flows downwards under the driving of water pressure, a large amount of water flow generates right impact force on the peripheral surface S1 of the guide cavity. The water flow impact force is large, and the impact force fluctuates to a certain extent, so that the whole drainage pump shell 100 generates large vibration and noise. And the water flow can generate certain rotational flow when turning, the rotational flow is not beneficial to the stable operation of the impeller 300, and vibration and noise can be avoided during operation.

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

first, since the drainage boss 161 is tapered 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 flowing into the pump inlet 114 directly impacts the drainage boss 161, the drainage boss 161 can guide the part of the water to flow downwards, so that the water can flow along the drainage boss 161 to the inward channel 220, which is beneficial for the water to flow into the impeller 300 in the main pump shell 200 along the axial direction.

The majority of the water flow entering pump inlet 114 is split into two streams by diversion boss 161. A first drainage channel 101 is formed between the drainage boss 161 and the front section of the peripheral surface S1 of the drainage cavity, and a second drainage channel 102 is formed between the drainage boss 161 and the rear section of the peripheral surface S1 of the drainage cavity. After a part of the water flow is divided forward, the water flow flows to the right through the first drainage channel 101. After part of the water flow is divided backwards, the water flow flows rightwards through the second drainage channel 102. After the two flows are divided, the impact force to the right of the drainage pump casing 100 is reduced. When the two water flows meet, the impact acting forces of the two water flows are opposite in direction, so that a part of the impact acting forces can be mutually offset, and the impact force to the front and back directions of the drainage pump shell 100 is smaller. Therefore, compared with a scheme without the drainage boss 161, the scheme of the present application can greatly reduce the vibration and noise of the drainage pump casing 100.

In the process that water flows from left to right along the first drainage channel 101 and the second drainage channel 102, the water flow is driven by water pressure, guided by the drainage boss 161 and reversed by the squeezing action of the backflow water flow, and the water flow direction can smoothly flow along the axial inward inlet channel 220 by radial turning.

The drainage boss 161 is used for guiding the water flow flowing in from the pump suction port 114 to the first drainage channel 101 and the second drainage channel 102 after being divided, compared with the scheme without the drainage boss 161, the scheme with the drainage boss 161 reduces the flow area of the water flow, so that the water pressure is not increased sharply due to the fact that the water flow entering from the pump suction port 114 is not decreased sharply, and the water flow impact acting force is relieved.

Therefore, the drainage boss 161 is arranged to guide the water flow in the water inlet drainage cavity 110 in a split manner, so as to limit the flow area of the water flow, avoid the rapid drop of the flow speed and the rapid rise of the water pressure of the water flow, and enable the flow condition of the water flow to be stable during the guiding. After the diversion, the diversion of a single water flow is easier, and the impact force generated by the two water flows to the drainage pump shell 100 in the diversion process can be partially offset. Particularly, the drainage boss 161 is surrounded by the first drainage channel 101 and the second drainage channel 102, the flow state of water flow in the first drainage channel 101 and the second drainage channel 102 is stable, and the impact generated by the water flow in the drainage boss 161 is reduced by the buffering of the water flow in the first drainage channel 101 and the second drainage channel 102. Therefore, the overall vibration of the pump casing 100 is reduced, and noise is reduced.

Under the guidance of the circumferential surface S1 of the drainage cavity and the drainage boss 161, the water flow is smaller in rotational flow generated during reversing, the flow is smoother, the radial rotational flow generated during water flow direction conversion is eliminated as far as possible, and the impact loss in the flow channel is reduced.

And the guide bosses 161 smoothly guide the flow of water toward the main pump case 200, and the flow of water is diverted with a certain flow distance before entering the main pump case 200, during which the flow of water tends to be stable. Therefore, the overall size of the draft pump casing 100 does not need to be excessively large, and the washing pump 1000 can obtain high flow efficiency and reduce vibration and noise during operation.

In 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 drainage cavity end surface S2, which is favorable for guiding water to smoothly and smoothly flow to the drainage boss 161 along the arc transition surface, and then to guide the water to flow through the drainage boss 161 and the inner channel 220.

Specifically, the circumferential surface S1 of the leading cavity is in arc transition connection with the end surface S2 of the leading cavity, so that water flow can be guided to smoothly and stably flow to the circumferential surface S1 of the leading cavity along the arc transition surface, and then flow to the inward passage 220 by being guided by the circumferential surface S1 of the leading cavity.

In some embodiments, as shown in fig. 1, the flow guiding boss 161 is a solid of revolution, so that when the water flows along the flow guiding boss 161 in a rotating manner, the flow is smoother, the water flow resistance is smaller, and the water flow flows along the flow guiding boss 161 to the inward passage 220 is smoother.

In some embodiments, as shown in fig. 1, the peripheral surface S1 of the guide cavity is a cylindrical surface. Therefore, when water flows rotationally along the circumferential surface S1 of the guide cavity, the water flows more smoothly and the water flow resistance is smaller, so that the water flows more smoothly along the circumferential surface S1 of the guide cavity to the inward channel 220.

Optionally, the end of the flow inducing boss 161 is a spherical cap surface convexly disposed toward the second mounting port 113. Therefore, when the water flow around the whole angle of the circular drainage boss 161 flows through the spherical crown surface, the water flow is gathered to the axis of the drainage boss 161 along the spherical crown surface, and the water flow is restrained to flow along the axial direction.

Of course, the flow guide 160 in this application is not limited to the flow guide boss 161, and a flow guide tube 162 may be used, and the flow guide tube 162 may be disposed around the axis L of the impeller 300, and the flow guide tube 162 is opened at one end toward the inward passage 220. Alternatively, the drainage tube 162 is provided with a drainage inlet 163 at a side away from the pump suction inlet 114, so that the two divided water flows can enter the drainage tube 162 through the drainage inlet 163 after being merged and then be guided to the inward passage 220 by the drainage tube 162. This is beneficial to the turbulent water flow entering the draft tube 162 to be restrained and despin, so that the water flow enters the impeller 300 along the axial direction.

In some embodiments, as shown in fig. 1, drain 160 includes a drain baffle 168. The outer peripheral surface of the water inlet guide cavity 110 is a guide cavity peripheral surface S1, and the pump suction port 114 and the guide partition plate 168 are both disposed on the guide cavity peripheral surface S1 and located on opposite sides of the inner inlet passage 220. Therefore, the rotational flow formed when the water flows along the peripheral surface S1 of the guide cavity can be further weakened, and the water flow can be promoted to change direction and flow along the axial direction.

Specifically, the baffle 168 extends in a direction parallel to the axis L of the impeller 300, which further facilitates reversing the direction of flow to flow in the axial direction. Optionally, the drainage baffle 168 is disposed opposite to the pump suction port 114, and the drainage baffle 168 and the pump suction port 114 are disposed at two radial ends of the drainage boss 161, and are located at the two split-flow merging position, where the mutual impact force when the two flows merge can be reduced, which is beneficial to the two flows continuing to maintain the split-flow state and then reversing under relative squeezing. Thus, the flow-directing baffle 168 in this position not only does not create flow resistance, but also provides a greater axial flow direction.

Of course, the present disclosure is not limited thereto, and there may be a plurality of drainage baffles 168, and the plurality of drainage baffles 168 are distributed at intervals along the circumferential direction.

In some embodiments, the forward functional member 1000C includes a heating member 600, and the heating member 600 is at least partially disposed around the axis L of the impeller 300. Another type of flow directing member 160 can be formed using heating element 600.

In some embodiments, as shown in fig. 1, both the heating element 600 and the drainage element 160 are disposed in the inlet drainage chamber 110, and the heating element 600 is disposed at least partially around the drainage element 160, such that the water flows along the first and second drainage channels 101 and 102 and also flows along the heating element 600. The heating element 600 is arranged in such a way, on one hand, the flowing direction of water flow capable of guiding is reduced, the flowing resistance of the water flow is reduced, on the other hand, the heating element 600 is effectively integrated with the first drainage channel 101 and the second drainage channel 102, and the size of the washing pump 1000 is further reduced.

In some embodiments, the heating element 600 includes: 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 port 114. The arrangement of the first heat pipe 610 facilitates drainage, and the arrangement of the second heat pipe 620 can play a role in blocking flow, so that water flow is guided 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 two first heat pipes 610 are arranged at intervals along the axial direction of the impeller 300, each first heat pipe 610 is disposed around the flow guide 160, and the second heat pipe 620 is connected to ends of the two first heat pipes 610 away from the pump suction port 114.

With the arrangement, when water flows in from the pump inlet 114, the first heat pipe 610 can play a certain guiding role, and guides the water flow to the second heat pipe 620, so that the water flow can be smoothly turned, the water flow can be guided to the impeller 300 along the axis L direction of the impeller 300, the rotational flow of the water flow is reduced, the hydraulic loss of a 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 flowing efficiency is improved.

In the embodiment shown in fig. 1, there are two first heat pipes 610, and the two first heat pipes 610 are located at the upper and lower sides of the pump suction port 114, which is equivalent to that when water flows into the pump suction 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 flow of water to the second heat pipe 620. Furthermore, the second heat pipe 620 is an arc-shaped pipe, and the opposite ends of the middle of the second heat pipe 620 protrude towards the direction far away from the pump suction port 114, so that the concentrated stress at the joint of the first heat pipe 610 and the second heat pipe 620 can be reduced, a certain buffering process is provided for the diversion of water flow, and the formation of turbulence is reduced.

In some embodiments, the drain pump case 100 forms a mounting tube 180 on a side away from the main pump case 200, a portion of the heating member 600 is located within the mounting tube 180, and an electrical end of the heating member 600 is mounted to an end of the mounting tube 180. The installation pipe 180 not only is arranged to the heating member 600, but also the electric connection end of the heating member 600 is enabled to avoid water flow impact, and the connection reliability is improved.

In some embodiments, as shown in FIG. 1, the top or side of the draft pump casing 100 is formed with a mounting tube 180, the mounting tube 180 being positioned above the inlet chamber 110 and in communication with the inlet chamber 110.

Specifically, the heating member 600 is at least partially positioned within the mounting tube 180. By the arrangement, the space occupation of other chambers can be reduced, the structure compactness is improved, and the installation, sealing and power-on connection of the heating element 600 can be concentrated at the installation pipe 180 to avoid the intensive parts of other parts of the washing pump 1000.

Of course, the heating element 600 may be disposed on the main pump casing 200 or other positions in other embodiments of the present application, which is not limited herein. Of course, in the present application, it is preferable that the heating member 600 is provided on the casing 100 of the draft pump, and the pressure index, the efficiency index, and the noise index are more excellent.

In some embodiments, as shown in fig. 1, the end surface of the main pump casing 200 facing into the inlet guide chamber 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 inlet guide chamber 110 in a radially inward direction.

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

Through the cooperation of the auxiliary guide end surface S3 and the drainage pump shell 100, the water inlet guide 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 guide cavity 110 and only can flow to the main pump shell 200. The auxiliary leading end surface S3 is shaped like a horn, on one hand, water flow is promoted to gather towards the center along the auxiliary leading end surface S3 so as to be guided to the inner inlet channel 220, turbulence caused by the water flow along the radial outer flow is reduced, and the water flow is restrained to flow to the impeller 300 along the axial direction as far 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 flows along the first flow guide 101 and the second flow guide 102 as much as possible under the guidance of the auxiliary guide end surface S3, so that the water flow is finally guided to the main pump shell 200 along the flow guide 160 as much as possible. Therefore, the auxiliary guide end surface S3 also has the function of converging water flow, which is beneficial to weakening the radial rotational flow of the water flow, so that the water flow flows to the impeller 300 along the axial direction.

Specifically, the auxiliary leading end surface S3 is similar to a conical cylinder surface as a whole. In the direction towards the end surface S2 of the guide cavity, the auxiliary guide end surface S3 can be changed in an equal diameter way or in an unequal diameter way.

Alternatively, the vertical cross-sectional dimensions of the inner passage 220 may be the same or different throughout the axis L. Further alternatively, the size of the vertical cross section of the inner passage 220 may vary along a certain rule when the vertical cross section is different. For example, the inbound channel 220 is a straight tube channel. As another example, the inward passage 220 is a tapered passage that gradually decreases in diameter in a direction toward the impeller 300. At this time, since the flow of the fluid medium flowing into the inner inlet passage 220 is stable, the section of the inner inlet passage 220 is gradually reduced backward to accelerate the flow velocity, thereby increasing the acceleration of the impeller 300. For another example, the inward passage 220 is a diverging passage having a diameter gradually increasing in a direction toward the impeller 300. Such a configuration of the inner passage 220 may serve to slow the flow rate when the flow rate flowing into the inner passage 220 is excessive.

Optionally, the wash pump 1000 further includes a fairing rib disposed within the intake passage 220. It can be understood that the flow-straightening ribs can reduce the generation of rotational flow of the fluid medium in the inward passage 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 rotational flow, and improve the driving effect of the impeller 300 on the fluid medium, thereby improving the flow efficiency.

In the scheme of the present application, the arrangement manner of the flow straightening rib is not limited, and the structure of the flow straightening rib needs to have a blocking effect on the fluid medium flowing in the inward passage 220 in the radial direction, and does not block the fluid medium flowing in the inward passage 220 in the axial direction. For example, the fairing ribs are provided as cross partitions extending in the axial direction. For example, the flow regulating ribs may be cross partitions or mesh partitions in the shape of a Chinese character 'jing'. Alternatively, the rectifying rib may be in a cross shape or a straight shape, and the rectifying rib may also be in other shapes, which is not limited herein.

In some embodiments, as shown in fig. 1 and 3, the impeller 300 includes: a hub 310, a first cover plate 320, a second cover plate 330, and blades 340.

Specifically, a first cover plate 320 is positioned adjacent the rear end cover 400, a second cover plate 330 is positioned adjacent the draft pump casing 100, vanes 340 are coupled between the second cover plate 330 and the first cover plate 320, and the hub 310 is coupled to the first cover plate 320. The second cover plate 330 is annular and disposed about the axis L of the impeller 300, the second cover plate 330 surrounding a portion of the central inlet 301 forming a circumferential outlet 302 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, strong bearing capacity and stronger reliability under the high-flow and high-pressure industry.

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 in the inner intake passage 220.

It will be appreciated that when the pressure at the central inlet 301 decreases and the pressure at the circumferential outlet 302 increases, the pressure difference between the two will cause the fluid medium to flow from the circumferential outlet 302 to the central inlet 301 from above the second cover plate 330, creating an unwanted backflow, which is referred to 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 intake passage 220, and the existence of the gap inevitably causes the above-described annular gap backflow. For the production that reduces the annular gap backward flow, advance the passageway 220 including through the cooperation of front end pipe 331 at least part in this application, be favorable to making the backward flow route extension and narrow and small, utilize to increase the backward flow volume that increases backflow resistance and reduce the annular gap to can reduce the acting loss that the backward flow arouses.

Alternatively, the front end tube 331 is provided with a front seal groove on the outer peripheral wall thereof, and the front seal groove is provided as a seal 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 its small volume when flowing forward to the position where the front seal groove is not provided, and expands due to its large volume when flowing to the position where the front seal groove is provided. The fluid medium repeatedly undergoes the process of compression and expansion, increasing 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, a back seat cavity 270 is defined in the washing pump 1000, and the back seat cavity 270 communicates with a side of the impeller housing 210 away from the inner inlet passage 220. The rear cover 400 is provided with a driving shaft 710, and the driving shaft 710 is connected to the hub 310 of the impeller 300. The provision of the rear housing 270 provides sufficient space for the hub 310 and the drive shaft 710 connected to the hub 310 to be assembled and rotated, thereby reducing unnecessary wear.

Specifically, as shown in fig. 1 and 3, the impeller 300 further includes: an aft seat ring 370, the aft seat ring 370 being annular and disposed about the axis L of the impeller 300, the aft seat ring 370 being attached to a surface of the first cover plate 320 facing the aft end cover 400, the aft seat ring 370 fitting within the aft seat cavity 270 at least at the aft end. The provision of aft seat ring 370 enables aft seat cavity 270 to be substantially isolated from impeller cavity 210, reducing the flow of fluidic media discharged from circumferential outlet 302 into aft seat cavity 270.

It is understood that the rear end cap 400 is provided with a fitting hole 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 cavity 210 through the assembly hole 409, thereby improving the integration level. When the driving shaft 710 is assembled to the washing pump 1000, 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 a lubricant. By providing the backseat ring 370 to separate the backseat cavity 270 from the impeller pocket 210, the problem of leakage due to extrusion of fluid medium into the assembly hole 409 is reduced, and the contamination is also reduced.

Optionally, the outer peripheral wall of the rear seat ring 370 is provided with a rear seal groove, which is provided to form a sealing structure. Thus, when the fluid medium discharged from the circumferential outlet 302 enters the gap between the outer circumferential wall of the rear seat ring 370 and the inner circumferential wall of the rear seat 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 vane 340 extends spirally around the axis L of the impeller 300, the edge of the vane 340 adjacent to the axis L is a leading edge 341, and the distance between the leading edge 341 and the axis L gradually increases in the direction toward the central inlet 301. Thus, when the water flow enters the central inlet 301 along the axial direction, the leading edge 341 of the vane 340 gradually cuts off the water flow, so that the water flow is divided and flows outwards along the radial direction under the centrifugal action. Therefore, the leading edge 341 is arranged in this way, so that the water inflow resistance can be greatly reduced, and the energy consumption is reduced.

Specifically, the entire blade 340 is a curved sheet, and if the blade is a twisted sheet in a three-dimensional space, the blade 340 is more flexible in shape, and can be changed in a direction favorable for pressurizing water flow, so that the flow resistance is effectively reduced, the water flow characteristic in the impeller 300 is improved on the premise of increasing the flow rate, and the efficiency is improved.

When the blades 340 adopt the spiral twisted blades, the water flow is well guided, and the hydraulic shock loss is small. Fig. 5 shows a numerical simulation of an impeller 300, where it can be seen that the flow of water along the blades 340 is very smooth.

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

The shape of the impeller 300 is not limited to the above-mentioned embodiments, and may be other types of impellers, such as a straight blade type, a combined blade type, a semi-open type impeller, and the like.

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

In the example of fig. 6 and 7, the volute chamber 211 formed in the main pump casing 200 has a cross-section similar to a trapezoid, and the cross-sectional shape of the volute chamber 211 is gradually changed at different positions. Wherein, the vortex chamber 211 is divided into 8 minutes from the vortex tongue 212 along the flowing direction of the water flow, and a section is obtained at intervals of 45 degrees, the section numbers are from 1 to 8, and the section at each number position of the vortex chamber 211 in fig. 6 is formed in one-to-one correspondence with that in fig. 7. Three other sections are formed on the diffuser pipe, the section numbers are from 9 to 11, and the section at each numbered position of the diffuser pipe in fig. 6 is formed in one-to-one correspondence in fig. 7. The volute structure comprises the 11 sections, the number of the sections is 1-11 respectively, the section shape is gradually transited from a trapezoid to a circle, and the section area is gradually increased from 1 to 11 in proportion.

Of course, in the present application, the main pump housing 200 may not be a volute structure, and the cross section of the impeller cavity 210 may also be a uniform cross-sectional shape, such as a rectangle, a pear shape, a circle, and the like.

In some embodiments, the wash pump 1000 is vertically disposed, the drain pump housing 100 is attached above the main pump housing 200, the back cover 400 is attached below the main pump housing 200, and the pump intake port 114 and the outlet channel 280 are located on the sides of the wash pump 1000.

That is, the washing pump 1000 has a vertical structure, and the washing pump 1000 adopts a side-in side-out scheme, that is, the pump inlet 114 sucks in the side surface in the horizontal direction and discharges the liquid laterally from the water outlet passage 280. From this, the washing pump 1000 stability of performance is higher, and spatial layout is more reasonable.

Of course, the present disclosure is not limited thereto, and the washing pump 1000 may also be of a horizontal structure.

For example, the washing pump 1000 may be configured to be capable of being moved up and down or moved up and down.

In some embodiments, as shown in fig. 1, a seal 810 is disposed between the main pump casing 200 and each of the rear end cap 400 and the drain pump casing 100 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 and side-out scheme. The pump shell comprises a main pump shell 200, a rear end cover 400 and a drainage pump shell 100, the pump shell is of an upper-lower layered structure, the upper drainage pump shell 100 and a heating element 600 are integrated, better heating efficiency can be obtained, and meanwhile generated local gas can be discharged through the main pump shell 200, so that the problem of cavitation noise is solved. In the main pump casing 200, the impeller 300 and the volute structure are designed hydraulically, the impeller 300 is provided with twisted three-dimensional space modeling blades 340, and the volute chamber 211 is designed with unequal cross sections, so that the fluid impact loss and the fluid induced vibration are reduced.

Compared with the existing common washing pump, the pressure of the washing pump 1000 can be increased by 40%. 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 vibration noise of the existing washing pump is high, and the washing pump 1000 can buffer the problems of vibration and cavitation vibration.

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

The following describes a washing appliance a according to an embodiment of the present invention with reference to the accompanying drawings.

As shown in fig. 8, a washing pump is disposed in the washing appliance a, the washing pump is the washing pump 1000 according to the above embodiment, and the structure of the washing pump 1000 is not described herein again.

According to the utility model discloses washing electrical apparatus A through setting up above-mentioned washing pump 1000, is favorable to improving the washing effect, reduces energy consumption, reduces vibration, noise.

Specifically, the washing appliance a may be a dishwasher, a washing machine, or the like, and may be other devices requiring 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 dishwashers and washing machines according to embodiments of the present invention are known to those skilled in the art and will not be described in detail herein.

In the description herein, references to the description of the terms "embodiment," "example," etc., mean 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, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. 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: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims (13)

1. A washing 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 containing cavity is defined in the main pump shell, an inner inlet channel communicated with the impeller containing cavity is formed in one axial end of the main pump shell, the drainage pump shell is installed 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 suction inlet communicated with the water inlet guide cavity;

an impeller positioned within the impeller pocket, the impeller having a central inlet disposed toward the intake passage;

leading function piece, leading function piece establishes the intracavity is drawn to the water, leading function piece includes at least one in heating member and the drainage piece.

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

3. The wash pump of claim 2 wherein said flow director includes a flow directing boss extending along an axis of said impeller, said flow directing boss tapering in a direction toward said central inlet.

4. The wash pump of claim 1 wherein said forward function includes a drain, said drain including a drain baffle;

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

5. The wash pump of claim 1, wherein the pre-function includes 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: the first heat pipe extends around the axis of the impeller, and the second heat pipe is connected to one end, far away from the pump suction inlet, of the first heat pipe.

7. The washer pump as recited in claim 5 wherein said drain pump housing forms a mounting tube on a side remote from said main pump housing, a portion of said heating element being located within said mounting tube, an electrical connection end of said heating element being mounted to an end of said mounting tube.

8. The wash pump as claimed in claim 1, wherein an end surface of said main pump casing facing said water inflow guide chamber is an auxiliary guide end surface, said auxiliary guide end surface being annular and curved, said auxiliary guide end surface being provided to gradually project toward an inside of said water inflow guide chamber in a radially inward direction.

9. The washing pump as claimed in claim 1, wherein the main pump casing is a volute, an annular passage from the outer periphery of the impeller to the inner peripheral wall of the impeller housing forms a volute chamber of the volute, the main pump casing has a water outlet passage to form a diffuser pipe of the volute, and a volute tongue is provided at a separation part of the volute chamber and the diffuser pipe;

the cross-sectional area of the vortex chamber is gradually increased from the vortex tongue to the diffuser pipe along the flowing direction of the water flow.

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

a first cover plate;

the hub is connected with the first cover plate;

a second cover plate, wherein 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;

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

11. A wash pump according to claim 10, wherein the vanes extend helically about the axis of the impeller, the edges of the vanes adjacent the axis being leading edges, the distance between the leading edges and the axis increasing in a direction towards the central inlet.

12. A washing pump according to any of claims 1-11, characterized in that the axis of the impeller is arranged vertically or transversely;

the main pump shell is opened at one end far away from the drainage pump shell, the pump shell assembly further comprises a rear end cover, the rear end cover is connected to one end, far away from the drainage pump shell, of the main pump shell, and the impeller is installed on the rear end cover.

13. Washing appliance, characterized in that it comprises a washing pump according to any of claims 1-12.

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