CN217926419U - Centrifugal impeller, centrifugal compressor, air conditioner outdoor unit and air conditioner - Google Patents
Centrifugal impeller, centrifugal compressor, air conditioner outdoor unit and air conditioner Download PDFInfo
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- CN217926419U CN217926419U CN202222246933.1U CN202222246933U CN217926419U CN 217926419 U CN217926419 U CN 217926419U CN 202222246933 U CN202222246933 U CN 202222246933U CN 217926419 U CN217926419 U CN 217926419U
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Abstract
The present disclosure provides a centrifugal impeller, a centrifugal compressor, an outdoor unit of an air conditioner and an air conditioner. The centrifugal impeller comprises a hub and a plurality of blades arranged on the hub, each blade comprises a pressure surface, a suction surface, a front edge and a tail edge, the front edge is located at the junction of the pressure surface and the suction surface of an inlet of the centrifugal impeller, the tail edge is located at the junction of the pressure surface and the suction surface of an outlet of the centrifugal impeller, the front edge is gradually inclined to the opposite direction of the airflow direction from the radial inner side to the radial outer side of the centrifugal impeller, and the included angle between the front edge and the axial direction of the centrifugal impeller is gradually increased. The centrifugal impeller, the centrifugal compressor, the air conditioner outdoor unit and the air conditioner are beneficial to reducing the pneumatic loss of the centrifugal impeller caused by the uneven axial speed of air flow at the inlet of the centrifugal impeller, so that the efficiency of the centrifugal impeller is improved.
Description
Technical Field
The disclosure relates to the technical field of pumping devices, in particular to a centrifugal impeller, a centrifugal compressor, an air conditioner outdoor unit and an air conditioner.
Background
A centrifugal impeller includes a hub and a plurality of blades mounted on the hub. The blade includes a pressure surface, a suction surface, a leading edge located at a juncture of the pressure surface and the suction surface of an inlet of the centrifugal impeller, and a trailing edge located at a juncture of the pressure surface and the suction surface of an outlet of the centrifugal impeller.
Fig. 1 is a schematic structural view of a blade of a centrifugal impeller of the related art. Referring to fig. 1, the leading edge 13 'of the vane 1' gradually inclines in the opposite direction of the air flow direction in from the radially inner side to the radially outer side of the centrifugal impeller and forms an angle λ with the axial direction of the centrifugal impeller.
In the design of the centrifugal impeller shown in fig. 1, the direction of the gas flow in entering the inlet of the centrifugal impeller is generally considered approximately parallel to the axial direction of the centrifugal impeller (i.e. the horizontal direction shown in fig. 1), and referring to fig. 2, the size of the inlet of the centrifugal impeller is generally designed according to the volume flow rate of the gas flow entering the inlet of the centrifugal impeller and the axial average velocity v of the inlet gas flow. Fig. 2 a shows a blade model in designing a blade of a centrifugal impeller. According to the distribution principle of the axial average velocity v of the air flow at the inlet of the centrifugal impeller shown in fig. 2, the flow passage area at the inlet of the centrifugal impeller close to the hub is small, and the flow passage area at the inlet of the centrifugal impeller close to the shroud is large. As shown in fig. 1, the area of the hub of the centrifugal impeller can be increased by forming the leading edge 13 'of the blade 1' at an included angle λ with respect to the axial direction of the centrifugal impeller, thereby preventing the centrifugal impeller from being clogged.
In addition, as shown in fig. 3, the trailing edge 14 'of the blade 1' of the related art centrifugal impeller forms a substantially right angle with the pressure surface 11 'and the suction surface 12'.
In implementing the technical solution of the present disclosure, the inventors found that:
although the shape of the front edge 13 'of the blade 1' of the centrifugal impeller can ensure that the centrifugal impeller basically meets the flow requirement, the impact loss and the separation loss generated by the inlet airflow of the centrifugal impeller are large, and the efficiency of the centrifugal impeller is adversely affected.
The shape of the trailing edge 14 'of the blade 1' of the above centrifugal impeller enables a large backward slip angle to be generated after the airflow flows out of the impeller, and the airflow slip increases the friction loss and separation loss of the airflow in the subsequent flow passage, and adversely affects the efficiency of the centrifugal impeller.
SUMMERY OF THE UTILITY MODEL
The purpose of this disclosure is to provide a centrifugal impeller, a centrifugal compressor, an outdoor unit of an air conditioner and an air conditioner, aiming to improve the efficiency of the centrifugal impeller.
The first aspect of the present disclosure provides a centrifugal impeller, including a hub and a plurality of blades mounted on the hub, the blades include a pressure surface, a suction surface, a leading edge located at a junction of the pressure surface and the suction surface at an inlet of the centrifugal impeller, and a trailing edge located at a junction of the pressure surface and the suction surface at an outlet of the centrifugal impeller, the leading edge gradually inclines to a direction opposite to an airflow direction from a radial inner side to a radial outer side of the centrifugal impeller, and an included angle between the leading edge and an axial direction of the centrifugal impeller gradually increases.
In some embodiments, the leading edge may have a progressively increasing or continuously increasing angle with the axial direction of the centrifugal impeller.
In some embodiments, the centrifugal impeller wherein the leading edge comprises a plurality of straight segments connected in series, a plurality of curved segments connected in series, a single curved segment, or a combination of at least one straight segment and at least one curved segment.
In some embodiments of the centrifugal impeller, the maximum radius m and the minimum radius n of the inlet of the centrifugal impeller are preferably determined according to the following formulas:
where Mv is a design value of a volume flow rate per unit time of the inlet airflow of the centrifugal impeller, ax2+ bx + c is an axial velocity of the inlet airflow of the centrifugal impeller at a radius x centered on an axis of the centrifugal impeller, and a, b, and c are constants determined according to simulation or experiment.
In some embodiments, the centrifugal impeller further comprises a second curved surface portion connected to the trailing edge, wherein a radius of curvature of the second curved surface portion is greater than a radius of curvature of the first curved surface portion.
In the centrifugal impeller of some embodiments, the first curved surface portion is a first circular arc surface, and the second curved surface portion is a second circular arc surface.
In some embodiments, the ratio of the radius of the first arcuate surface to the radius of the second arcuate surface is about 2:1.
A second aspect of the present disclosure provides a centrifugal compressor comprising the centrifugal impeller of the first aspect of the present disclosure.
A third aspect of the present disclosure provides an outdoor unit of an air conditioner including the centrifugal compressor of the second aspect of the present disclosure.
A fourth aspect of the present disclosure provides an air conditioner including the outdoor unit of the third aspect of the present disclosure.
Based on the centrifugal impeller that this disclosure provided, the leading edge of blade from the radial inboard to the radial outside of centrifugal impeller is gradually to the opposite direction slope of air current direction and with centrifugal impeller's axial contained angle grow gradually, do benefit to and reduce centrifugal impeller's pneumatic loss that the axial velocity of air current is inhomogeneous causes at centrifugal impeller entrance, for example the impact loss of air current to the pressure surface of blade and the separation loss in apex department to do benefit to and improve centrifugal impeller's efficiency.
The centrifugal compressor, the air conditioner outdoor unit and the air conditioner provided by the disclosure have the same advantages as the centrifugal impeller provided by the disclosure.
Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the disclosure and together with the description serve to explain the disclosure and not to limit the disclosure. In the drawings:
fig. 1 is a schematic structural view of a blade of a centrifugal impeller of the related art.
FIG. 2 is a schematic illustration of an inlet airflow velocity profile employed in determining the shape of the leading edge of a blade of a prior art centrifugal impeller.
Fig. 3 is a partial structural view of the trailing edge of a blade of a centrifugal impeller of the prior art.
Fig. 4 is a front view structural schematic diagram of a centrifugal impeller according to an embodiment of the present disclosure.
Fig. 5 is a side view schematically showing the centrifugal impeller shown in fig. 4.
Fig. 6 is a schematic structural view of a blade of the centrifugal impeller shown in fig. 4.
FIG. 7 is a schematic illustration of the velocity profile employed by the blades of the centrifugal impeller shown in FIG. 4 in determining the shape of the leading edge.
Fig. 8 is a partial structural view at the trailing edge of the blade of the centrifugal impeller shown in fig. 4.
Detailed Description
The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without making any creative effort, shall fall within the protection scope of the present disclosure.
The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as exemplary only and not as limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present disclosure.
In the description of the present disclosure, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are presented only for the convenience of describing and simplifying the disclosure, and in the absence of a contrary indication, these directional terms are not intended to indicate and imply that the device or element being referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore, should not be taken as limiting the scope of the disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.
In order to solve the technical problems of large impact loss and separation loss generated by air flow at an inlet in a centrifugal impeller in the related art, the embodiment of the application provides the centrifugal impeller. As shown in fig. 4 and 5, the centrifugal impeller comprises a hub 2 and a plurality of blades 1 mounted on the hub 2, wherein the blades 1 comprise a pressure surface 11, a suction surface 12, a leading edge 13 at the interface of the pressure surface 11 and the suction surface 12 at the inlet of the centrifugal impeller, and a trailing edge 14 at the interface of the pressure surface 11 and the suction surface 12 at the outlet of the centrifugal impeller. As shown in fig. 6, the leading edge 13 is inclined in the opposite direction to the airflow direction from the radially inner side to the radially outer side of the centrifugal impeller and has an angle with the axial direction of the centrifugal impeller which is gradually increased. The direction of the arrows in fig. 4 represents the direction of rotation of the centrifugal impeller when in operation. The angle of inclination a of the leading edge 13, which is closest to the hub 2, to the axial direction of the centrifugal impeller is shown in figure 6. In fig. 6 the air flow direction in is parallel to the axial direction of the centrifugal impeller.
Using a quadratic curve v x ＝ax 2 + bx + c fitting the axial velocity v of the gas flow at the inlet of the centrifugal impeller x The distribution in the radial direction of the centrifugal impeller is more realistic, where v x The axial velocity of the gas flow at the inlet of the centrifugal impeller at a radius x centered on the axis of the centrifugal impeller, a, b, c are constants determined according to simulation or experiment.
As shown in fig. 7, as the radius x increases, the axial velocity of the gas flow at the inlet of the centrifugal impeller increases, with increasing magnitude. Fig. 7B shows a blade model in designing a blade of a centrifugal impeller. As shown in fig. 6, in the centrifugal impeller according to the embodiment of the present disclosure, the leading edge 13 of the blade 1 gradually inclines in the opposite direction of the airflow direction in from the radially inner side to the radially outer side of the centrifugal impeller and an included angle (hereinafter, also referred to as a leading edge inclination angle) with the axial direction of the centrifugal impeller gradually increases, that is, a structure of the leading edge inclination angle of the gradual-change centrifugal impeller is adopted, which more conforms to a radial distribution rule of a quadratic curve of the axial speed of the airflow at the inlet of the centrifugal impeller, and as the radius increases, the flow passage area rapidly increases from the hub 2 to the shroud (not shown), and simultaneously, as the axial speed of the airflow gradually increases, the blocking effect caused by the blade 1 gradually decreases, and as the angle of the leading edge inclination angle gradually increases from the hub 2 to the shroud, the axial speed of the airflow is gradually reduced, so that the structure of the leading edge inclination angle of the gradual-change centrifugal impeller is beneficial to reducing the aerodynamic loss of the centrifugal impeller caused by the non-uniform axial speed of the airflow at the inlet of the centrifugal impeller, such as the impact loss of the airflow on the pressure surface 11 of the blade 1 and the separation loss at the tip, thereby being beneficial to improving the centrifugal impeller efficiency.
In some embodiments of the centrifugal impeller, the angle between the leading edge 13 and the axial direction of the centrifugal impeller may be gradually or continuously increased. For example, in some embodiments of the centrifugal impeller, the leading edge 13 may include a plurality of linear segments connected in series, a plurality of curved segments connected in series, a single curved segment, or a combination of at least one linear segment and at least one curved segment.
In the centrifugal impeller of some embodiments, the maximum radius m and the minimum radius n of the inlet of the centrifugal impeller are preferably determined according to the following formulas:
wherein Mv is a design value of a volume flow rate per unit time of an inlet airflow of the centrifugal impeller, ax 2 + bx + c is the axial velocity of the gas flow at the inlet of the centrifugal impeller at a radius x centered on the axis of the centrifugal impeller, a, b, c are constants determined according to simulation or experiment.
Based on a quadratic curve v x ＝ax 2 The maximum radius m and the minimum radius n of the inlet of the centrifugal impeller are reasonably arranged by + bx + c, so that the size of the inlet of the centrifugal impeller is better matched with the structure of the front edge inclination angle of the blades of the gradual change type centrifugal impeller, the structure of the front edge inclination angle of the blades of the gradual change type centrifugal impeller is facilitated to realize the function of the structure, and the efficiency of the centrifugal impeller is facilitated to be improved.
As shown in fig. 8, in some embodiments of the centrifugal impeller, an end of the pressure surface 11 close to the trailing edge 14 includes a first curved surface portion 111 connected to the trailing edge 14, an end of the suction surface 12 close to the trailing edge 14 includes a second curved surface portion 121 connected to the trailing edge 14, and a radius of curvature of the first curved surface portion 111 is larger than a radius of curvature of the second curved surface portion 121.
The arrangement of the tail edge 14 of the blade 1 of the centrifugal impeller considers the pressure gradient influence of the air flow on the pressure difference existing between the pressure surface 11 and the suction surface 12, the thickness of the blade 1 at the centrifugal outlet is gradually reduced, the energy loss generated by the air flow sliding at the centrifugal impeller outlet can be effectively reduced, and the efficiency of the centrifugal impeller is favorably improved.
In some embodiments, the first curved surface portion 111 is a first arc surface, and the second curved surface portion 121 is a second arc surface.
The blade 1 adopts the double-arc section tail edge at the outlet of the centrifugal impeller, which is beneficial to reducing the loss generated by airflow sliding, effectively reducing the outlet loss of the centrifugal impeller and improving the working efficiency of the centrifugal impeller.
The radian design of the trailing edge 14 of the blade 1 is carried out according to the pressure difference between the pressure surface 11 and the suction surface 12 and the thickness of the blade 1. For example, in some embodiments of the centrifugal impeller, the ratio of the radius of the first circular arc surface to the radius of the second circular arc surface is about 2:1.
The embodiment of the disclosure also provides a centrifugal compressor. The centrifugal compressor comprises the centrifugal impeller according to the embodiment of the disclosure.
The centrifugal compressor of the disclosed embodiment has the advantages of the centrifugal impeller of the disclosed embodiment.
The embodiment of the disclosure also provides an air conditioner outdoor unit comprising the centrifugal compressor of the embodiment of the disclosure. The embodiment of the disclosure also provides an air conditioner, which comprises the outdoor unit of the air conditioner of the embodiment of the disclosure. The air conditioner outdoor unit and the air conditioner have the advantages of the centrifugal impeller.
The centrifugal impeller, the centrifugal compressor, the air conditioner outdoor unit and the air conditioner of the embodiment of the disclosure can be used in various application places of the centrifugal impeller, the centrifugal compressor, the air conditioner outdoor unit and the air conditioner. In addition, the device is also suitable for places requiring higher pressure ratio and can still ensure higher efficiency. For example, the low GWP refrigerant medium has characteristics of low density, high compression difficulty, and the like, and the high working efficiency at a high pressure ratio can be achieved by compressing the low GWP refrigerant medium with the centrifugal impeller or the centrifugal compressor of the embodiments of the present disclosure.
As can be seen from the above description, in the centrifugal impeller, the centrifugal compressor, the outdoor unit of an air conditioner, and the air conditioner according to the embodiments of the present disclosure, effective measures for improving the efficiency of the centrifugal impeller are proposed. Aiming at the impact loss and the separation loss generated at the inlet of the centrifugal impeller, the inclination angle of the front edge of the blade 1 of the centrifugal impeller and the diameter sum of the inlet are optimally designed according to the rule that the axial speed of the airflow at the inlet of the centrifugal impeller is distributed along the radial direction of the centrifugal impeller according to a quadratic function, so that the efficiency of the centrifugal impeller is improved. Aiming at the air flow slippage loss caused by the thickness of the blade 1 at the tail edge 14 of the air flow at the outlet of the centrifugal impeller, the structure at the tail edge 14 of the blade 1 is optimally designed according to the pressure difference generated by the pressure surface 11 and the suction surface 12, so that the loss at the outlet of the centrifugal impeller can be effectively reduced, and the efficiency of the centrifugal impeller is improved.
Finally, it should be noted that: the above examples are intended only to illustrate the technical solutions of the present disclosure and not to limit them; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will understand that: modifications to the embodiments of the disclosure or equivalent replacements of parts of the technical features may be made, which are all covered by the technical solution claimed by the disclosure.
Claims (10)
1. A centrifugal impeller comprising a hub (2) and a plurality of blades (1) mounted on the hub (2), the blades (1) comprising a pressure surface (11), a suction surface (12), a leading edge (13) at the interface of the pressure surface (11) and the suction surface (12) at the inlet of the centrifugal impeller and a trailing edge (14) at the interface of the pressure surface (11) and the suction surface (12) at the outlet of the centrifugal impeller, characterized in that the leading edge (13) is inclined gradually from the radially inner side to the radially outer side of the centrifugal impeller in the opposite direction of the air flow direction (in) and gradually increases the included angle with the axial direction of the centrifugal impeller.
2. The centrifugal impeller according to claim 1, wherein the leading edge (13) has a progressively or continuously increasing angle to the axial direction of the centrifugal impeller.
3. The centrifugal impeller according to claim 1, wherein the leading edge (13) comprises a plurality of straight segments connected in series, a plurality of curved segments connected in series, a single curved segment, or a combination of at least one straight segment and at least one curved segment.
4. The centrifugal impeller according to any one of claims 1 to 3, wherein the maximum radius m and the minimum radius n of the inlet of the centrifugal impeller are preferably determined according to the following formulae:
wherein Mv is a design value of a volume flow rate per unit time of an inlet airflow of the centrifugal impeller, ax 2 + bx + c is the axial velocity of the gas flow at the inlet of the centrifugal impeller at a radius x centered on the axis of the centrifugal impeller, a, b, c are constants determined according to simulation or experiment.
5. The centrifugal impeller according to any of claims 1 to 3, wherein the end of the pressure surface (11) close to the trailing edge (14) comprises a first curved surface portion (111) bordering the trailing edge (14), the end of the suction surface (12) close to the trailing edge (14) comprises a second curved surface portion (121) bordering the trailing edge (14), the radius of curvature of the first curved surface portion (111) being larger than the radius of curvature of the second curved surface portion (121).
6. The centrifugal impeller according to claim 5, wherein the first curved surface portion (111) is a first circular arc surface and the second curved surface portion (121) is a second circular arc surface.
7. The centrifugal impeller of claim 6, wherein a ratio of the radius of the first circular arc surface to the radius of the second circular arc surface is about 2:1.
8. A centrifugal compressor comprising a centrifugal impeller according to any one of claims 1 to 7.
9. An outdoor unit of an air conditioner, comprising the centrifugal compressor of claim 8.
10. An air conditioner comprising the outdoor unit of claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222246933.1U CN217926419U (en) | 2022-08-25 | 2022-08-25 | Centrifugal impeller, centrifugal compressor, air conditioner outdoor unit and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202222246933.1U CN217926419U (en) | 2022-08-25 | 2022-08-25 | Centrifugal impeller, centrifugal compressor, air conditioner outdoor unit and air conditioner |
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| CN217926419U true CN217926419U (en) | 2022-11-29 |
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| CN202222246933.1U Active CN217926419U (en) | 2022-08-25 | 2022-08-25 | Centrifugal impeller, centrifugal compressor, air conditioner outdoor unit and air conditioner |
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