Compressor impeller, centrifugal compressor and air conditioner

Abstract

The present invention provides a compressor impeller, a centrifugal compressor and an air conditioner, relating to the technical field of compressors, and solving the technical problem in the prior art that when the compressor impeller rotates, the generated noise is relatively large. The compressor impeller includes an impeller hub and blades, wherein the blades are distributed at intervals along the circumferential direction of the impeller hub, and the blades are unevenly distributed along the circumferential direction of the impeller hub. The present invention is used to reduce the noise generated by the impeller during the operation of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a compressor impeller, a centrifugal compressor provided with the impeller, and an air conditioner. Background Art

[0002] Centrifugal compressors have the advantages of large capacity, simple and compact structure, high reliability, etc., and are widely used in fields such as comfort air conditioners, equipment cooling, northern heating, district cooling, etc. With the rapid development of the industrialization process, centrifugal compressors are gradually developing towards large-scale and high-speed, and the resulting noise problems are becoming more and more serious. Noise not only affects the physical health of workers, but also causes noise pollution to the surrounding environment. Therefore, the development and research of low-noise centrifugal compressors is a very necessary task.

[0003] There are many reasons for centrifugal compressors to generate noise. Aerodynamic noise is the most common noise source of centrifugal compressors. The various losses caused by the high-speed rotation of the centrifugal compressor impeller and the flow of the medium in the flow passage, and the aerodynamic static-dynamic interference noise generated by the impeller and the diffuser all belong to aerodynamic noise.

[0004] One of the effective ways to control the noise of centrifugal compressors is to control its noise source. The periodic action of the impeller wake and the diffuser is the reason why the fundamental frequency (blade passing frequency) noise becomes the main aerodynamic noise of centrifugal compressors. In order to reduce the noise peak at the fundamental frequency, this patent uses the method of an unequal pitch impeller to disperse the noise peak at the fundamental frequency, thereby reducing the total noise level. Summary of the Invention

[0005] The purpose of the present invention is to provide a compressor impeller, a centrifugal compressor provided with the impeller, and an air conditioner, which solve the technical problem that the noise generated is relatively large when the compressor impeller rotates in the prior art. The many technical effects that can be produced by the preferred technical solutions provided by the present invention are described in detail below.

[0006] To achieve the above purpose, the present invention provides the following technical solutions:

[0007] A compressor impeller provided by the present invention includes an impeller hub and blades. Among them, the blades are spaced apart along the circumferential direction of the impeller hub on the impeller hub, and the blades are non-uniformly distributed along the circumferential direction of the impeller hub.

[0008] Further, the number of the blades is N, and along the circumferential direction of the impeller hub, the N blades are divided into m groups, and the blades in each group are respectively arranged along the circumferential direction of the impeller hub according to a preset interval rule.

[0009] Further, the blades in each group are the same, and the blades in each group are arranged at the same interval regularly along the circumferential direction of the impeller hub.

[0010] Further, m is an even value.

[0011] Further, one end of the side where the blade is connected to the impeller hub and close to the air inlet of the compressor wheel is the reference end. The line passing through the reference end and the central axis of the impeller hub and perpendicular to the central axis is the reference line. The included angle between two adjacent reference lines is the blade circumferential angle. The absolute value of the difference between the blade circumferential angles of any two blades of the compressor impeller is not greater than a certain preset value.

[0012] Further, the absolute value of the difference between the blade circumferential angles of any two blades of the compressor impeller is not greater than 5°.

[0013] Further, one end of the side where the blade is connected to the impeller hub and close to the air inlet of the compressor wheel is the reference end. The line passing through the reference end and the central axis of the impeller hub and perpendicular to the central axis is the reference line. The number of the blades is an even number, and any one of the reference lines in the radial direction of the compressor impeller passes through the reference ends of two blades.

[0014] Further, the compressor impeller is made of a metal material.

[0015] A centrifugal compressor includes the compressor impeller as described above.

[0016] An air conditioner includes the compressor impeller as described above.

[0017] The present invention provides a compressor impeller, which includes an impeller hub and blades. The blades are unevenly distributed along the circumferential direction of the impeller hub, that is, the blades are distributed on the impeller hub at unequal intervals, so as to disperse the noise peaks caused by the periodic action of the impeller wake and the diffuser, thereby reducing the noise of the centrifugal compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained according to these drawings without creative efforts.

[0019] Figure 1 It is a top view schematic diagram of the compressor impeller provided by the embodiment of the present invention.

[0020] In the figure, 1 is the impeller hub; 2 is the blade. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0021] To make the objectives, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be described in detail below. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. All other implementation manners obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope protected by the present invention.

[0022] See Figure 1 , the present invention provides a compressor impeller, including an impeller hub 1 and blades 2. The compressor impeller can be made of a metal material. Among them, the blades 2 are distributed at intervals along the circumferential direction of the impeller hub 1, and the blades 2 are unevenly distributed along the circumferential direction of the impeller hub 1, that is, the blades 2 are distributed on the impeller hub 1 at unequal intervals. The impeller is the main source of noise in a centrifugal compressor. The present invention provides an unequal-pitch impeller for a centrifugal compressor to disperse the noise peaks of the periodic action of the impeller wake and the diffuser, thereby reducing the noise of the centrifugal compressor. In addition, the unequal-pitch impeller structure mentioned in the present invention is applicable to rotating machinery with an impeller, such as a centrifugal compressor, a turbocharger, etc.; in addition, the unequal-pitch impeller structure mentioned in the present invention is applicable to a closed impeller and an open impeller.

[0023] As an optional implementation manner of an embodiment of the present invention, the number of the blades 2 is N. Along the circumferential direction of the impeller hub 1, the N blades 2 are divided into m groups, and the blades 2 in each group are respectively arranged along the circumferential direction of the impeller hub 1 according to a preset interval rule; the number of the blades 2 in each group can be the same and the blades 2 in each group are arranged along the circumferential direction of the impeller hub 1 at the same interval rule; m can be an even value.

[0024] As an optional implementation manner of an embodiment of the present invention, one end of the side where the blade 2 is connected to the impeller hub 1 and close to the air inlet of the compressor wheel is the reference end. The line passing through the reference end and the central axis of the impeller hub 1 and perpendicular to the central axis is the reference line. The included angle between two adjacent reference lines is the blade circumferential angle. Changing the evenly distributed blades along the impeller circumference to unequally distributed blades may cause changes in the internal flow of the impeller, thereby reducing the aerodynamic performance of the impeller. In order not to affect the aerodynamic performance of the impeller as much as possible, the absolute value of the difference between the circumferential angles of any two blades of the compressor impeller is not greater than a certain preset value. This preset value can be 5°, that is, the absolute value of the difference between the circumferential angles of any two blades of the compressor impeller is not greater than 5°. For example, |θ1 - θ| ≤ 5°.

[0025] As an optional implementation manner of the embodiment of the present invention, one end of the blade 2 connected to the impeller hub 1 and close to the air inlet of the compressor wheel is the reference end, and the line passing through the reference end and the central axis of the impeller hub 1 and perpendicular to the central axis is the reference line. Changing the blades evenly distributed along the circumference of the impeller to blades with unequal pitch may cause changes in the internal flow of the impeller, thereby reducing the aerodynamic performance of the impeller. To ensure the dynamic balance during the operation of the impeller, the number of blades 2 is an even number, and any reference line in the radial direction of the compressor impeller passes through the reference ends of two blades 2. See Figure 1 , which shows that θ = θ2, that is, θ and θ2 are diagonal to each other.

[0026] Regarding the installation of the impeller, the following instructions are provided: During assembly, the locking torque of the impeller should be ensured to prevent the impeller from loosening. At the same time, the torsional torque of the impeller should be strictly controlled. If the torsional torque is too small, the locking force is insufficient, and the impeller may rotate relative to the main shaft during the operation of the centrifugal compressor; if the torsional torque is too large, the main shaft may be damaged due to overload.

[0027] In addition, it should be noted that changing the blades evenly distributed along the circumference of the impeller to blades with unequal pitch may cause changes in the internal flow of the impeller, thereby reducing the aerodynamic performance of the impeller. Therefore, while changing the circumferential pitch of the blades, the blade profile can be improved accordingly. This is not only beneficial to maintaining a good flow state in the impeller passage, thus helping to maintain the original aerodynamic performance of the impeller, but also may be beneficial to exerting the noise reduction effect of the unequal pitch blades.

[0028] Embodiment 1:

[0029] A compressor impeller includes an impeller hub 1 and blades 2. Among them, the blades 2 are distributed at intervals along the circumferential direction of the impeller hub 1, and the blades 2 are unevenly distributed along the circumferential direction of the impeller hub 1. One end of the blade 2 connected to the impeller hub 1 and close to the air inlet of the compressor wheel is the reference end, and the line passing through the reference end and the central axis of the impeller hub 1 and perpendicular to the central axis is the reference line. The included angle between two adjacent reference lines is the circumferential angle of the blade. The absolute value of the difference between the circumferential angles of any two blades of the compressor impeller is not greater than 5°. The number of blades 2 is an even number, and any reference line in the radial direction of the compressor impeller passes through the reference ends of two blades 2.

[0030] Embodiment 2:

[0031] A centrifugal compressor includes the compressor impeller described in Embodiment 1.

[0032] Embodiment 3:

[0033] An air conditioner includes the compressor impeller described in Embodiment 1.

[0034] As described above, it is only the specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art within the technical scope disclosed by the present invention can easily think of changes or substitutions, which should all be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims described above.

Claims

1. A compressor impeller, characterized in that, It includes an impeller hub (1) and blades (2), wherein, the blades (2) are distributed at intervals along the circumferential direction of the impeller hub (1), and the blades (2) are non-uniformly distributed along the circumferential direction of the impeller hub (1); one end of the side where the blade (2) is connected to the impeller hub (1) and close to the air inlet of the compressor impeller is the reference end, the line passing through the reference end and the central axis of the impeller hub (1) and perpendicular to the central axis is the reference line, and the included angle between two adjacent reference lines is the blade circumferential angle, and the absolute value of the difference between any two blade circumferential angles of the compressor impeller is not greater than 5°; one end of the side where the blade (2) is connected to the impeller hub (1) and close to the air inlet of the compressor impeller is the reference end, the line passing through the reference end and the central axis of the impeller hub (1) and perpendicular to the central axis is the reference line, the number of the blades (2) is an even number, and any reference line in the radial direction of the compressor impeller passes through the reference ends of two blades (2).

2. The compressor impeller according to claim 1, characterized in that, The number of the blades (2) is N, and the N blades (2) are divided into m groups along the circumferential direction of the impeller hub (1), and the blades (2) in each group are respectively arranged along the circumferential direction of the impeller hub (1) according to a preset interval rule.

3. The compressor impeller according to claim 2, characterized in that, The blades (2) in each group are the same, and the blades (2) in each group are arranged along the circumferential direction of the impeller hub (1) at the same interval rule.

4. The compressor impeller according to claim 3, characterized in that, m is an even value.

5. The compressor impeller according to claim 1, characterized in that, The compressor impeller is made of a metal material.

6. A centrifugal compressor, characterized in that, It includes the compressor impeller according to any one of claims 1-5.

7. An air conditioner, characterized in that, It includes the compressor impeller according to any one of claims 1-5.

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