CN110594169A

CN110594169A - Fan and heat exchange equipment with same

Info

Publication number: CN110594169A
Application number: CN201911000272.0A
Authority: CN
Inventors: 陈帆; 汤雁翔; 刘司轶; 邹先平; 李志宽
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2019-10-21
Filing date: 2019-10-21
Publication date: 2019-12-20

Abstract

The invention relates to a fan and a heat exchange device provided with the same, wherein the fan comprises: the volute comprises an accommodating cavity provided with an air inlet and an air outlet; the blade structure is rotatably accommodated in the accommodating cavity around a rotating axis, and two assembling gaps are respectively formed between two opposite ends of the blade structure in the rotating axis direction and the cavity wall of the accommodating cavity; wherein, the protruding two rings that are equipped with of chamber wall that hold the chamber, two keep off the ring and encircle two fitting gaps and the both ends that the blade structure is close to two fitting gaps respectively, keep off and form the choked flow passageway that communicates fitting gap between ring and the blade structure, the choked flow passageway is buckled and is extended in the axis of rotation direction. Above-mentioned fan, the choked flow passageway that forms through keeping off between ring and the blade structure has restricted the air current that holds in the chamber and has leaked through the fit-up gap to effectively reduce the leakage quantity of fan, and then improve the amount of wind and the work efficiency of fan.

Description

Fan and heat exchange equipment with same

Technical Field

The invention relates to the technical field of heating and ventilation equipment, in particular to a fan and heat exchange equipment with the same.

Background

The centrifugal fan is a machine which increases the pressure of gas and discharges the gas by means of the input mechanical energy, and is widely applied to ventilation, dust exhaust and cooling of factories, mines, tunnels, cooling towers, vehicles, ships and buildings, and cooling and ventilation of household electrical appliances such as air conditioning equipment. The multi-wing centrifugal fan is used as one of the centrifugal fans, and has the characteristics of large blade outlet angle, large flow coefficient, high pressure coefficient, small and compact structure, low noise and the like, so that the multi-wing centrifugal fan is widely applied to the field of heating and ventilation equipment.

The multi-wing centrifugal fan structure generally mainly comprises a volute and fan blades, and a certain assembly gap exists between the volute and the end faces of the fan blades, so that under the condition that the backpressure of the centrifugal fan is high, a part of air flow returns to a flow channel through the gap again, and the blades do work repeatedly on the air flow, so that the efficiency of the fan is reduced, and the efficiency of a tail end complete machine provided with the fan is reduced.

Therefore, under the background of advocating green life and low-carbon life, how to improve the efficiency of the multi-wing centrifugal fan and save electric energy is a problem to be solved urgently.

Disclosure of Invention

Therefore, it is necessary to provide a fan with high working efficiency and a heat exchange device provided with the fan, aiming at the problem that the multi-wing centrifugal fan is low in working efficiency.

A blower, comprising:

the volute comprises an accommodating cavity provided with an air inlet and an air outlet; and

the blade structure is rotatably accommodated in the accommodating cavity around a rotating axis, and two assembling gaps are respectively formed between the two opposite ends of the blade structure in the rotating axis direction and the cavity wall of the accommodating cavity;

the two baffle rings are respectively arranged on the wall of the accommodating cavity in a protruding mode, the two baffle rings respectively surround the two assembling gaps and the two ends, close to the two assembling gaps, of the blade structures, a flow blocking channel communicated with the assembling gaps is formed between the baffle rings and the blade structures, and the flow blocking channel is bent and extended in the direction of the rotating axis.

According to the fan, the flow blocking channel formed between the baffle ring and the blade structure limits the air flow in the accommodating cavity from leaking out through the assembly gap, so that the leakage of the fan is effectively reduced, and the air quantity and the working efficiency of the fan are improved; meanwhile, due to the fact that the spacing exists between the baffle ring and the vane structure, interference between the vane structure and the volute cannot occur.

In one embodiment, the distance between the slinger and the blade structure is less than the width of the assembly gap.

In one embodiment, the volute includes a first volute side plate, a second volute side plate and a volute enclosing plate, the first volute side plate and the second volute side plate are spaced in the rotation axis direction and are oppositely arranged, and the volute enclosing plate is connected between the first volute side plate and the second volute side plate;

the first volute side plate, the second volute side plate and the volute enclosing plate jointly enclose to form the accommodating cavity, one of the retaining rings is convexly arranged on one side of the accommodating cavity facing the first volute side plate, and the other retaining ring is convexly arranged on one side of the accommodating cavity facing the second volute side plate.

In one embodiment, the blade structure comprises a blade assembly and two water retaining rings positioned at two ends of the blade assembly, the two water retaining rings are arranged at intervals in the direction of the rotation axis, and the orthographic projection of any one of the retaining rings on the blade structure is at least partially overlapped with one of the water retaining rings.

In one embodiment, at least one of the baffle ring and the blade structure is provided with at least one flow blocking tooth protruding towards the other.

In one embodiment, at least one of the choke teeth is disposed at two opposite ends of each of the retainer ring and the blade structure in the direction of the rotation axis, and the choke teeth located on the retainer ring and the choke teeth located on the blade structure are spaced and staggered in the direction of the rotation axis.

In one embodiment, each of the baffle rings is provided with two choke teeth at intervals along the direction of the rotation axis, and two opposite ends of the blade structure in the direction of the rotation axis are provided with one choke tooth; the orthographic projection of the choked teeth on the baffle ring on the blade structure is between two choked teeth on the baffle ring.

In one embodiment, the minimum distance between the blocker teeth on the baffle ring and the blade structure is 3% -7% of the diameter of the blade structure.

In one embodiment, the minimum distance between the blocker teeth on the blocker ring and the blocker teeth on the blade structure is greater than 5 mm.

In one embodiment, the minimum distance between the baffle ring and the flow blocking teeth on the blade structure is 3% -7% of the diameter of the blade structure.

A heat exchange device comprises the fan.

Drawings

Fig. 1 is a schematic structural diagram of a fan according to an embodiment of the present invention;

FIG. 2 is a partial radial cross-sectional view of a wind turbine according to an embodiment of the present invention;

FIG. 3 is a partial radial cross-sectional view of a wind turbine according to another embodiment of the present invention;

fig. 4 is a schematic size diagram of the blower shown in fig. 3.

Detailed Description

To facilitate an understanding of the invention, the invention will now be described more fully with reference to the accompanying drawings. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

As shown in fig. 1, a heat exchange device (not shown) according to an embodiment of the present invention is provided with a fan 100 for discharging a gas, and the fan 100 is a bidirectional suction type centrifugal fan, preferably a multi-wing bidirectional suction type centrifugal fan. The structure of the middle blower 100 of the present application will be described below by taking a heat exchanger as an air conditioner as an example. The present embodiment is described as an example, and the technical scope of the present application is not limited thereto. It is understood that in other embodiments, the heat exchange device may also be embodied as other devices for installing the fan 100, which is not limited herein, and the fan 100 may also be another type of fan, such as a centrifugal fan with unidirectional suction. It should be noted that other structures of the heat exchange device are not the main points of the present application, and therefore are not described herein.

With continued reference to fig. 1, the blower 100 includes a volute 10 and a vane structure 30, the vane structure 30 is installed in the volute 10 and can rotate around a rotation axis in the volute 10 to realize gas discharge.

Specifically, the volute 10 includes a first volute side plate 12, a second volute side plate 14, and a volute closure 16. The first volute side plate 12 and the second volute side plate 14 are spaced and arranged oppositely, and the spacing direction of the first volute side plate 12 and the second volute side plate 14 is the same as the rotation axis direction of the vane structure 30. A volute enclosure plate 16 is connected between the first and second volute side plates 12, 14 and surrounds edges of the first and second volute side plates 12, 14. Therefore, the first volute side plate 12, the second volute side plate 14 and the volute enclosing plate 16 enclose together to form an accommodating cavity, and the first volute side plate 12, the second volute side plate 14 and the volute enclosing plate 16 are cavity walls of the accommodating cavity.

Further, the first volute side plate 12 and the second volute side plate 14 are both provided with circular air inlets communicating with the accommodating chamber, the two air inlets are respectively located on two sides of the blade structure 30 in the direction of the rotation axis, the central axis of each air inlet coincides with the rotation axis of the blade structure 30, the volute enclosing plate 16 is provided with an air outlet 162 communicating with the accommodating chamber, and the central axis of the air outlet 162 extends along the tangential direction of the blade structure 30.

Thus, in the rotation process of the vane structure 30, the external air enters the accommodating cavity from the two air inlets on the first volute side plate 12 and the second volute side plate 14, and then is discharged out of the accommodating cavity through the air outlet 162 under the action of the vane structure 30.

As shown in fig. 1 and 2, the blade structure 30 includes a blade assembly 32 and a water dam 34. The blade assembly 32 is a hollow cylindrical structure, and includes a plurality of blades arranged in sequence circumferentially around the axis of rotation of the blade structure 30. The water retaining ring 34 is a circular ring structure surrounding the rotation axis of the blade structure 30, and the width direction of the water retaining ring 34 is the same as the extension direction of the rotation axis. The two water retaining rings 34 are disposed at intervals in the direction of the rotation axis of the blade structure 30 and at two ends of the blade assembly 32, respectively, so as to prevent the blade structure 30 from being deformed too much during the rotation process, which may affect the normal operation of the fan 100.

Further, in order to avoid interference of the vane structure 30 with the scroll casing 10 during rotation, two fitting gaps 70 are respectively formed between opposite ends of the vane structure 30 in the direction of the rotation axis and the wall of the accommodating chamber. In the research process, the inventor finds that, due to the existence of the assembly gap 70, a certain proportion of airflow is not discharged out of the accommodating cavity through the air outlet 162, but returns to the blade structure 30 through the assembly gap 70 to form a circular flow, so that energy waste is caused, and the air volume and the efficiency of the fan 100 are reduced. Therefore, in order to solve the above problem, two baffle rings 18 are convexly disposed on the cavity wall of the accommodating cavity in the present application, the two baffle rings 18 respectively surround the two assembly gaps 70 and the two ends of the vane structure 30 close to the two assembly gaps 70, a flow blocking channel 90 communicating with the assembly gaps 70 is formed between the baffle rings 18 and the vane structure 30, and the flow blocking channel 90 is bent and extended in the rotation axis direction.

In this way, the flow blocking passage 90 formed between the baffle ring 18 and the blade structure 30 limits the air flow in the accommodating cavity from leaking out through the assembly gap 70, so as to effectively reduce the leakage amount of the fan 100, and further improve the air volume and the working efficiency of the fan 100; meanwhile, due to the spacing between the baffle ring 18 and the vane structure 30, interference between the vane structure 30 and the volute casing 10 is not caused.

In some embodiments, the distance between the blocker ring 18 and the vane structure 30 is less than the width of the fitting gap 70 (i.e., the height of the blocker passage 90 is less than the width of the fitting gap 70), thereby reducing the cross-sectional area of the airflow leakage path and effectively reducing the amount of airflow leakage.

Specifically, the two baffle rings 18 are both in a circular ring-shaped structure around the rotation axis of the blade structure 30, one of the baffle rings 18 is protruded from one side of the first volute side plate 12 facing the accommodating cavity, the other baffle ring 18 is protruded from one side of the second volute side plate 14 facing the accommodating cavity, and an orthographic projection of any one baffle ring 18 on the blade structure 30 is at least partially overlapped with one of the water retaining rings 34. Preferably, the orthographic projection of any one of the slingers 18 on the blade structure 30 coincides with one of the water dam 34. In this way, the baffle ring 18 surrounds the opposite ends of the blade structure 30 on the rotation axis and forms a flow blocking passage 90 together with the water deflector 34, and the angle formed between the flow blocking passage 90 and the assembly gap 70 is approximately 90 °.

As shown in fig. 3 and 4, in some embodiments, at least one of the retainer ring 18 and the blade structure 30 is provided with at least one spoiler tooth 50 protruding toward the other, thereby forming a spoiler channel 90 extending in a direction of the rotational axis while being bent. Thus, when the airflow flows through the flow blocking channel 90, the airflow is blocked by the flow blocking teeth 50 to change direction, and the vortex is generated in the flow blocking channel 90 to block the flow blocking channel 90, so that the flow resistance of the airflow is increased, the sealing efficiency is improved, and finally the air volume and the working efficiency of the fan 100 are improved.

Specifically, in some embodiments, each of the blocker teeth 50 extends circumferentially of the blocker ring 18 or the blade structure 30, and the blocker teeth 50 have a rectangular cross-section. It is understood that the specific shape of the choke passage 90 and the shape and number of the choke teeth 50 are not limited to the above, and may be set according to actual requirements.

Further, at least one choke tooth 50 is respectively disposed at both ends of each of the retainer ring 18 and the blade structure 30 in the direction of the rotation axis, and the choke teeth 50 located at the retainer ring 18 and the choke teeth 50 located at the blade structure 30 are spaced and staggered in the direction of the rotation axis, so that difficulty of airflow flowing through the choke passage 90 is further increased.

Specifically, in one embodiment, each baffle ring 18 is provided with two choke teeth 50 at intervals along the central axis direction of the blade structure 30, two opposite ends of the blade structure 30 in the rotation axis direction are provided with one choke tooth 50, and an orthographic projection of the choke teeth 50 of the blade structure 30 on the baffle ring 18 is located between the two choke teeth 50 of the baffle ring 18. In this way, the two choke teeth 50 located on the baffle ring 18 and the choke teeth 50 located on the blade structure 30 are alternately arranged to form the "zigzag" shaped choke passage 90, so that the effect of blocking the airflow is good.

In other embodiments, three choked teeth 50 may be spaced apart from each of the retainer rings 18, two choked teeth 50 may be disposed at opposite ends of the blade structure 30 in the direction of the rotation axis, and one choked tooth 50 may be disposed at each of the retainer rings 18, and two choked teeth 50 may be disposed at opposite ends of the blade structure 30 in the direction of the rotation axis.

As shown in fig. 4, in some embodiments, the minimum distance L1 between the blocker teeth 50 of the retainer ring 18 and the blade structure 30 is 3% to 7% of the diameter D of the blade structure 30, and the minimum distance L2 between the blocker teeth 50 of the retainer ring 18 and the blocker teeth 50 of the blade structure 30 is greater than 5mm, so as to prevent the blade structure 30 from being deformed during operation and interfering with the retainer ring 18. Moreover, when the distance L3 between the retainer ring 18 and the choker teeth 50 of the vane structure 30 is too large, the sealing effect is weakened, and when the distance L3 between the retainer ring 18 and the choker teeth 50 of the vane structure 30 is too small, the vane structure 30 is likely to interfere with the volute 10 during operation, so that the minimum distance L3 between the retainer ring 18 and the choker teeth 50 of the vane structure 30 is 3% to 7% of the diameter D of the vane structure 30. It will be appreciated that the specific dimensions of the blocker ring 18 and the blocker teeth 50 may be set as desired.

Above-mentioned fan 100 and be equipped with its indirect heating equipment, the setting of the choked flow passageway 90 of buckling in fan 100 can effectively restrain the high-pressure draught in spiral case 10 from getting back to blade structure 30 again from the fit-up gap 70 between blade structure 30 and spiral case 10 to effectively reduce the air current and leaked, effectively improved the amount of wind and the little efficiency of work of fan 100, and then improved indirect heating equipment's radiating efficiency, improved indirect heating equipment's life.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims

1. A fan, comprising:

the volute (10) comprises an accommodating cavity provided with an air inlet and an air outlet (162); and

the blade structure (30) is rotatably accommodated in the accommodating cavity around a rotating axis, and two assembling gaps (70) are respectively formed between the two opposite ends of the blade structure (30) in the rotating axis direction and the cavity wall of the accommodating cavity;

the two baffle rings (18) are convexly arranged on the cavity wall of the accommodating cavity, the two baffle rings (18) respectively surround the two assembling gaps (70) and the two ends, close to the two assembling gaps (70), of the blade structure (30), a flow blocking channel (90) communicated with the assembling gaps (70) is formed between the baffle rings (18) and the blade structure (30), and the flow blocking channel (90) is bent and extended in the direction of the rotating axis.

2. The fan according to claim 1, characterized in that the distance between the baffle ring (18) and the blade structure (30) is smaller than the width of the fitting gap (70).

3. The fan according to claim 1, wherein the volute (10) comprises a first volute side plate (12), a second volute side plate (14), and a volute bulkhead (16), the first volute side plate (12) and the second volute side plate (14) being spaced apart and disposed opposite in the direction of the rotational axis, the volute bulkhead (16) being connected between the first volute side plate (12) and the second volute side plate (14);

the first volute side plate (12), the second volute side plate (14) and the volute enclosing plate (16) jointly enclose to form the accommodating cavity, one of the retaining rings (18) is arranged in a protruding mode, the first volute side plate (12) faces towards one side of the accommodating cavity, and the other retaining ring (18) is arranged in a protruding mode, the second volute side plate (14) faces towards one side of the accommodating cavity.

4. The fan according to claim 1, wherein the blade structure (30) comprises a blade assembly (32) and two water retaining rings (34) at two ends of the blade assembly (32), the two water retaining rings (34) are arranged at intervals in the direction of the rotation axis, and the orthographic projection of any one of the water retaining rings (18) on the blade structure (30) is at least partially overlapped with one of the water retaining rings (34).

5. The fan according to claim 1, characterized in that at least one of the baffle ring (18) and the blade structure (30) is provided with at least one flow-blocking tooth (50) protruding towards the other.

6. The fan according to claim 5, wherein each of the baffle ring (18) and the blade structure (30) is provided with at least one of the blocker teeth (50) at opposite ends in the direction of the rotational axis, and the blocker teeth (50) located at the baffle ring (18) and the blocker teeth (50) located at the blade structure (30) are spaced and staggered in the direction of the rotational axis.

7. The fan according to claim 6, wherein each baffle ring (18) is provided with two baffle teeth (50) at intervals along the direction of the rotation axis, and the opposite ends of the blade structure (30) in the direction of the rotation axis are provided with one baffle tooth (50); the orthographic projection of the blocking tooth (50) of the blade structure (30) on the baffle ring (18) is between two blocking teeth (50) of the baffle ring (18).

8. The fan according to claim 6, characterized in that the minimum distance of the blocker teeth (50) located on the baffle ring (18) with respect to the blade structure (30) is 3-7% of the diameter of the blade structure (30).

9. The fan according to claim 6, characterized in that the minimum distance of the blocker teeth (50) located on the baffle ring (18) with respect to the blocker teeth (50) located on the blade structure (30) is greater than 5 mm.

10. The fan according to claim 6, characterized in that the minimum distance of the baffle ring (18) with respect to the blocker teeth (50) of the blade structure (30) is between 3% and 7% of the diameter of the blade structure (30).

11. A heat exchange device comprising a fan according to any one of claims 1 to 10.