Air conditioner outdoor unit

Abstract

The application discloses an air conditioner outdoor unit, and relates to the technical field of air conditioners, and aims at solving the problem of the reduced work capacity of the secondary impeller caused by the double-stage centrifugal compressor in the prior art. The air conditioner outdoor unit comprises a multi-stage compressor, the multi-stage compressor comprises a primary volute, a primary impeller, a secondary compression assembly, a communication pipe and a despinning structure, the primary impeller is arranged in the primary volute; the communication pipe connects the primary volute and the secondary compression assembly; the despinning structure comprises a support shaft and a plurality of despinning blades; the plurality of despinning blades are arranged at intervals in the circumferential direction of the support shaft, the despinning blade has a connecting surface connected with a circumferential wall of the support shaft; the despinning blade has a cross section located away from the support shaft; the cross section comprises a reference line, a center line, a first edge line and a second edge line; the reference line is located on one side of the center line close to the first edge line and is parallel to the axis of the support shaft; in the flow direction of refrigerant, the distance between the center line and the reference line gradually decreases. The air conditioner outdoor unit is used for adjusting the temperature of gas.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of air conditioning technology, and in particular to an air conditioner outdoor unit. BACKGROUND

[0002] A double-stage centrifugal compressor is usually arranged in the outdoor unit of an air conditioner. The double-stage centrifugal compressor is usually connected with a primary impeller and a secondary impeller by a shaft, and the outlet of a primary volute and the inlet of a secondary volute are communicated by a bend pipe. The refrigerant entering the primary volute is compressed by the primary impeller, and then enters the secondary volute through the bend pipe to be compressed by the secondary impeller, so as to ensure the efficiency of air conditioning.

[0003] In the related art, in order to ensure the compactness of the structure, the primary volute is usually offset relative to the primary impeller when the double-stage centrifugal compressor is designed. That is, the center surface of the primary impeller perpendicular to the axis of the primary impeller does not coincide with the center surface of the primary volute perpendicular to the axis of the primary impeller in the axial direction of the primary impeller.

[0004] The design of the double-stage centrifugal compressor described above will cause the flow direction of the refrigerant to change when the refrigerant flows out of the primary impeller and enters the gas flow passage of the primary volute. As a result, when the refrigerant flows out of the primary volute and enters the bend pipe, a rotational flow phenomenon will be formed in the outlet pipe of the primary volute. This in turn causes the secondary impeller to generate resistance when the refrigerant enters the secondary volute, resulting in a decrease in the work capacity of the secondary impeller, and thus a decrease in the energy efficiency of the double-stage centrifugal compressor. SUMMARY

[0005] The embodiments of the present application provide an air conditioner outdoor unit, which solves the problem that the double-stage centrifugal compressor in the prior art causes the work capacity of the secondary impeller to decrease, thereby reducing the energy efficiency of the double-stage centrifugal compressor.

[0006] To achieve the above object, the embodiments of the present application adopt the following technical solutions:

[0007] According to a first aspect of the present application, an outdoor unit of an air conditioner is provided, comprising a multi-stage compressor, the multi-stage compressor comprising a first volute, a first impeller, a second compression assembly, a communication pipe and a deswirler structure, the first impeller being arranged in the first volute; the second compression assembly being arranged spaced apart from the first volute; the communication pipe connecting an outlet of the first volute and the second compression assembly; the deswirler structure comprising a support shaft and a plurality of deswirler blades, the support shaft being connected in the communication pipe, and an axial direction of the support shaft being consistent with an axial direction of the communication pipe; the plurality of deswirler blades being arranged spaced apart along a circumferential direction of the support shaft, the deswirler blade having a connecting surface connecting a peripheral wall of the support shaft; wherein the deswirler blade has a cross section on a side of the connecting surface away from the support shaft, the cross section being parallel to an axis of the support shaft and perpendicular to a length direction of the deswirler blade; the cross section comprising a reference line, a center line and a first edge line and a second edge line arranged along a thickness direction of the deswirler blade; a midpoint of a line segment formed by the intersection of a tangent line of any point on the first edge line and the first edge line and the second edge line being located on the center line; the reference line being located on a side of the center line close to the first edge line and being parallel to the axis of the support shaft; along a flow direction of the refrigerant, a distance between the center line and the reference line gradually decreases.

[0008] The outdoor unit of the air conditioner provided by the present application is provided, the refrigerant enters the first volute, and the refrigerant entering the first volute can be compressed once by the rotation of the first impeller. The outlet of the first volute is connected to the second compression assembly through the communication pipe, and the refrigerant compressed in sequence can flow through the communication pipe and then enter the second compression assembly, and the second compression assembly can compress the refrigerant twice.

[0009] The support shaft of the deswirler blade is connected in the communication pipe, and the plurality of deswirler blades are arranged spaced apart along the circumferential direction of the support shaft on the support shaft. And along the flow direction of the refrigerant, the distance between the center line of the cross section of the deswirler blade and the reference line gradually decreases, so that when the refrigerant flows to the deswirler blade, the refrigerant can quickly and easily contact one side of the deswirler blade in the thickness direction, so that the deswirler blade can quickly guide the flow of the refrigerant. After the refrigerant enters between adjacent deswirler blades, the rotation phenomenon of the refrigerant in the flow process can be reduced due to the restriction of the adjacent deswirler blades, so as to reduce the resistance generated by the rotation phenomenon of the refrigerant to the second compression assembly, and then improve the work capacity of the second compression assembly, so as to improve the energy efficiency of the multi-stage compressor.

[0010] In some embodiments, the center line has a first end point and a second end point arranged in sequence along the flow direction of the refrigerant, and an included angle between a tangent line of the center line at the first end point and the reference line is a first included angle; along a direction of the deswirler blade away from the support shaft, the deswirler blade has a plurality of cross sections arranged in sequence, and the first included angles of the plurality of cross sections gradually increase; in this way, after the refrigerant flows to the deswirler blade, the refrigerant can flow to the direction of the deswirler blade close to the inner peripheral wall of the communication pipe, so as to reduce the rotation phenomenon of the part of the refrigerant rotating along the circumferential direction of the communication pipe.

[0011] In some embodiments, when the cross section coincides with the side of the support shaft away from the racemic blade, the first included angle of the cross section is an edge included angle, and the edge included angle is greater than or equal to 20° and less than or equal to 50°; the edge included angle in the range can make the racemic blade have better streamline property in the direction of the racemic blade away from the support shaft, thereby improving the flow guiding effect of the racemic blade on the refrigerant.

[0012] In some embodiments, the edge included angle is greater than or equal to 20° and less than or equal to 30°; or, the edge included angle is greater than or equal to 30° and less than or equal to 40°; or, the edge included angle is greater than or equal to 40° and less than or equal to 50°; the edge included angle in each of the above ranges can make the racemic blade have better streamline property in the direction of the racemic blade away from the support shaft, thereby improving the flow guiding effect of the racemic blade on the refrigerant.

[0013] In some embodiments, the tangent of the center line at the second end point is parallel to the axis of the support shaft; in this way, when the refrigerant flows to one end of the racemic blade close to the second end point, the flow direction of the refrigerant is close to the axis direction of the communication pipe, thereby further enhancing the weakening effect of the racemic blade on the rotational flow phenomenon of the refrigerant.

[0014] In some embodiments, the thickness of the racemic blade gradually decreases in the direction of the refrigerant flow; in this way, the refrigerant can flow more smoothly when converging after flowing through the racemic blade, thereby making the refrigerant have better streamline property after flowing out of the racemic blade to improve the flow performance of the refrigerant.

[0015] In some embodiments, the difference between the maximum thickness of the racemic blade and the minimum thickness of the racemic blade is greater than or equal to 2 mm and less than or equal to 4 mm; when the difference between the maximum thickness of the racemic blade and the minimum thickness of the racemic blade is in the above range, the streamline property of the refrigerant after flowing through the racemic blade can be ensured, and the racemic blade can have smaller resistance to the refrigerant.

[0016] In some embodiments, the minimum thickness of the racemic blade is greater than or equal to 6 mm and less than or equal to 8 mm; the minimum thickness of the racemic blade in the above range can facilitate the processing of the racemic blade, and at the same time, the racemic blade can have smaller resistance to the refrigerant.

[0017] In some embodiments, the connecting surface has a first edge line and a second edge line arranged along the thickness direction of the blade, the first edge line and the second edge line are both straight lines parallel to the axis of the support shaft; and / or, the number of the deswirl blades is greater than or equal to 2 and less than or equal to 5; and / or, the communication pipe includes an outlet pipe and a guide pipe, the outlet pipe communicates the outlet of the primary volute and the inlet of the guide pipe, the outlet of the guide pipe communicates with the secondary compression assembly, and the deswirl structure is arranged in the outlet pipe; the first edge line and the second edge line are both straight lines parallel to the axis of the support shaft, which can make the flow linearity of the deswirl blade higher and improve the guide effect of the deswirl blade on the refrigerant; the number of the deswirl blades is within the above range, which can make the deswirl blade have a good guide effect on the refrigerant; and the deswirl structure is arranged in the outlet pipe, which can make the rotational flow phenomenon of the refrigerant weaken for a long time, thereby reducing the influence of the refrigerant on the secondary compression assembly.

[0018] According to a second aspect of the present application, an outdoor unit of an air conditioner is provided, which includes a multi-stage compressor, the multi-stage compressor including a primary volute, a primary impeller, a secondary compression assembly, a communication pipe, and a deswirl structure, the primary impeller being arranged in the primary volute and used for performing primary compression on refrigerant entering the primary volute; the secondary compression assembly being arranged at intervals from the primary volute and used for performing secondary compression on the refrigerant; the communication pipe communicating an outlet of the primary volute and the secondary compression assembly, so that the refrigerant in the primary volute flows through the communication pipe and then enters the secondary compression assembly; and the deswirl structure including a support shaft and a plurality of deswirl blades, the support shaft being connected to the communication pipe, an axial direction of the support shaft being consistent with an axial direction of the communication pipe; the plurality of deswirl blades being arranged at intervals along a circumferential direction of the support shaft, and each deswirl blade having a connecting surface connecting a peripheral wall of the support shaft; wherein the deswirl blade has a cross section on a side of the connecting surface away from the support shaft, the cross section being parallel to an axis of the support shaft and perpendicular to a length direction of the deswirl blade; the cross section including a reference line, a center line, and a first edge line and a second edge line arranged along a thickness direction of the blade; the connecting surface has a first edge line and a second edge line arranged along the thickness direction of the blade; a straight line perpendicular to a tangent line of any point on the first edge line intersects the first edge line and the second edge line to form a midpoint of a line segment on the center line; the reference line is on a side of the center line close to the first edge line and parallel to the axis of the support shaft; in a flow direction of the refrigerant, a spacing between the center line and the reference line gradually decreases; and the first edge line and the second edge line are both straight lines parallel to the axis of the support shaft.

[0019] It should be noted that the technical effects brought by the implementation manners of the second aspect can refer to the technical effects brought by the corresponding implementation manners of the first aspect, which will not be described here again. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 FIG. 1 is a structural schematic diagram of a multi-stage compressor in an embodiment of the present application;

[0021] Figure 2 Part structure schematic diagram of multistage compressor in the embodiment of the application;

[0022] Figure 3 Part structure schematic diagram of multistage compressor in the embodiment of the application;

[0023] Figure 4 Structure schematic diagram of racemization structure in the embodiment of the application;

[0024] Figure 5 Part structure schematic diagram of racemization structure in the embodiment of the application; Figure 2 Enlarged schematic diagram of structure at A in the embodiment of the application;

[0025] Figure 6 Part structure schematic diagram of racemization structure in the embodiment of the application;

[0026] Figure 7 Part structure schematic diagram of racemization structure in the embodiment of the application;

[0027] Figure 8 Part structure schematic diagram of racemization structure in the embodiment of the application;

[0028] Figure 9 Part structure schematic diagram of racemization structure in the embodiment of the application;

[0029] Figure 10 Structure schematic diagram of racemization blade in the embodiment of the application;

[0030] Figure 11 Structure schematic diagram of racemization blade in the embodiment of the application;

[0031] Figure 12 Flow field effect schematic diagram of racemization blade when edge included angle is 20° in the embodiment of the application;

[0032] Figure 13 Flow field effect schematic diagram of racemization blade when edge included angle is 30° in the embodiment of the application;

[0033] Figure 14 Flow field effect schematic diagram of racemization blade when edge included angle is 40° in the embodiment of the application;

[0034] Figure 15 Flow field effect schematic diagram of racemization blade when edge included angle is 50° in the embodiment of the application;

[0035] Figure 16 Part structure schematic diagram of racemization structure in the embodiment of the application;

[0036] Figure 17 Flow field effect schematic diagram when racemization structure is not installed in the multistage compressor in the embodiment of the application;

[0037] Figure 18 Figure 1 is a schematic diagram of a flow field effect after installing a desymmetrization structure in a multistage compressor in an embodiment of the present application.

[0038] Reference signs:

[0039] 1 - first stage volute; 11 - first inlet; 12 - first outlet;

[0040] 2 - first stage impeller;

[0041] 3 - communication pipe; 31 - outlet pipe; 32 - guide pipe; 33 - support;

[0042] 4 - second stage compression assembly; 41 - second stage volute;

[0043] 5 - desymmetrization structure; 51 - support shaft; 52 - desymmetrization blade; 521 - inflow part; 522 - outflow part; 523 - connecting surface; 5231 - first area; 5232 - second area; 5233 - first edge line; 5234 - second edge line; 5235 - third edge line; 5236 - fourth edge line; 524 - cross section; 5241 - first part; 5242 - second part; 5243 - reference line; 5244 - center line; 52441 - first end point; 52442 - second end point; 5245 - first side line; 5246 - second side line; 5247 - third side line; 5248 - fourth side line; 525 - first side surface; 526 - second side surface; 527 - third side surface; 528 - fourth side surface; 529 - first intersection line; 5291 - third end point; 5292 - fourth end point. DETAILED DESCRIPTION

[0044] The embodiments of the present application will be described in detail below with reference to the drawings.

[0045] In the description of the present application, it needs to be understood that the terms "center", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements indicated must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0046] The terms "first", "second" are only for the purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise stated, the meaning of "multiple" is two or more.

[0047] In the description of the present application, it is necessary to point out that unless explicitly defined and limited, the terms "mounting", "connecting", "connection" should be understood in a broad sense, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium, or the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances. In addition, when describing the pipeline or channel, the "connecting" and "connection" used in the present application have the meaning of conducting. The specific meaning should be understood in combination with the context.

[0048] In the embodiments of the present application, the words such as "exemplary" or "for example" are used to mean serving as an example, instance, or illustration. Any embodiment or design presented as "exemplary" or "for example" in the embodiments of the present application should not be interpreted as being more preferred or advantageous than other embodiments or design schemes. In fact, the use of the words such as "exemplary" or "for example" is intended to present the relevant concept in a specific manner.

[0049] Air conditioners, as a kind of common household appliances, are widely used in daily life. An air conditioner includes an air conditioner outdoor unit and an air conditioner indoor unit. The air conditioner outdoor unit and the air conditioner indoor unit cooperate to adjust the indoor air temperature.

[0050] Specifically, when the air conditioner is cooling, the compressor in the air conditioner outdoor unit compresses the gaseous refrigerant into high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant is cooled by the heat exchanger of the air conditioner outdoor unit to become liquid refrigerant at normal temperature and high pressure. The liquid refrigerant at normal temperature and high pressure then enters the air conditioner indoor unit. The liquid refrigerant at normal temperature and high pressure absorbs a large amount of heat through the heat exchanger of the air conditioner indoor unit, so that the air temperature in the air cavity of the air conditioner indoor unit is reduced. The fan of the air conditioner indoor unit then outputs the air at low temperature, thereby cooling the indoor air.

[0051] When the air conditioner is heating, the compressor in the air conditioner outdoor unit compresses the gaseous refrigerant into high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant enters the heat exchanger of the air conditioner indoor unit to condense and liquefy into liquid refrigerant at normal temperature and high pressure, and releases a large amount of heat. The air temperature in the air cavity of the air conditioner indoor unit is increased, and the fan of the air conditioner indoor unit then outputs the air at high temperature, thereby increasing the temperature of the indoor air. The liquid refrigerant at normal temperature and high pressure is reduced in pressure through the throttling device, and then enters the heat exchanger of the air conditioner outdoor unit. The liquid refrigerant at normal temperature and high pressure evaporates to become gaseous refrigerant at low temperature and low pressure, which enters the compressor in the air conditioner outdoor unit to start the next cycle.

[0052] The compressor in the outdoor unit of an air conditioner can be either a reciprocating compressor or a centrifugal compressor. Centrifugal compressors typically employ multi-stage compressors to enhance their efficiency.

[0053] However, due to the limited space inside the outdoor unit of the air conditioner, centrifugal compressors usually adopt a back-to-back structure. Taking a two-stage centrifugal compressor as an example, the first-stage volute and the second-stage volute are spaced apart along their axial direction, and then the first-stage volute and the second-stage volute are connected by a bend in the pipe.

[0054] In related technologies, to ensure the compactness of a two-stage centrifugal compressor, the first-stage volute is typically offset relative to the first-stage impeller during its design. This causes a change in the flow direction of the refrigerant as it flows from the first-stage impeller to the first-stage volute, resulting in a swirling flow of refrigerant at the outlet of the volute and the compressor itself. In other words, the refrigerant rotates circumferentially along the pipe while flowing within it.

[0055] The swirling of the refrigerant causes it to enter the secondary volute and create resistance to the secondary impeller, thus reducing the work capacity of the secondary impeller and consequently lowering the energy efficiency of the two-stage centrifugal compressor.

[0056] Based on this, this application provides an outdoor unit for an air conditioner, such as... Figure 1 As shown, the outdoor unit of the air conditioner includes a multi-stage compressor.

[0057] like Figure 1 As shown, the multi-stage compressor includes a first-stage volute 1 and a first-stage impeller 2. The first-stage volute 1 has a first inlet 11 and a first outlet 12, and the first-stage impeller 2 is disposed inside the first-stage volute 1.

[0058] The refrigerant entering the multi-stage compressor can enter the first-stage volute 1 through the first inlet 11, and then the refrigerant entering the first-stage volute 1 is compressed once by the rotation of the first-stage impeller 2.

[0059] The multi-stage compressor also includes a connecting pipe 3 and a secondary compression assembly 4. The secondary compression assembly 4 is spaced apart from the primary volute 1. Specifically, the secondary compression assembly 4 can be located on one side of the primary volute 1 along its axial direction, or on one side of the primary volute 1 along its axial direction perpendicular to its axial direction.

[0060] The connecting pipe 3 connects the outlet of the first-stage volute 1 to the second-stage compression assembly 4, that is, the connecting pipe 3 connects the first outlet 12 and the second-stage compression assembly 4. The refrigerant, after being compressed once by the first-stage impeller 2, enters the connecting pipe 3 through the first outlet 12 of the first-stage volute 1, and then enters the second-stage compression assembly 4, where the refrigerant is compressed a second time.

[0061] The number of the secondary compression assemblies 4 can be one or multiple. When the number of the secondary compression assemblies 4 is multiple, the multiple secondary compression assemblies 4 are connected in sequence through pipes. The refrigerant flowing out of the communication pipe 3 enters the multiple secondary compression assemblies 4 in sequence, and is compressed by the multiple secondary compression assemblies 4 in sequence, so that the refrigerant is compressed multiple times to improve the compression effect of the multi-stage compressor on the refrigerant.

[0062] The secondary compression assembly 4 can be a piston compression assembly or a centrifugal compression assembly. Here, the secondary compression assembly 4 is taken as a centrifugal compression assembly for illustration.

[0063] Specifically, the secondary compression assembly 4 includes a secondary volute 41 and a secondary impeller (not shown in the figure). The communication pipe 3 communicates the first outlet 12 of the primary volute 1 and the inlet of the secondary volute 41. The refrigerant compressed by the primary impeller 2 flows through the first outlet 12 and the communication pipe 3 in sequence, and then enters the secondary volute 41 from the inlet of the secondary volute 41, and is compressed by the rotation of the secondary impeller.

[0064] In order to reduce the influence of the rotational flow phenomenon of the refrigerant on the secondary impeller, as shown in Figure 2 , the multi-stage compressor further includes a despin structure 5. The despin structure 5 is arranged in the communication pipe 3 and is used to slow down the rotational flow phenomenon of the refrigerant.

[0065] As shown in Figure 1 , the communication pipe 3 includes an outlet pipe 31 and a flow guide pipe 32. The outlet pipe 31 is the outlet pipe 31 of the primary volute 1, is arranged at the outlet of the primary volute 1, and communicates the outlet of the primary volute 1 and the inlet of the flow guide pipe 32, and is used to make the refrigerant in the primary volute 1 flow into the flow guide pipe 32.

[0066] The outlet of the flow guide pipe 32 communicates with the secondary compression assembly 4. Specifically, the outlet of the flow guide pipe 32 communicates with the inlet of the secondary volute 41, and is used to transmit the refrigerant in the flow guide pipe 32 to the secondary volute 41.

[0067] The despin structure 5 can be arranged at multiple positions in the communication pipe 3. For example, as shown in Figure 2 , the despin structure 5 is arranged in the outlet pipe 31; for example, as shown in Figure 3 , the despin structure 5 is arranged in the flow guide pipe 32.

[0068] Preferably, the despin structure 5 is arranged in the outlet pipe 31. In this way, the rotational flow phenomenon of the refrigerant can be weakened at the outlet of the primary volute 1, and the refrigerant after the weakening of the rotational flow phenomenon has a longer time for buffering during the flow through the flow guide pipe 32, so that the influence of the refrigerant on the secondary impeller can be effectively slowed down.

[0069] As shown in Figure 4 , the racemic structure 5 includes a support shaft 51 and a plurality of racemic blades 52. The support shaft 51 is connected in the communication pipe 3, specifically, the support shaft 51 is connected with the inner circumferential wall of the communication pipe 3.

[0070] For example, as shown in Figure 5 , two support members 33 are arranged on the inner circumferential wall of the communication pipe 3, the two support members 33 are arranged along the axial direction of the communication pipe 3, the support shaft 51 is arranged between the two support members 33, and one end of the support shaft 51 is connected with one of the support members 33, and the other end of the support shaft 51 is connected with the other support member 33, so as to realize the connection of the support shaft 51 with the circumferential wall of the communication pipe 3.

[0071] Among them, the support member 33 can be a support plate, a support frame, etc. The connection of the support shaft 51 with the support member 33, and the connection of the support member 33 with the communication pipe 3 can be connected through bolts, screws, etc. fasteners, or can be connected through one casting.

[0072] Preferably, the support shaft 51 and the support member 33, and the support member 33 and the communication pipe 3 are manufactured by one casting, etc. This saves the subsequent assembly process, thereby reducing the cost.

[0073] As shown in Figure 4 , a plurality of racemic blades 52 are arranged on the support shaft 51 along the circumferential direction of the support shaft 51. Specifically, the racemic blades 52 are connected to the circumferential wall of the support shaft 51.

[0074] The racemic blade 52 includes an inflow portion 521 and an outflow portion 522 arranged in sequence along the flow direction of the refrigerant. At least part of the inflow portion 521 is curved in the thickness direction of the racemic blade 52, for guiding the racemic blade 52 to flow the refrigerant flowing thereon, so that the refrigerant can flow along the axial direction of the communication pipe 3 after flowing out of the racemic blade 52.

[0075] The specific bending direction of the inflow portion 521 of the racemic blade 52 can be opposite to the direction of the rotation of the refrigerant around the circumferential direction of the communication pipe 3. When the refrigerant flows in the communication pipe 3 to the racemic blade 52, it will flow out from the gap between adjacent racemic blades 52. In this process, the refrigerant can quickly impact on the side of the racemic blade 52 in the thickness direction in the circumferential direction of the communication pipe 3.

[0076] In this way, the racemic blade 52 can block the refrigerant in the circumferential direction of the communication pipe 3, and guide the refrigerant to flow out between two adjacent racemic blades 52, thereby reducing the rotational flow phenomenon of the refrigerant, so that the refrigerant can flow along the axial direction of the communication pipe 3 after flowing out of the racemic blade 52, thereby reducing the resistance generated by the rotational flow phenomenon of the refrigerant to the secondary impeller, thereby improving the work capacity of the secondary impeller, to increase the energy efficiency of the multi-stage compressor.

[0077] The axial direction of the support shaft 51 is consistent with the axial direction of the communication pipe 3, so that the resistance of the despiral vane 52 to the refrigerant entering the gap between adjacent despiral vanes 52 is smaller, which is more conducive to the flow of the refrigerant in the axial direction of the communication pipe 3.

[0078] On this basis, in order to make the refrigerant more smoothly enter between adjacent despiral vanes 52, so that the despiral vane 52 guides the flow of the refrigerant, as shown in Figure 6 The side of the despiral vane 52 connected with the peripheral wall of the support shaft 51 is a connecting surface 523, and the despiral vane 52 also has a cross section 524. The cross section 524 is located on the side of the connecting surface 523 away from the support shaft 51, that is, the cross section 524 is any cross section 524 on the side of the connecting surface 523 away from the support shaft 51.

[0079] The cross section 524 is a cross section parallel to the axis (such as the line M shown in Figure 6 ) of the support shaft 51 and perpendicular to the length direction (such as the direction X shown in Figure 6 ) of the despiral vane 52. The length direction in the despiral vane 52 is the direction in which the despiral vane 52 extends away from the support shaft 51.

[0080] The cross section 524 can be divided into a first part 5241 and a second part 5242 arranged in sequence along the flow direction of the refrigerant, wherein the first part 5241 is located in the inflow part 521, and the second part 5242 is located in the outflow part 522. The connecting surface 523 can be divided into a first region 5231 and a second region 5232 arranged in sequence along the flow direction of the refrigerant, wherein the first region 5231 is located in the inflow part 521, and the second region 5232 is located in the outflow part 522.

[0081] As shown in Figure 7 , the cross section 524 includes a reference line 5243, a center line 5244, and a first edge line 5245 and a second edge line 5246 arranged in sequence along the thickness direction of the despiral vane 52. The midpoint of the line segment formed by the intersection of the tangent line perpendicular to any point on the first edge line 5245 and the first edge line 5245 and the second edge line 5246 is located on the center line 5244; the reference line 5243 is located on the side of the center line 5244 close to the first edge line 5245, and is parallel to the axis (such as the line M shown in Figure 7 ) of the support shaft 51.

[0082] It should be noted that for any point of the first edge line 5245, the tangent of the first edge line 5245 at the point is the first tangent, the straight line perpendicular to the first tangent is the first perpendicular, the intersection of the first perpendicular and the first edge line 5245 is the first intersection, the intersection of the first perpendicular and the second edge line 5246 is the second intersection, and the line segment formed by connecting the first intersection and the second intersection is the first line segment.

[0083] Since the first edge line 5245 is composed of multiple points, multiple first line segments are formed between the first edge line 5245 and the second edge line 5246, and the line formed by the midpoints of the multiple first line segments is the midline 5244 of the cross section 524.

[0084] In the flow direction of the refrigerant, the distance between the midline 5244 and the reference line 5243 gradually decreases.

[0085] That is, the midline 5244 can be a curved line curved in the thickness direction of the despun blade 52, at this time, the despun blade 52 is curved, and the curved direction is the direction in which the first edge line 5245 points to the second edge line 5246. The midline 5244 can also be an inclined straight line, at this time, the despun blade 52 is a flat plate arranged obliquely.

[0086] Here, the midline 5244 is taken as an example of a curved line curved in the thickness direction of the despun blade 52. The midline 5244 has a first end point 52441 and a second end point 52442 arranged in sequence in the flow direction of the refrigerant. Since the distance between the midline 5244 and the reference line 5243 gradually decreases, the portion of the despun blade 52 close to the first end point 52441 is more curved than the portion of the despun blade 52 close to the second end point 52442.

[0087] It should be noted that, as shown in Figure 8 , the despun blade 52 has a first side surface 525 in the thickness direction thereof. As shown in Figure 9 , the despun blade 52 also has a second side surface 526 in the thickness direction thereof, and the first side surface 525 and the second side surface 526 are oppositely arranged. The first edge line 5245 is located on the first side surface 525, and the second edge line 5246 is located on the second side surface 526.

[0088] The despun blade 52 is arranged as described above. Since the portion of the first side surface 525 close to the first end point 52441 is more curved, the refrigerant can more smoothly contact the first side surface 525 (i.e., the side surface on which the first edge line 5245 is located) of the despun blade 52 in the flow process of the refrigerant, and the refrigerant can smoothly flow out between adjacent despun blades 52 under the guidance of the first side surface 525, thereby more effectively guiding the flow of the refrigerant.

[0089] In addition, as shown in Figure 8As shown, the racemic blade 52 also has a third side surface 527. As shown in FIG. 5, the first side surface 525, the third side surface 527, the second side surface 526 and the fourth side surface 528 are sequentially connected end to end. Figure 9 As shown, the racemic blade 52 also has a fourth side surface 528. The third side surface 527 and the fourth side surface 528 are sequentially arranged along the flow direction of the refrigerant, and the first side surface 525, the fourth side surface 528, the second side surface 526 and the third side surface 527 are sequentially connected end to end.

[0090] As shown in FIG. 5, the first side surface 525 and the third side surface 527 intersect to form a first intersection line 529. As shown in FIG. 5, the first intersection line 529 has a third end point 5291 and a fourth end point 5292 sequentially arranged along the direction of the racemic blade 52 away from the support shaft 51. Any point between the third end point 5291 and the fourth end point 5292 is located on the side of the third end point 5291 close to the second side surface 526, and the fourth end point 5292 is also located on the side of the third end point 5291 close to the second side surface 526. Figure 10 As shown, the cross section 524 also includes a third edge line 5247 and a fourth edge line 5248. The third edge line 5247 is located on the third side surface 527, and the fourth edge line 5248 is located on the fourth side surface 528. The first edge line 5245, the fourth edge line 5248, the second edge line 5246 and the third edge line are sequentially connected end to end.

[0091] The third edge line 5247 and the fourth edge line 5248 are both arc lines, used to connect the first edge line 5245 and the second edge line 5246, so that the first edge line 5245 smoothly transitions to the second edge line 5246. That is, the third side surface 527 and the fourth side surface 528 are also arc surfaces, used to make the first side surface 525 smoothly transition to the second side surface 526.

[0092] In this way, when the refrigerant flows in contact with the racemic blade 52, it first contacts the third side surface 527 and then flows onto the first side surface 525. The third side surface 527 is provided in an arc shape, which can reduce the resistance of the racemic blade 52 to the refrigerant, so that the refrigerant is smoothly in contact with the first side surface 525 and is guided by the first side surface 525.

[0093] In some embodiments, in order to improve the guiding effect of the racemic blade 52 on the refrigerant, to more effectively reduce the rotational flow phenomenon of the refrigerant, as shown in FIG. 5, the cross section 524 has a first end point 52441 and a second end point 52442 sequentially arranged along the direction of the racemic blade 52 away from the support shaft 51. The first end point 52441 and the second end point 52442 are located on the side of the first end point 52441 close to the second side surface 526, and the second end point 52442 is also located on the side of the first end point 52441 close to the second side surface 526. Figure 10 As shown, the angle between the tangent line of the center line 5244 at the first end point 52441 and the reference line 5243 is a first included angle a. Along the direction of the racemic blade 52 away from the support shaft 51, the racemic blade 52 has a plurality of cross sections 524 sequentially arranged, and the first included angle a of the plurality of cross sections 524 gradually increases.

[0094] That is, as shown in FIG. 5, the first side surface 525 and the third side surface 527 intersect to form a first intersection line 529. As shown in FIG. 5, the first intersection line 529 has a third end point 5291 and a fourth end point 5292 sequentially arranged along the direction of the racemic blade 52 away from the support shaft 51. Any point between the third end point 5291 and the fourth end point 5292 is located on the side of the third end point 5291 close to the second side surface 526, and the fourth end point 5292 is also located on the side of the third end point 5291 close to the second side surface 526. Figure 8

[0095] ​In other words, while the deswirl blade 52 bends along its thickness direction, the portion of the deswirl blade 52 near the third side surface 527 is also tilted.

[0096] In this way, after the refrigerant comes into contact with the first side 525 of the deswirl vane 52, as the refrigerant flows axially along the connecting pipe 3, it will also flow along the end of the deswirl vane 52 near the support shaft 51 towards the end of the deswirl vane 52 away from the support shaft 51. This allows some of the refrigerant to flow towards the inner circumferential wall of the connecting pipe 3, thereby impacting the portion of the refrigerant rotating circumferentially along the connecting pipe 3, reducing the swirling phenomenon of the refrigerant rotating circumferentially along the connecting pipe 3, and further reducing the swirling phenomenon of the refrigerant.

[0097] It should be noted that when the cross section 524 coincides with the side of the de-swirl blade 52 away from the support shaft 51, the first included angle α of the cross section 524 is the largest. The first included angle α of the cross section 524 can be named the edge included angle β, that is, the largest first included angle α is the edge included angle β.

[0098] The included edge angle β is greater than or equal to 20° and less than or equal to 50°.

[0099] When the included edge angle β is within the above range, the streamline of the deswirl vane 52 is better in the direction away from the support shaft 51. The deswirl vane 52 also has a better guiding effect on the refrigerant, which can make the refrigerant flow more smoothly between adjacent deswirl vanes 52 and can better reduce the swirling phenomenon of the refrigerant.

[0100] And, as Figure 11 As shown, the connecting surface 523 has a first edge line 5233 and a second edge line 5234 arranged along the thickness direction of the blade. The connecting surface 523 also has a third edge line 5235 and a fourth edge line 5236 arranged sequentially along the flow direction of the refrigerant, with the first edge line 5233, the fourth edge line 5236, the second edge line 5234 and the third edge line 5235 connected end to end in sequence.

[0101] The first edge line 5233 is located on the first side 525, the second edge line 5234 is located on the second side 526, the third edge line 5235 is located on the third side 527, and the fourth edge line 5236 is located on the fourth side 528.

[0102] At this point, both the first edge line 5233 and the second edge line 5234 can be straight lines parallel to the axis of the support shaft 51. That is, the angle between the tangent of the first edge line 5233 at the intersection of the first edge line 5233 and the straight line formed by the orthographic projection of the axis of the support shaft 51 onto the connecting surface 523 is 0°. In this way, the deswirl vane 52 has better streamline in the direction away from the support shaft 51, and the amount of refrigerant flowing to the first side surface 525 of the deswirl vane 52 near the support shaft 51 is less.

[0103] Furthermore, the aforementioned arrangement of the deswirl vane 52 facilitates the flow of refrigerant on the first side 525 of the deswirl vane 52 toward the end of the deswirl vane 52 away from the support shaft 51, thereby more effectively eliminating the swirling phenomenon of the refrigerant.

[0104] For example, the included edge angle β is greater than or equal to 20° and less than or equal to 30°. For instance, the included edge angle β can be 20°, 22°, 25°, 28°, 30°, etc.

[0105] like Figure 12 As shown, when the included edge angle β is 20°, the refrigerant flow has good linearity during the process of flowing through the deswirl vane 52, and the refrigerant can maintain a straight line overall after flowing out of the deswirl vane 52.

[0106] like Figure 13 As shown, when the included edge angle β is 30°, the refrigerant flow has a good linearity during the process of flowing through the deswirl vane 52, and the refrigerant can also maintain a straight line after flowing out of the deswirl vane 52.

[0107] Furthermore, compared to the case where the edge angle β is 20°, the streamline height of the refrigerant flow is improved when the edge angle β is 30°, and the straightness of the refrigerant after exiting the deswirl vane 52 is also improved. It is evident that within the range of edge angle β greater than or equal to 20° and less than or equal to 30°, the deswirl vane 52 can reduce the swirling phenomenon of the refrigerant.

[0108] For example, the included edge angle β is greater than or equal to 30° and less than or equal to 40°. For instance, the included edge angle β can be 30°, 32°, 35°, 38°, 40°, etc.

[0109] like Figure 14As shown, when the edge angle β is 40°, although the streamline of the refrigerant flow is slightly weaker compared to when the edge angle β is 30°, the overall flowability of the refrigerant is still better, and the overall straightness of the refrigerant after exiting the deswirl vane 52 is also better. It is evident that within the range of edge angle β greater than or equal to 30° and less than or equal to 40°, the deswirl vane 52 can also reduce the swirling phenomenon of the refrigerant.

[0110] For example, the included edge angle β is greater than or equal to 40° and less than or equal to 50°. For instance, the included edge angle β can be 40°, 42°, 45°, 48°, 50°, etc.

[0111] like Figure 15 As shown, when the edge angle β is 50°, the flow of refrigerant through the deswirl vane 52 is less streamlined compared to when the edge angle β is 40° and when the edge angle β is 30°. However, the overall flowability of the refrigerant and the overall straightness of the refrigerant after it exits the deswirl vane 52 can also reduce the swirling phenomenon of the refrigerant.

[0112] Therefore, within the range of an edge angle β greater than or equal to 20° and less than or equal to 50°, the deswirl blades 52 can reduce the swirling effect of the refrigerant. Specifically, the deswirl reduction effect is best when the edge angle β is around 30°.

[0113] Based on this, in order to improve the straightness of the refrigerant flow when it exits the deswirl blade 52, such as... Figure 10 As shown, the tangent of the midline 5244 at the second endpoint 52442 can be made (as shown). Figure 10 The line N shown is parallel to the axis of the support shaft 51.

[0114] In this way, as the refrigerant flows through the deswirl vane 52, due to the guiding effect of the deswirl vane 52, when the refrigerant flows to the end of the deswirl vane 52 near the second endpoint 52442, the flow direction of the refrigerant is close to the axial direction of the connecting pipe 3, thereby further enhancing the effect of the deswirl vane 52 on reducing the swirling phenomenon of the refrigerant.

[0115] In some embodiments, the number of deswirl blades 52 is greater than or equal to 2 and less than or equal to 5. When the number of deswirl blades 52 is within this range, the deswirl blades 52 can have a better guiding effect on the refrigerant.

[0116] If the number of deswirl vanes 52 is less than two, they will not effectively guide the refrigerant; if the number of deswirl vanes 52 is too large, it will increase the resistance to the flow of the refrigerant in the connecting pipe 3, thus affecting the flowability of the refrigerant.

[0117] In some embodiments, to make the refrigerant flow through the deswirl vane 52 smoother, such as Figure 16 As shown, the thickness of the deswirl blade 52 can be gradually reduced along the direction of refrigerant flow. That is, the thickness of the end of the deswirl blade 52 closest to the third side surface 527 (e.g.) Figure 16 The thickness H1 shown is greater than the thickness of the end of the deswirl blade 52 near the fourth side surface 528 (e.g., Figure 16 The thickness H2 is shown in the figure.

[0118] This allows the refrigerant to flow more smoothly when it converges at the end of the deswirl vane 52 near the fourth side 528 after passing through the deswirl vane 52, thus improving the flow performance of the refrigerant after it exits the deswirl vane 52.

[0119] Based on this, the difference between the maximum thickness and the minimum thickness of the deswirl blade 52 can be greater than or equal to 2 mm and less than or equal to 4 mm. That is, the thickness of the end of the deswirl blade 52 closest to the third side surface 527 (e.g., Figure 16 The thickness H1 shown in the figure is similar to the thickness of the deswirl blade 52 near the fourth side surface 528. Figure 16 The difference between the thickness H2 shown in the figure is greater than or equal to 2 mm and less than or equal to 4 mm.

[0120] For example, the difference between the maximum thickness and the minimum thickness of the racemic blade 52 can be 2 mm, 3 mm, 4 mm, etc.

[0121] When the difference between the maximum thickness and the minimum thickness of the deswirl blade 52 is within the above range, the streamline of the refrigerant after flowing through the deswirl blade 52 can be guaranteed, and the resistance of the deswirl blade 52 to the refrigerant can be reduced.

[0122] Furthermore, the minimum thickness of the anti-swirl blade 52 is greater than or equal to 6 mm and less than or equal to 8 mm. That is, the thickness of the end of the anti-swirl blade 52 closest to the fourth side surface 528 (e.g., Figure 16 The thickness H2 shown is greater than or equal to 6 mm and less than or equal to 8 mm.

[0123] For example, the minimum thickness of the racemic blade 52 can be 6mm, 7mm, 8mm, etc.

[0124] The minimum thickness of the deswirl blade 52 is within the above range, which facilitates the processing of the deswirl blade 52 and also reduces the resistance of the deswirl blade 52 to the refrigerant.

[0125] By setting the number and thickness of the desvane blade 52, the first included angle a of the desvane blade 52, and the tangent line of the middle line 5244 of the connecting surface 523 and the cross section 524 at the second end point 52442, the flow guiding effect of the desvane blade 52 on the refrigerant can be improved as a whole.

[0126] As shown in FIG. 1, when the desvane structure 5 is not arranged in the communicating pipe 3, the refrigerant has a clear rotational flow phenomenon when flowing to the outlet of the primary volute 1. Figure 17 As shown in FIG. 1, when the desvane structure 5 is not arranged in the communicating pipe 3, the refrigerant has a clear rotational flow phenomenon when flowing to the outlet of the primary volute 1.

[0127] Figure 18 As shown in FIG. 1, when the desvane structure 5 is not arranged in the communicating pipe 3, the refrigerant has a clear rotational flow phenomenon when flowing to the outlet of the primary volute 1.

[0128] As shown in FIG. 1, when the desvane structure 5 is not arranged in the communicating pipe 3, the refrigerant has a clear rotational flow phenomenon when flowing to the outlet of the primary volute 1.

[0129] Although the present application has been described in connection with the embodiments thereof with reference to the drawings, it will be apparent to those skilled in the art that various changes in form and details can be made therein without departing from the spirit and scope of the application. Therefore, the scope of the application should not be limited to the specific embodiments, but should be defined by the appended claims and their equivalents. In the claims, the word "comprising" does not exclude other elements or steps, and the singular does not exclude the plural and vice-versa, unless the context clearly requires these exclusions. The use of relative terms like "about", "approximately", "substantially" and the like acknowledges variations that can exist in the values that the terms describe and / or the inventiveness can tolerate. The application is not limited to the embodiments described herein but can vary freely within the scope of the claims and their equivalents.

[0130] Although the present application has been described in connection with the embodiments thereof with reference to the drawings, it will be apparent to those skilled in the art that various changes in form and details can be made therein without departing from the spirit and scope of the application. Therefore, the scope of the application should not be limited to the specific embodiments, but should be defined by the appended claims and their equivalents. In the claims, the word "comprising" does not exclude other elements or steps, and the singular does not exclude the plural and vice-versa, unless the context clearly requires these exclusions. The use of relative terms like "about", "approximately", "substantially" and the like acknowledges variations that can exist in the values that the terms describe and / or the inventiveness can tolerate. The application is not limited to the embodiments described herein but can vary freely within the scope of the claims and their equivalents.

[0131] ​The above merely illustrates the specific embodiments of the present application, but the protection scope of the present application is not limited thereto, any person skilled in the art can easily think of the changes or replacements within the technical range disclosed by the present application, which should be covered in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. An air conditioner outdoor unit comprising a multi-stage compressor, characterized by, The multi-stage compressor comprises: a first-stage volute; a first-stage impeller arranged in the first-stage volute; a second-stage compression assembly arranged in a spaced manner with the first-stage volute; a communication pipe communicating an outlet of the first-stage volute with the second-stage compression assembly; a racemization structure, the racemization structure comprising: a support shaft connected in the communication pipe, and an axial direction of the support shaft being consistent with an axial direction of the communication pipe; a plurality of racemization blades arranged in a spaced manner along a circumferential direction of the support shaft, the racemization blades having a connecting surface connecting a circumferential wall of the support shaft; wherein the racemization blade has a cross section on a side of the connecting surface away from the support shaft, the cross section being parallel to an axis of the support shaft and perpendicular to a length direction of the racemization blade; the cross section comprises a reference line, a center line, and a first edge line and a second edge line arranged along a thickness direction of the racemization blade; a straight line perpendicular to a tangent line of any point on the first edge line intersects with the first edge line and the second edge line to form a midpoint of a line segment on the center line; the reference line is located on a side of the center line close to the first edge line and is parallel to the axis of the support shaft; in a flow direction of the refrigerant, a spacing between the center line and the reference line gradually decreases; the center line has a first end point and a second end point arranged in sequence along the flow direction of the refrigerant, and an included angle between a tangent line of the center line at the first end point and the reference line is a first included angle; in a direction of the racemization blade away from the support shaft, the racemization blade has a plurality of cross sections arranged in sequence, and the first included angles of the plurality of cross sections gradually increase.

2. The air conditioner outdoor unit according to claim 1, characterized by when the cross section coincides with a side surface of the racemization blade away from the support shaft, the first included angle of the cross section is an edge included angle, and the edge included angle is greater than or equal to 20° and less than or equal to 50°.

3. The air conditioner outdoor unit according to claim 2, characterized by the edge included angle is greater than or equal to 20° and less than or equal to 30°; or, the edge included angle is greater than or equal to 30° and less than or equal to 40°; or, the edge included angle is greater than or equal to 40° and less than or equal to 50°.

4. The air conditioner outdoor unit according to any one of claims 1 to 3, characterized by, a tangent line of the center line at the second end point is parallel to the axis of the support shaft.

5. The air conditioner outdoor unit according to any one of claims 1-3, characterized by, in the flow direction of the refrigerant, a thickness of the racemization blade gradually decreases.

6. The air conditioner outdoor unit according to claim 5, characterized by a difference between a maximum thickness of the racemization blade and a minimum thickness of the racemization blade is greater than or equal to 2 mm and less than or equal to 4 mm.

7. The air conditioner outdoor unit according to claim 5, wherein the minimum thickness of the racemization blade is greater than or equal to 6 mm and less than or equal to 8 mm.

8. The air conditioner outdoor unit according to any one of claims 1-3, characterized by, a number of the racemization blades is greater than or equal to 2 and less than or equal to 5; and / or, the communication pipe comprises an outlet pipe and a flow guide pipe, the outlet pipe communicates an outlet of the first-stage volute with an inlet of the flow guide pipe, an outlet of the flow guide pipe communicates with the second-stage compression assembly, and the racemization structure is arranged in the outlet pipe.

9. An air conditioner outdoor unit comprising a multi-stage compressor, characterized by, The multi-stage compressor comprises: a first-stage volute; a first-stage impeller arranged in the first-stage volute, for performing primary compression on refrigerant entering the first-stage volute; a second-stage compression assembly arranged in a spaced manner with the first-stage volute, for performing secondary compression on the refrigerant; A communication pipe is arranged to communicate the outlet of the primary volute with the secondary compression assembly, so that the refrigerant in the primary volute flows through the communication pipe and enters the secondary compression assembly; The racemic structure comprises: A support shaft is connected to the communication pipe, and the axial direction of the support shaft is consistent with the axial direction of the communication pipe; A plurality of racemic blades are arranged along the circumferential direction of the support shaft, and the racemic blades have a connecting surface connecting the peripheral wall of the support shaft; The racemic blade has a cross section on the side away from the support shaft, which is parallel to the axis of the support shaft and perpendicular to the length direction of the racemic blade; The cross section comprises a reference line, a center line, and a first edge line and a second edge line arranged along the thickness direction of the racemic blade; the connecting surface has a first edge line and a second edge line arranged along the thickness direction of the blade; The midpoint of the line segment formed by the intersection of the first edge line and the second edge line is located on the center line; the reference line is located on the side of the center line close to the first edge line, and is parallel to the axis of the support shaft; In the flow direction of the refrigerant, the distance between the center line and the reference line gradually decreases; the first edge line and the second edge line are straight lines parallel to the axis of the support shaft; The center line has a first end point and a second end point arranged in sequence in the flow direction of the refrigerant, and the included angle between the tangent line of the center line at the first end point and the reference line is a first included angle; In the direction away from the support shaft, the racemic blade has a plurality of cross sections arranged in sequence, and the first included angle of the plurality of cross sections gradually increases.

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