CN220286039U - Impeller and range hood - Google Patents

Abstract

The utility model relates to an impeller and a range hood, which comprises a middle plate, wherein a plurality of inner blades are arranged on the middle plate, an air inlet angle beta 1 with an angle range of 5-25 degrees is formed between a first end of each inner blade and the middle plate, an air outlet angle beta 2 with an angle range of 80-95 degrees is formed between a second end of each inner blade and the middle plate, a plurality of outer blades are connected to the outer periphery of the middle plate, the outer blades surround each inner blade and are arranged along the height direction of the middle plate, when the impeller works, air flows from the air inlet angle beta 1 and flows into an air channel between the two adjacent outer blades along the air inlet angle beta 2 of each inner blade, and because the air inlet angle beta 1 of each inner blade is limited to 5-25 degrees and the air outlet angle beta 2 of each inner blade is limited to 80-95 degrees, when air flows from the inner blade to the outer blade, the impact force of the air flowing into the inner blade is reduced due to the fact that the air inlet angle beta 1 is smaller, and the effect of noise reduction is achieved; the air kinetic energy is effectively improved because the air outlet angle is beta 2, so that the air flow can smoothly enter the outer blades, and the air inlet quantity is increased.

Description

Impeller and range hood

Technical Field

The utility model relates to the technical field of kitchen appliances, in particular to an impeller and a range hood.

Background

The kitchen ventilator is a kitchen appliance for exhausting the smoke generated by cooking to the outside, and the impeller is a core component of the kitchen ventilator, and the performance of the kitchen ventilator directly affects the exhaust performance and working noise of the kitchen ventilator. The blades are arranged on the impeller, and the number of the blades directly affects the windward area of the impeller, so that the air inlet quantity is increased by increasing the number of the blades in the prior art, so that the air outlet quantity of the whole range hood is improved. However, the number of blades is too large, so that the air channel space between every two blades is reduced, and the noise is larger, and therefore, the air exhaust amount of the whole machine is improved in an optimized mode of increasing the number of the blades of the impeller, and the improvement difficulty is larger and larger.

In view of this, how to reduce the noise of the impeller and increase the air intake thereof is a technical problem to be solved.

Disclosure of Invention

The utility model aims to provide an impeller and a range hood, which can effectively reduce the noise of the impeller and increase the air intake of the impeller.

The technical problems are solved by the following technical scheme:

the impeller comprises a middle plate, a plurality of inner blades are arranged on the middle plate, an air inlet angle beta 1 with an angle range of 5-25 degrees is formed between a first end of each inner blade and the middle plate, an air outlet angle beta 2 with an angle range of 80-95 degrees is formed between a second end of each inner blade and the middle plate, a plurality of outer blades are connected to the outer periphery of the middle plate, the outer blades surround the inner blades and are arranged along the height direction of the middle plate, and air flow can enter from the air inlet angle beta 1 and enter an air channel between the two outer blades after flowing to the air outlet angle beta 2 along the inner blades.

Compared with the background technology, the impeller and the range hood have the following beneficial effects:

when the impeller rotates, air flow enters from the air inlet angle beta 1 and flows to the air outlet angle beta 2 along the inner blade and then enters the air channel between the two adjacent outer blades, and the air inlet angle beta 1 of the inner blade is limited in the range of 5-25 degrees and the air outlet angle beta 2 is limited in the range of 80-95 degrees, so that when air flows from the inner blade to the outer blade, the impact force of the air flow entering the inner blade is reduced due to the smaller air inlet angle beta 1, and the noise reduction effect is realized; the air kinetic energy is effectively improved because the air outlet angle is beta 2, so that the air flow can smoothly enter the outer blades, and the air inlet quantity is increased. Therefore, the impeller can effectively reduce noise and increase air inlet quantity; because the range hood disclosed by the utility model uses the impeller, the range hood disclosed by the utility model can effectively increase the exhaust air quantity of the whole range hood under the effects that the noise can be effectively reduced and the air quantity can be effectively increased by the impeller, so that the exhaust efficiency is improved.

In one embodiment, an airflow transfer passage is formed between one end of the inner blade, which is close to the outer blade, and the outer blade.

In one embodiment, the radius of the impeller is set to R and the cross-sectional length of the inner vane along its length is set to m, where m=0.3 to 0.6R.

In one embodiment, the middle disc comprises a large annular disc, a connecting part and a small annular disc, the outer periphery of the large annular disc is connected with the outer blade, the large annular disc is connected from the inner periphery of the large annular disc to one end of the small annular disc through the connecting part, the root part of the inner blade is inlaid on the connecting part, and the inner blade extends from the small annular disc to the large annular disc.

In one embodiment, the inner blade is a twisted curved blade, and an angle formed between a circular arc tangent line of a start point of a root of the twisted curved blade and a tangent line of an outer peripheral edge of the small annular disk is the air inlet angle β1.

In one embodiment, an angle formed between a circular arc tangent line of the end point of the root of the twisted curved blade and a tangent line of the outer peripheral edge of the large annular disk is the air outlet angle β2.

In one embodiment, a side surface of the outer blade facing the inner blade is an inner wall surface, opposite ends of the inner wall surface are respectively connected with the top and the bottom of the outer blade in a transitional manner through an arc, and the arc protrudes towards the inner blade.

In one embodiment, the arc length of the top end surface and the bottom end surface on the outer blade is set to D, and the arc length of the middle part is set to D, which is related to d=1.2 to 1.6D.

In one embodiment, the overall height of the outer blade is set to L1, and the height of the middle blade of the outer blade except for the arc transition connection is set to L2, so that the relationship between L1 and L2 is l2= 0.4L1-0.6L1.

The utility model also provides a range hood, which comprises a driving unit and the impeller, wherein the driving unit is in driving connection with a middle disc of the impeller so as to drive the impeller to rotate.

Drawings

FIG. 1 is a schematic view of the impeller of the present utility model;

FIG. 2 is a schematic view of an embodiment relating to the attachment of a center plate to an inner blade;

FIG. 3 is a schematic view showing the structure of the inner blade and the middle disc forming angles beta 1 and beta 2;

FIG. 4 is a top view of an embodiment relating to an impeller;

FIG. 5 is a cross-sectional view of an embodiment involving an impeller;

FIG. 6 is a second cross-sectional view of an embodiment involving an impeller;

FIG. 7 is a front view of an embodiment relating to an outer blade;

FIG. 8 is a schematic view of an embodiment relating to an outer blade;

fig. 9 is a schematic view showing another angle structure of the outer blade according to the embodiment.

Reference numerals illustrate: 10. a middle plate; 101. a small annular disc; 102. a large annular disc; 103. a connection part; 20. an inner blade; 30. an outer blade; 40. an upper end plate; 50. and a lower end plate.

Detailed Description

The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.

In the description of the present application, it should be understood that, if the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," etc. indicate or refer to an orientation or a positional relationship based on that shown in the drawings, it is merely for convenience of description and to simplify the description, and does not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present application.

In the description of the present application, unless otherwise indicated, the meaning of "a plurality" is two or more, and the meaning of "a number" is one or more.

In the description of the present application, unless explicitly stated or limited otherwise, the terms "mounted," "connected," and "connected" should be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art in a specific context.

In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, communication, etc. should be construed broadly, and those skilled in the art may reasonably ascertain the specific meaning of the terms in the present utility model by combining the specific contents of the technical solutions.

Examples:

in one embodiment, referring to fig. 1, an impeller includes a plurality of outer blades 30, an annular upper end plate 40 and an annular lower end plate 50, opposite ends of each outer blade 30 are respectively fixed on the upper end plate 40 and the lower end plate 50, and the plurality of outer blades 30 are arranged in parallel along the circumferential direction of the impeller; the impeller further includes a middle disk 10, wherein the middle disk 10 is located between the upper end disk 40 and the lower end disk 50, and the upper end disk 40, the middle disk 10 and the lower end disk 50 are coaxially disposed. The center plate 10 is provided with a plurality of inner blades 20, each outer blade 30 is provided to penetrate through the outer periphery of the center plate 10, and a plurality of outer blades 30 are provided around the inner blades 20 and along the height direction of the center plate 10. Wherein, an air inlet angle beta 1 with an angle range of 5-25 degrees is formed between the first end of the inner blade 20 and the middle disc 10, and an air outlet angle beta 2 with an angle range of 80-95 degrees is formed between the second end of the inner blade 20 and the middle disc 10. When the impeller rotates, air enters from the inlet angle beta 1, flows along the inner blade 20 to the outlet angle beta 2, and then enters the air duct between the two adjacent outer blades 30. As can be seen from the above, the impeller has the effect of reducing noise by limiting the inlet angle β1 of the inner vane 20 to 5-25 ° and the outlet angle β2 to 80-95 ° so that the impact force of the air flow entering the inner vane 20 is reduced due to the smaller inlet angle β1 when the air flows from the inner vane 20 to the outer vane 30; the air kinetic energy is effectively improved due to the larger air outlet angle beta 2, so that the air flow can smoothly enter the outer blades 30, and the air inlet quantity is increased. Therefore, the impeller of the embodiment can effectively reduce the noise of the impeller and increase the air inlet quantity of the impeller.

In one embodiment, the inlet angle β1 is 5 ° and the outlet angle β2 is 80 °; of course, in another embodiment, the air inlet angle β1 may be set to 25 ° and the air outlet angle β2 to 95 °. Alternatively, the intake angle β1 may be set to 20 °, and the exhaust angle β2 may be set to 90 °, which is not limited herein.

In one embodiment, referring to fig. 2, the middle plate 10 includes a large annular plate 102, a connecting portion 103 and a small annular plate 101 coaxially disposed, the outer periphery of the large annular plate 102 is connected to the outer vane 30, the large annular plate 102 is connected from the inner periphery thereof to one end of the small annular plate 101 by the connecting portion 103, the connecting portion 103 is in a horn-shaped structure, that is, the middle plate 10 is fixedly connected to the outer periphery (outer ring) of the small annular plate 101 by the smaller end of the horn-shaped connecting portion 103, the larger end is fixedly connected to the inner periphery (inner ring) of the large annular plate 102, the root of the inner vane 20 is inlaid on the connecting portion 103, and the inner vane 20 extends from the small annular plate 101 to the large annular plate 102, so that the air flow can enter from the beginning (end near the small annular plate 101) of the inner vane 20 and flow along the end (end near the large annular plate 102) of the inner vane 20 when the impeller rotates.

It should be noted that the connection portion 103 of the horn-like structure is beneficial for guiding the air flow into the inner blade 20, so that the air flow more smoothly flows from the inner blade 20 to the outer blade 30, and the air intake is further increased.

It should be noted that, the middle disk 10 is nested with a plurality of inner blades 20, the number of the inner blades 20 is limited between 8 and 16, the plurality of inner blades 20 increases the working area of the rotary impeller for air, and more air flows to the outer blades through the inner blades 20, so as to further improve the air intake of the impeller, improve the air discharge rate and increase the smoke discharge efficiency.

In one embodiment, the inner blades 20 are, but not limited to, twisted curved blades, which can enable the air flow to enter the impeller more smoothly, so as to increase the air intake of the impeller. As shown in fig. 3, the angle formed between the arc tangent line of the root of the twisted curved blade and the tangent line of the outer peripheral edge of the small annular disk 101 is the air inlet angle β1; the angle formed between the arc tangent of the end point of the root of the twisted curved blade and the tangent of the outer peripheral edge of the large annular disk 102 is the above-described air outlet angle β2. Therefore, under the action of the torsion curved surface blades, the air flow can efficiently enter the torsion curved surface blades from the air inlet angle beta 1 and flow to the air outlet angle beta 2, and the air inlet angle beta 1 is an angle formed between the arc tangent line of the starting point of the root of the torsion curved surface blades and the tangent line of the peripheral edge of the small annular disc 101, so that the effect of the air flow entering the torsion curved surface blades can be further improved; since the air outlet angle β2 is an angle formed between a circular arc tangent of the end point of the root of the twisted curved blade and a tangent of the outer peripheral edge of the large annular disk 102, the air flow from the inner blade 20 to the air inlet of the outer blade 30 can be further promoted.

In one embodiment, an airflow transmission channel is formed between one end of the inner vane 20, which is close to the outer vane 30, and the airflow transmission channel can share the airflow transmitted from the inner vane 20 to the outer vane 30, so as to improve the effect of entering the outer vane 30 by airflow, thereby improving the air intake effect of the impeller. Referring to fig. 4 and 5, the radius of the impeller of this embodiment is set to R, the cross-sectional length of the inner vane 20 along the length thereof is set to m, where m=0.3 to 0.6r, and m=0.3 to 0.6R defines the above-mentioned air flow passage. That is, it can be understood that m=0.3 to 0.6R can avoid the inner vane 20 from being too long, when the inner vane 20 is too long, air will flow from the inner vane 20 directly to the outer vane 30, resulting in the overlarge volume of air borne by the outer vane 30, because the distance (airflow transmission path) between the inner vane 20 and the outer vane 30 is used to share the air flow transmitted by the inner vane 20; when the air volume brought by the inner blades 20 is not received by the parts of the outer blades 30 near the inner blades 20, the air volume born by the parts of the outer blades 30 is smaller, so that the air volume among the outer blades 30 is uneven, and the air inlet effect is affected; m=0.3 to 0.6R can also avoid the phenomenon that the inner vane 20 is too short, and if the inner vane 20 is too short, the air flow flowing out from the inner vane 20 becomes unstable and turbulence is liable to occur.

In one embodiment, m=0.3r, the radius R of the impeller is the outer annular radius of either the annular upper end disk 40 or the annular lower end disk 50; of course, in other embodiments, m=0.6r, not limited herein.

In one embodiment, a side of the outer blade 30 facing the inner blade 20 is an inner wall surface of the outer blade 30, and opposite ends of the inner wall surface of the outer blade 30 are respectively connected with the top and the bottom of the outer blade 30 by arc transition, and the arc is convex to the inner blade 20. As can be specifically understood, referring to fig. 1, opposite ends of the inner wall surface of the middle part of the outer blade 30 are respectively connected with the top end surface of the top of the outer blade 30 and the bottom end surface of the bottom in an arc transition manner. Since the camber line is convex toward the inner blade 20, the top or bottom of the outer blade 30 is gradually widened toward the middle thereof, so that air smoothly and continuously enters the outer blade 30, and noise of abrupt air flow and rotation is reduced. Of course, the middle portions of the outer blades 30 have the same size in the length direction, so that the windward area of the outer blades 30 can be ensured not to be reduced.

In one embodiment, referring to fig. 8-9, any one of the plurality of outer blades is a three-dimensional curved-deflection design that curves toward an adjacent blade, rather than a straight blade design. Specifically, the arc length of both ends of the outer blade 30 in the height direction is different from the arc length of the middle section of the outer blade 30, wherein the arc length of the top end face of the top and the bottom end face of the bottom on the outer blade 30 is set to D, the arc length of the middle section is set to D, and the relationship is d=1.2 to 1.6D. Thus, too long or too short d can be avoided, and if too long d, the air inlet blades at the upper end and the lower end of the outer blade 30 have larger air inlet resistance, and noise is caused; if d is too short, the wind area of the whole impeller is too small, and the wind quantity is reduced.

In one embodiment, referring to fig. 6 or 7, the overall height of the outer blade 30 is set to L1, the height of the middle blade of the outer blade 30 except for the arc transition is set to L2, and then the relationship between L1 and L2 is l2= 0.4L1-0.6L1. Thus, the too short or too long L2 can be avoided, and if the L2 is too short, the wind area of the whole impeller is too small, and the air quantity is reduced; if L2 is too long, the air inlet blades and air inlet resistance at the upper and lower ends of the outer blades 30 are larger, and noise is caused.

On the basis of the structure, the utility model also provides a range hood, which comprises a driving unit and the impeller of any embodiment, wherein the driving unit is in driving connection with the impeller so as to drive the impeller to rotate. Specifically, the driving unit is a driving motor, and an output shaft of the driving motor is in driving connection with the inner ring of the small annular disc 101, so that the impeller can be driven to rotate. Because the range hood provided by the utility model uses the impeller, the range hood provided by the utility model can increase the exhaust quantity of the whole machine and improve the exhaust efficiency.

In the specific content of the above embodiment, any combination of the technical features may be performed without contradiction, and for brevity of description, all possible combinations of the technical features are not described, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The foregoing detailed description of the embodiments presents only a few embodiments of the present utility model, which are described in some detail and are not intended to limit the scope of the present utility model. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the utility model, which are all within the scope of the utility model. Accordingly, the scope of protection of the present utility model is to be determined by the appended claims.

Claims (10)

1. The impeller is characterized by comprising a middle plate (10), wherein a plurality of inner blades (20) are arranged on the middle plate (10), an air inlet angle beta 1 with an angle range of 5-25 degrees is formed between a first end of each inner blade (20) and the middle plate (10), an air outlet angle beta 2 with an angle range of 80-95 degrees is formed between a second end of each inner blade (20) and the middle plate (10), a plurality of outer blades (30) are connected to the outer periphery of the middle plate (10), the outer blades (30) surround the inner blades (20) and are arranged along the height direction of the middle plate (10), and air flow can enter from the air inlet angle beta 1 and enter an air channel between the two outer blades (30) after flowing to the air outlet angle beta 2 along the inner blades (20).

2. The impeller according to claim 1, characterized in that an air flow transfer passage is formed between the outer blade (30) and one end of the inner blade (20) adjacent to the outer blade (30).

3. Impeller according to claim 2, characterized in that the radius of the impeller is set to R and the inner vane (20) is set to m along its length cross-sectional length, where m = 0.3-0.6R.

4. The impeller according to claim 1, characterized in that the middle disc (10) comprises a large annular disc (102), a connecting portion (103) and a small annular disc (101), the outer periphery of the large annular disc (102) is connected with the outer blades (30), the large annular disc (102) is connected from the inner periphery thereof to one end of the small annular disc (101) by the connecting portion (103), the root portion of the inner blade (20) is inlaid on the connecting portion (103) and the inner blade (20) extends from the small annular disc (101) to the large annular disc (102).

5. The impeller according to claim 4, characterized in that the inner blade (20) is a twisted curved blade, the angle formed between the circular arc tangent of the start of the twisted curved blade root and the tangent of the peripheral edge of the small annular disc (101) being the inlet angle β1.

6. The impeller according to claim 5, characterized in that the angle formed between the arc tangent of the end point of the twisted curved blade root and the tangent of the peripheral edge of the large annular disc (102) is the outlet angle β2.

7. The impeller according to claim 1, characterized in that a side of the outer blade (30) facing the inner blade (20) is an inner wall surface, opposite ends of the inner wall surface being respectively connected with the top and bottom of the outer blade (30) by means of arc transitions, the arc protruding towards the inner blade (20).

8. The impeller according to claim 7, characterized in that the arc length of the top and bottom end surfaces on the outer blade (30) is set to D, the arc length of the middle part is set to D, and the relationship is d=1.2 to 1.6D.

9. The impeller according to claim 7, characterized in that the overall height of the outer blades (30) is set to L1, the intermediate blade height of the outer blades (30) except for the camber line transition is set to L2, and the relationship between L1 and L2 is l2= 0.4L1-0.6L1.

10. A range hood comprising a drive unit and an impeller according to any one of claims 1-9, said drive unit being in driving connection with said middle plate (10) of said impeller for driving said impeller in rotation.