CN112780581A

CN112780581A - Cleaning equipment

Info

Publication number: CN112780581A
Application number: CN202110082671.7A
Authority: CN
Inventors: 吴美全; 赵航; 龚明强; 程福萍
Original assignee: Midea Group Co Ltd; Jiangsu Midea Cleaning Appliances Co Ltd
Current assignee: Midea Group Co Ltd; Jiangsu Midea Cleaning Appliances Co Ltd
Priority date: 2021-01-21
Filing date: 2021-01-21
Publication date: 2021-05-11

Abstract

The invention provides cleaning equipment, and relates to the technical field of household appliances. The cleaning device includes a housing formed with an accommodating chamber; the impeller is arranged in the accommodating cavity and is fixedly connected with the shell; wherein, the impeller includes: a rotating shaft; the blade groups are arranged at intervals along the axial direction of the rotating shaft; each blade group comprises a plurality of moving blades and a plurality of static blades which are arranged at intervals along the axial direction, the moving blades are arranged at intervals along the circumferential direction and are fixedly connected with the rotating shaft, and the static blades are arranged at intervals along the circumferential direction; the fan cover surrounds the blade groups and is coaxial with the rotating shaft to form an air inlet and an air outlet; the plurality of stationary blades are fixedly connected with the fan cover. The cleaning device of the invention effectively improves the cleaning efficiency.

Description

Cleaning equipment

Technical Field

The invention belongs to the technical field of household appliances, and particularly relates to a cleaning device.

Background

The cleaning device sucks dust on the surface to be cleaned through the vacuumizing action of the fan. The impeller is used as a core component of the fan, can change performance parameters such as the flow direction, the speed, the pressure, the flow rate and the like of gas, and forms vacuum at the inlet of the fan, so that the external gas can be continuously sucked into the fan. The impeller comprises a rotating shaft and blades fixed on the rotating shaft, wherein the blades rotate under the driving of the rotating shaft and generate disturbance on the airflow, so that the airflow is accelerated and pressurized and is discharged from the outlet. The associated impeller design pressure ratio is low, resulting in inefficient cleaning equipment.

Disclosure of Invention

In view of the above, the present invention provides a cleaning device to solve the technical problem of how to improve the cleaning efficiency of the cleaning device.

The technical scheme of the invention is realized as follows:

an embodiment of the present invention provides a cleaning apparatus, including: a housing formed with an accommodation chamber; the impeller is arranged in the accommodating cavity and is fixedly connected with the shell; wherein the impeller comprises: a rotating shaft; the blade groups are arranged at intervals along the axial direction of the rotating shaft; each blade group comprises a plurality of moving blades and a plurality of static blades which are arranged at intervals along the axial direction, the moving blades are arranged at intervals along the circumferential direction and are fixedly connected with the rotating shaft, and the static blades are arranged at intervals along the circumferential direction; the fan cover surrounds the blade groups and is coaxial with the rotating shaft to form an air inlet and an air outlet; the plurality of stationary blades are fixedly connected with the fan cover.

Further, the direction from the air inlet to the air outlet is substantially the same as the axial direction.

Furthermore, the impeller further comprises a plurality of guide vanes arranged between the air inlet and the vane group in the axial direction, and the plurality of guide vanes are arranged at intervals along the circumferential direction.

Further, the outer diameter of the fan cover is 40-50 mm; the length of the fan cover is 50-60 mm.

Further, the impeller is a plastic piece.

Further, the rotation shaft includes: a rotating shaft; the wheel disc is sleeved on the outer side of the rotating shaft and is coaxially arranged with the rotating shaft; wherein the plurality of moving blades are fixedly connected with the outer wall surface of the wheel disc.

Further, the disk is integrally formed with the plurality of moving blades.

Further, the fan housing and the plurality of stationary blades are integrally formed.

Further, the cross-sectional area of the wheel disc gradually increases from the air inlet to the air outlet.

Further, a ratio of an extended length of the moving blade to an extended length of the stationary blade is a predetermined ratio.

The cleaning equipment comprises a shell and an impeller, wherein the impeller comprises a rotating shaft, a plurality of blade groups and a fan cover, and each blade group comprises a plurality of moving blades and a plurality of static blades which are arranged at intervals along the axial direction. The cleaning equipment provided by the embodiment of the invention realizes speed reduction and pressurization of gas by arranging the impeller with the multi-stage structure, and compared with a single-stage impeller structure, the multi-stage impeller structure can obtain a higher pressure ratio under the condition of not increasing the space volume of the impeller so as to improve the efficiency of the impeller and further improve the cleaning efficiency of the cleaning equipment. In addition, the cleaning equipment provided by the embodiment of the invention can fully utilize the space to arrange the impeller with the multi-stage structure, and the impeller with the multi-stage structure is applied to the field of cleaning equipment with smaller occupied space, so that the application range of the impeller with the multi-stage structure is widened.

Drawings

FIG. 1 is a schematic diagram showing the distribution of internal structural components of a related vacuum cleaner;

FIG. 2 is a schematic diagram of a working principle of a related blower;

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

FIG. 4 is an exploded view of an impeller according to an embodiment of the present invention;

FIG. 5a is a schematic, simplified forward blade view of an impeller;

FIG. 5b is a schematic, diagrammatic view of the rearward facing blades of the impeller;

FIG. 5c is a schematic sketch of a radial blade of an impeller;

fig. 6 is a schematic view of an internal structure of a fan housing of an impeller according to an embodiment of the present invention;

FIG. 7 is a cross-sectional view of an impeller according to an embodiment of the present invention;

FIG. 8a is a schematic view of a configuration of a guide vane of an impeller according to an embodiment of the present invention;

FIG. 8b is a schematic view of another embodiment of the guide vanes of the impeller of the present invention;

fig. 9 is another structural schematic view of the rotating shaft of the impeller according to the embodiment of the present invention.

Description of reference numerals:

1-cleaning equipment, 10-shell, 10A-air suction channel, 10B-air outlet, 20-rolling brush component, 30-separating device, 40-filtering device, 50-air outlet device, 60-fan, 61-impeller, 611-rotating shaft, 6111-rotating shaft, 6112-wheel disc, 612-blade group, 6121-moving blade, 6122-stationary blade, 613-fan housing, 613A-air inlet, 613B-air outlet, 614-guide blade, 62-volute, 63-machine shell, L1-outer diameter of fan housing, length of L2-fan housing, length of L3-moving blade, length of L4-stationary blade, and beta-blade outlet angle

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

The individual features described in the embodiments can be combined in any suitable manner without departing from the scope, for example different embodiments and aspects can be formed by combining different features. In order to avoid unnecessary repetition, various possible combinations of the specific features of the invention will not be described further.

In the following description, the term "first/second/so" is used merely to distinguish different objects and does not mean that there is a common or relationship between the objects. It should be understood that the description of the "upper", "lower", "outer" and "inner" directions as related to the orientation in the normal use state, and the "left" and "right" directions indicate the left and right directions indicated in the corresponding schematic drawings, and may or may not be the left and right directions in the normal use state.

It should be noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element. The term "coupled", where not otherwise specified, includes both direct and indirect connections. By "adjacent" is meant that the corresponding two parts are not in contact but the gap between the two parts is much less wide than either of the two parts.

The invention provides a cleaning device which can be a dust collector, a sweeping robot, a cleaning machine, a mopping machine, a floor washing machine and the like. It should be noted that the type of application scenario of the present invention does not limit the cleaning device of the present invention. The operation of the dust collector will be generally described below by taking the dust collector as an example.

The related cleaner 1 may include: the device comprises a shell 10, a rolling brush assembly 20, a separating device 30, a filtering device 40, an air outlet device 50 and a fan 60. An air suction channel 10A is formed in the shell 10, an air outlet 10B communicated with the interior of the shell and the outside is formed in the rear end of the shell 10, and a cavity formed in the air outlet device 50 is used for installing a fan 60 for vacuum extraction. During operation of the cleaner, it is driven to move over the surface to be cleaned, while the fan 60 performs a vacuum operation, so that the air pressure inside the housing 10 of the cleaner 1 is much lower than the air pressure of the external environment, thereby forming an air flow from the surface to be cleaned to the inside of the cleaner, and dust and debris on the surface are rolled up by the roll brush assembly 20, mixed into the air flow, is sucked into the interior of the housing through the dust suction inlet, and after the air flow with dust passes through the suction passage 10A, then enters a separating device 30, the separating device 30 separates and removes dust from the airflow with dust, the dust and other garbage are collected by the separating device 30, the clean air flow after separating the dust enters the air outlet device 50 through the filtering device 40, and in the air outlet device 50, the clean air flow flows into the fan 60, the blower 60 is blown to cool, then flows out of the blower 60, and finally is discharged to the outside through the air outlet 10B. The air flow is generated by the vacuum pumping of the fan 60 and is matched with the rolling brush assembly 20 to sweep dust, the air flow with the dust is sucked into the dust collector 1, then the dust is separated and removed through the separating device 30, finally the clean air flow is discharged into the air, and the cleaning and dust removal work of the dust collector on the whole surface to be cleaned is completed through the movement of the dust collector 1.

It can be understood that the efficiency of the fan directly affects the suction power of the cleaner, and the impeller, which is the core component of the fan, can change the air intake, pressure ratio and speed, and also directly affects the fan efficiency of the fan. The operation of the impeller 61 of the related blower 60 will be generally described below.

The impeller 61 may be a centrifugal impeller or an axial-flow impeller, and in the case of the centrifugal impeller 61, as shown in fig. 2, the fan 60 may include the impeller 61 and a scroll 62. The impeller 61 is disposed in the volute 62, the impeller 61 includes blades arranged at intervals, and an airflow channel, referred to as a blade channel, is formed between adjacent blades. When the impeller 61 rotates, the air in the blade path is disturbed, starts to rotate along with the impeller 61, and moves outwards under the action of centrifugal force, so that negative pressure is formed in the central area of the impeller 61, and the area is also the air inlet of the impeller. The outside air is sucked into the blade channel from the air inlet of the impeller 61 under the action of negative pressure, the blades have a guiding function, and performance parameters such as the flow speed, the pressure, the flow and the like of the air can be changed. The gas medium flowing in under the action of the blades acquires kinetic energy and pressure energy. The airflow is thrown out by the vane channels, enters the volute 62, is guided in a centralized manner, and is discharged from the air outlet of the volute 62.

In an embodiment of the invention, the cleaning apparatus provides a different impeller configuration than the associated fan. Specifically, the cleaning apparatus includes a housing 10 and an impeller 61. Specifically, the shape and structure of the housing 10 are arbitrary and can be set according to the specific application and application environment, for example, the height of the housing 10 of the household floor sweeping robot is small, so that the housing can be conveniently and flexibly moved into and out of a narrow space between furniture and a surface to be cleaned, and the center of gravity is low, so that the stability and reliability in the moving process can be effectively guaranteed, and the housing has good storage performance due to small size. The housing 10 may be of a generally cylindrical, rectangular or other configuration. The housing 10 may be a substantially thin-walled member, meeting structural lightweight requirements for the cleaning apparatus. The housing 10 is formed with a receiving cavity for receiving each structural component of the cleaning apparatus, and the housing 10 may also effectively protect each structural component.

The impeller 61 is disposed in the accommodating chamber and fixedly connected to the housing 10. Specifically, the impeller 61 is disposed in the accommodating cavity of the housing 10, and a negative pressure is formed in the accommodating cavity under the action of the impeller 61, so that dust on the surface to be cleaned is sucked into the accommodating cavity along with the external air flow.

As shown in fig. 3 and 4, the impeller 61 includes a rotation shaft 611, a plurality of blade groups 612, and a shroud 613. The fan housing 613 surrounds the plurality of blade sets 612 and is coaxial with the rotating shaft 611 to form an air inlet 613A and an air outlet 613B. Specifically, the hood 613 may be a substantially thin-walled member, and the shape and size of the hood 613 may be set according to actual needs, and the hood 613 encloses a hollow cavity with two open ends to form a channel for airflow circulation, where one open end is an airflow inlet end, i.e., the air inlet 613A, and the other open end is an airflow outlet end, i.e., the air outlet 613B. The rotating shaft 611 and the plurality of blade sets 612 are disposed in the cavity of the wind shield 613, and the airflow enters through the air inlet 613A, is decelerated and pressurized by the blade sets 612, and is finally discharged from the air outlet 613B.

Specifically, the rotating shaft 611 may be connected to a rotor of the motor to rotate under the driving of the motor. The rotation shaft 611 may be an axisymmetric structure to ensure stability of rotation, and a rotation center of the rotation shaft 611 is a symmetric axis of the rotation shaft 611. The structure of the rotating shaft 611 is flexible and various, and may be a structure with an equal cross section along the axial direction, a structure with a variable cross section area along the axial direction, or a structure combining a driving shaft and a wheel disc. The cross section means a plane perpendicular to the axial direction. The length of the rotating shaft 611 may be specifically set according to the specification of the fan housing 613.

As shown in fig. 4, a plurality of blade groups 612 are arranged at intervals in the axial direction of the rotating shaft 611. In addition, the plurality of representations is two or more. Specifically, each of the blade sets 612 represents a primary blade set of the impeller 61, and in the exemplary embodiment, two sets of blades are axially disposed, respectively a first-stage blade set and a second-stage blade set, in the inlet-to-outlet direction of the airflow, with the first-stage blade set and the second-stage blade set being spaced apart by a predetermined distance. The gas flows through each stage of blade group and is compressed stage by stage so as to increase the pressure of the gas. The first stage blade set and the second stage blade set may be identical or different in structure and shape, and in an exemplary embodiment, the first stage blade set and the second stage blade set are identical in structure, and each blade set 612 includes a plurality of moving blades 6121 and a plurality of stationary blades 6122 arranged at intervals in the axial direction. Specifically, a plurality of moving blades 6121 of each stage are disposed near the inlet end of the airflow, and a plurality of stationary blades 6122 are disposed near the outlet end of the airflow, that is, the blade sets 612 of the two stages are disposed in an alternating manner of the moving blades 6121 and the stationary blades 6122. The plurality of rotor blades 6121 and the plurality of stator blades 6122 of each stage serve as basic units of energy exchange.

As shown in fig. 4, a plurality of rotor blades 6121 are arranged at intervals in the circumferential direction and fixedly connected to the rotating shaft 611. Specifically, the plurality of moving blades 6121 may be disposed at equal intervals along the circumferential direction of the rotating shaft 611, and one end of the moving blades 6121 is fixedly connected to the rotating shaft 611, and may be integrally formed, or may be fixedly connected to the rotating shaft 611 by welding or gluing. The other end of the rotor blade 6121 is spaced a predetermined distance from the inner wall surface of the fan housing 613 so as to avoid interference with the fan housing 613. The rotor blade 6121 is installed on the rotating shaft 611, and in the operating state, the rotor blade 6121 is driven by the rotating shaft 611 to rotate at a high speed and apply work to the gas. The kinetic energy of the absolute velocity of the gas is increased and the kinetic energy of the relative velocity of the gas is decreased to increase the pressure of the gas by transmitting the compression shaft work to the gas flowing through the rotor blade 6121 by the rotor blade 6121. The rotor blades 6121 continuously apply work to the gas to increase the absolute velocity of the gas flow, thereby continuously supplying a high-velocity gas flow to the stator blades 6122.

The number of the rotor blades 6121 of each stage may be set according to actual needs, and the number of the rotor blades 6121 of each stage may be the same or different. The deflection direction of the first stage moving blade 6121 and the deflection direction of the second stage moving blade 6121 can be approximately the same, so that the stability of the airflow and the work efficiency of the blades are effectively ensured. The yaw direction refers to the angle of the exit angle β of the blade. The outlet angle β is the angle between the direction of extension of the outlet end of the blade and the tangential direction of the direction of rotation of the blade. Specifically, if beta is more than 90 degrees, the blade is a forward blade; if beta is less than 90 degrees, the blade is a backward blade; if β is 90 °, it is a radial blade. Specifically, the deflection direction of the blade can be flexibly set according to actual needs. As shown in fig. 5a, the two stages of moving blades 6121 can both adopt forward blades, the forward blade impeller has low efficiency and large noise, but the impeller has small size and low rotating speed under the same wind pressure and wind volume, and is suitable for medium and high pressure fans and occasions requiring small size of the fans; as shown in fig. 5b, the two stages of moving blades 6121 can both adopt backward blades, and the backward blades have high impeller efficiency, low noise and low possibility of overload when the flow is increased, so that the fan is suitable for large and medium-sized fans, but the fan needs larger impeller diameter or rotating speed when the air pressure and the air volume are the same; as shown in fig. 5c, the two-stage moving blades 6121 may be radial blades, and the radial blades are simple to manufacture, but have large impact loss and low efficiency.

In addition, the cross section of the moving blade 6121 may be twisted by a certain angle, that is, the moving blade 6121 has a certain deflection angle, and the deflection angle refers to the degree of curvature change of the blade in the blade length direction and the blade height direction. Specifically, the angle of the blade can directly influence the speed of the airflow, so that the performance of the fan is influenced, and the deflection angle of the blade can be set according to actual requirements. For a straight blade, the deflection angle of the blade is 0. For curved blades, the curvature of the blade may be variable or fixed. The deflection angle of the rotor blade 6121 in the first stage and the deflection angle of the rotor blade 6121 in the second stage may be the same or different. In the exemplary embodiment, the two stages of moving blades have the same degree of deflection to simplify the manufacturing process. The moving blade 6121 with a deflection angle can reduce the fan-shaped loss of the blade and improve the working capacity of the moving blade 6121.

As shown in fig. 6 and 7, a plurality of stationary blades 6122 are provided at intervals in the circumferential direction and adjacent to the rotating shaft 611, and the plurality of stationary blades 6122 are fixedly connected to the shroud 613. It should be noted that adjacent means that the two parts are not in contact but the gap width between the two parts is much smaller than the width of either of the two parts. Specifically, the plurality of stationary blades 6122 may be disposed around the rotating shaft 611 at equal intervals, the deflection directions of the stationary blades 6122 at each stage are substantially the same, so as to effectively ensure the work efficiency of the impeller, and the number and the deflection angle of the stationary blades 6122 at each stage may be the same or different, which is not limited herein. One end of the stationary blade 6122 is fixedly connected to the fan housing 613, which may be integrally formed, or may be fixedly connected to the fan housing 613 by welding or gluing. The other end of the stationary blade 6122 is spaced a predetermined distance from the outer wall surface of the rotating shaft 611 to avoid interference with the rotating shaft 611. That is, the stationary blades 6122 are stationary with respect to the shroud 613, and the rotor blades 6121 are rotatable with respect to the shroud 613 in an operating state.

It should be noted that the moving blade 6121 and the stationary blade 6122 at each stage maintain a preset spacing, an excessively small spacing may cause friction and collision between the moving blade 6121 and the stationary blade 6122 during rotation, an excessively large spacing may increase eddy current loss of the airflow in the blade, and a jet direction of the airflow in the gap may change, which may increase collision loss of the airflow. The proper spacing can be set according to actual needs.

Alternatively, as shown in fig. 7, the blade length (the distance in the vertical direction shown in fig. 7) of the rotor blade 6121 may be slightly longer than the blade length of the stator blade 6122. Specifically, by setting the length of the rotor blade 6121 to be longer than the length of the stator blade 6122, the gas ejected from the stator blade 6122 can be fully supplied to the rotor blade 6121 as much as possible, and collision and loss of leakage gas can be effectively reduced. However, the length of the rotor blade 6121 cannot be too long, so that a large number of vortices are prevented from occurring at the tip and the root of the rotor blade 6121.

The stationary blade 6122 may be a straight blade or a curved blade, and the stationary blade 6122 may change the flow area of the gas and the inlet airflow direction, thereby effectively ensuring the efficiency of the compressed gas. The high-speed gas flow from the moving blade 6121 is gradually decelerated in the stationary blade 6122, so that the kinetic energy of the absolute velocity of the gas can be partially converted into the pressure potential energy of the gas, thereby further increasing the pressure of the gas, i.e. the stationary blade 6122 can convert the velocity of the gas into pressure rise, and change the flow direction of the gas to adapt to the gas flow inlet direction of the moving blade of the next stage. The gas is compressed in the above-described operation from the first-stage rotor blades of the impeller 61 to the outlets of the stator blades of the last stage in a stepwise sequence. That is, the moving blade 6121 of each stage applies work to the gas flow, compresses the gas flow, then enters the stationary blade 6122 for speed reduction and pressurization, then enters the moving blade 6121 of the next stage for continuous compression and applying work, the previous working process is repeated, the pressure of the gas is increased by each stage of compression, and after multi-stage compression, the pressure of the gas can be greatly increased, so that the pressure ratio of the impeller is increased, wherein the pressure ratio is the ratio of the total outlet pressure and the total inlet pressure of the gas.

Optionally, outlet guide vanes and outlet diffusers may be installed at the end of the final stage to further increase the pressure of the gas.

It can be understood that the single-stage impeller needs to obtain a larger pressure ratio through a higher rotating speed and/or a larger volume, the space for accommodating the impeller of the cleaning equipment such as a dust collector is limited, and under the same volume space, compared with the single-stage impeller, the multi-stage impeller can reduce and pressurize the airflow in a step-by-step compression mode, and the wheel diameter ratio of the impeller is increased without expanding the space for accommodating the impeller of the dust collector, so that a higher pressure ratio can be obtained to increase the suction power of the cleaning equipment. Or, under the condition that the single-stage impeller and the multi-stage impeller have the same design pressure ratio, the structure volume of the multi-stage impeller can be designed to be smaller, so that the space for accommodating the impeller by cleaning equipment is saved, and the requirement of the miniaturization design of the structure is met.

In some embodiments, as shown in fig. 7, the direction from the inlet port 613A to the outlet port 613B is substantially the same as the axial direction. It can be understood that the centrifugal impeller is used for axial air intake and radial air outtake, which can change the flow direction of the inlet and outlet of the air flow, while the axial impeller is used for axial air intake and axial air outtake, which has the same flow direction, that is, the air intake direction and the air outtake direction of the axial impeller are both substantially the same as the extending direction of the rotating shaft 611. In the exemplary embodiment, the impeller 61 is an axial flow type impeller that achieves a higher flow rate than a centrifugal impeller. By setting the multistage impeller to an axial flow type structure, the air intake flow of the impeller is improved, the cleaning efficiency of the cleaning device is further improved, and the structure is simple and effective.

In some embodiments, as shown in fig. 6, the impeller 61 further includes a plurality of guide vanes 614 near the air inlet 613A and fixedly connected to the inner side of the wind shield 613. A plurality of guide vanes 614 are disposed between the inlet port 613A and the vane group 612. Specifically, one end of the guide vane 614 is fixedly connected to the inner wall surface of the fan housing 613, and may be integrally formed, or may be fixedly connected to the fan housing 613 by welding or gluing. The number, size, deflection direction and deflection angle of the guide vanes 614 can be set according to actual needs. The guide vane 614 is disposed near the air inlet 613A of the impeller, so that the air flow can enter the first stage moving blade 6121 at a proper angle, and the air flow loss is reduced. As shown in fig. 8a, the vane length of the guide vane 614 may be substantially the same as the radius of the fan housing 613 to increase the flow area of the guide vane 614, so that more airflow is guided by the guide vane 614 and enters the moving vane 6121; as shown in fig. 8b, the vane length of the guide vane 614 may be much smaller than the radius of the fan housing 613 to increase the rigidity of the guide vane 614. As shown in fig. 4, for the rotating shaft 611 with a longer axial length, the guide vane 614 may be sleeved at one end of the rotating shaft 611 through the hub, so that the rotation of the rotating shaft 611 is more stable and reliable, and an unstable phenomenon of the rotating shaft 611 swinging during the rotation process due to the cantilever beam effect caused by the too long length of the rotating shaft 611 is effectively avoided.

As shown in fig. 4, a plurality of guide vanes 614 are provided at intervals from the blade group 612 in the axial direction, and a plurality of guide vanes 614 are provided at intervals in the circumferential direction. Specifically, the plurality of guide vanes 614 may be arranged at equal intervals in the circumferential direction and spaced a predetermined distance from the two-stage vane group 612. The airflow first passes through guide vanes 614 and then enters the following vane set 612 at a flow rate and direction.

The guide vanes are arranged on the impeller to adjust the angle and the speed of the airflow of the air inlet, so that the airflow is injected into the vane group, the airflow loss is effectively reduced, the air inlet efficiency is further improved, and the impeller is simple in structure and convenient to process and manufacture.

In some embodiments, the outer diameter L1 of the hood is 40-50 mm. The length L2 of the fan cover is 50-60 mm. Specifically, the impeller 61 of the embodiment of the present invention may be a miniaturized impeller with a small volume structure to adapt to a cleaning device with a small space volume. Therefore, the application range of the impeller can be effectively improved, and the impeller is convenient to process and manufacture.

In some embodiments, impeller 61 is a plastic piece. Specifically, the impeller 61 may be a metal casting or a plastic part. Preferably, the impeller is produced from an easily die-cast material such as plastic. The impeller has a small volume structure, can meet the basic strength and rigidity design requirements by adopting a plastic material, and can also effectively reduce the manufacturing difficulty of a processing technology, shorten the production period of a product and save the material cost. In addition, compared with a metal piece, the plastic piece is lighter in weight under the condition of the same structure and volume, and the light-weight design requirement of the product of the cleaning equipment can be better met. And, the working of plastics does not have the risk of corrosion, and is better to the adaptability of environment, can effectively improve the life of impeller. Through setting the impeller to the working of plastics, the structure is simpler, and the manufacturing process degree of difficulty is little, with low costs, the quality is light and life is longer.

In some embodiments, as shown in FIG. 7, the spindle 611 includes a rotational shaft 6111 and a wheel disc 6112. The wheel disc 6112 is sleeved on the outer side of the rotating shaft 6111 and is arranged coaxially with the rotating shaft 6111, the plurality of moving blades 6121 are fixedly connected with the outer side wall surface of the wheel disc 6112, and the plurality of stationary blades 6122 are adjacent to the wheel disc 6112. Specifically, the rotating shaft 611 may be a split structure or an integrally formed structure, and the rotating shaft 6111 may be connected to a rotor of the motor to output shaft power as a driving member. The wheel disc 6112 is sleeved outside the rotating shaft 6111 and is fixedly connected with the rotating shaft 6111, and the fixed connection mode can be integrated molding, welding, bonding, key connection and the like. The shape and structure of the wheel disc 6112 can be flexibly set according to actual needs, for example, the wheel disc 6112 can be in a structural form with a variable cross-sectional area as shown in fig. 7, or in a structural form with an equal cross-section as shown in fig. 9, where the cross-section refers to a plane perpendicular to the axial extension direction. The blade group 612 is disposed between the wheel disc 6112 and the fan housing 613, wherein the rotor blade 6121 is fixedly connected to the wheel disc 6112, and one end of the stationary blade 6122 is spaced from the outer wall surface of the wheel disc 6112 by a preset distance. The disk 6112 may act as a bearing to support and position the rotor blade 6121.

Optionally, the guide vane 614 may be sleeved on the rotating shaft 6111 and disposed adjacent to the wheel disc 6112, so that the problem of rotational deflection caused by an excessively long axial length of the rotating shaft 6111 can be effectively avoided, and the running stability of the rotating shaft 6111 is improved.

The rotating shaft is arranged into a structure form of a rotating shaft and a wheel disc, and the rotating shaft transmits driving force to the moving blades from the wheel disc so as to enable the moving blades to rotate relative to the fan cover; and the wheel disc can effectively improve the torque of the rotating shaft, so that the rotating speed of the rotating shaft is improved.

In some embodiments, disk 6112 is integrally formed with a plurality of blades 6121. Specifically, in a working state, when the moving blade 6121 is brushed by an airflow acting force, the moving blade 6121 generates a bending moment, which causes fatigue fracture at a connection between the moving blade 6121 and the disk 6112, i.e., at a blade root. Compared with the connection modes such as welding or bonding, the integrally formed structure can improve the connection rigidity between the moving blade and the wheel disc, so that the connection firmness between the moving blade and the wheel disc can be effectively improved, and the service life of the impeller is prolonged. Compared with a large impeller, the impeller with a miniaturized structure can effectively reduce the difficulty of integrated manufacturing, and the manufacturing process is simple. Through setting up rim plate and moving blade integrated into one piece, effectively improve the stability that rim plate and moving blade are connected to the manufacturing process of this structure is simple, and the processing degree of difficulty is low.

In some embodiments, the shroud 613 is integrally formed with a plurality of stationary blades 6122. Specifically, in a working state, the stationary blade 6122 is also easily subjected to fatigue fracture at the blade root of the stationary blade 6122 under the scouring of the airflow, and the firmness of the connection between the fan housing 613 and the stationary blade 6122 can be improved through an integrally formed processing mode, so that the service life of the impeller is prolonged. The fan cover and the static blades are integrally formed, so that the connection stability of the fan cover and the static blades is effectively improved, the structure is simple in manufacturing process and low in processing difficulty.

In some embodiments, as shown in fig. 7, the cross-sectional area of the wheel disc 6112 gradually increases from the air inlet 613A to the air outlet 613B, and the guide vane 614 is disposed adjacent to the rotating shaft 6111. It should be noted that adjacent means that the two parts are not in contact but the gap width between the two parts is much smaller than the width of either of the two parts. Specifically, in the direction from the inlet to the outlet of the airflow, the flow area of the airflow gradually decreases, and the flow area of the airflow becomes smaller than that of the flow area with the equal cross section, so that the moving blade 6121 can further increase the absolute velocity of the airflow and increase the kinetic energy thereof, and the stationary blade 6122 can further convert the part of the kinetic energy into pressure potential energy, that is, convert the velocity into pressure rise, thereby further increasing the pressure ratio of the airflow. The pressure ratio of the airflow is further improved by arranging the wheel disc in a structure form that the cross-sectional area increases from the airflow inlet to the airflow outlet so as to reduce the flow area of the airflow.

In some embodiments, as shown in fig. 7, the ratio of the extended length L3 of the moving blade 6121 (the distance in the up-down direction shown in fig. 7) to the extended length L4 of the stationary blade 6122 is a predetermined ratio. Specifically, in the direction from the inlet to the outlet of the airflow, the flow area of the airflow is reduced and the airflow is gradually compressed under the same airflow flow rate, so that the pressure of the airflow is gradually increased, and the high pressure ratio is obtained. The blade length of the moving blade 6121 of each stage is greater than that of the stationary blade 6122, and the blade lengths of the adjacent stages are gradually decreased from the inlet to the outlet of the airflow. The gas is compressed by reducing the area of the gas flow passage to achieve a higher pressure ratio.

The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention.

Claims

1. A cleaning apparatus, comprising:

a housing formed with an accommodation chamber;

the impeller is arranged in the accommodating cavity and is fixedly connected with the shell;

wherein the impeller comprises:

a rotating shaft;

the blade groups are arranged at intervals along the axial direction of the rotating shaft; each blade group comprises a plurality of moving blades and a plurality of static blades which are arranged at intervals along the axial direction, the moving blades are arranged at intervals along the circumferential direction and are fixedly connected with the rotating shaft, and the static blades are arranged at intervals along the circumferential direction;

the fan cover surrounds the blade groups and is coaxial with the rotating shaft to form an air inlet and an air outlet; the plurality of stationary blades are fixedly connected with the fan cover.

2. The cleaning apparatus defined in claim 1, wherein the direction from the inlet to the outlet is substantially the same as the axial direction.

3. The cleaning apparatus as claimed in claim 2, wherein said impeller further includes a plurality of guide vanes disposed between said intake opening and said vane group in said axial direction, said plurality of guide vanes being disposed at intervals in said circumferential direction.

4. The cleaning apparatus as defined in claim 2, wherein the hood has an outer diameter of 40-50 mm; the length of the fan cover is 50-60 mm.

5. A cleaning device as claimed in claim 1 or 2, wherein the impeller is a plastic part.

6. The cleaning apparatus as claimed in claim 2, wherein the rotation shaft comprises:

a rotating shaft;

the wheel disc is sleeved on the outer side of the rotating shaft and is coaxially arranged with the rotating shaft;

wherein the plurality of moving blades are fixedly connected with the outer wall surface of the wheel disc.

7. The cleaning apparatus defined in claim 6, wherein the disk is integrally formed with the plurality of rotor blades.

8. The cleaning apparatus as defined in claim 1 or 2, wherein the fan housing is integrally formed with the plurality of stationary blades.

9. The cleaning apparatus defined in claim 6, wherein the wheel disc has a cross-sectional area that increases in a direction from the intake opening to the outtake opening.

10. The cleaning apparatus as claimed in claim 2, wherein a ratio of an extension length of the moving blade to an extension length of the stationary blade is a predetermined ratio.