Compressor and air compressor system

Abstract

The invention relates to a compressor and an air compressor system.The compressor comprises a machine shell assembly, and a containing cavity is defined in the machine shell assembly; the input pipe and the output pipe are fixedly arranged relative to the machine shell assembly; the rotor is rotatably arranged in the containing cavity, the rotor is provided with a cooling flow channel, the rotor has the axial direction and the radial direction, and the cooling flow channel penetrates through the rotor in the axial direction; according to the compressor, the rotor is provided with the axially-through cooling flow channel, on one hand, the cooling flow channel and the rotor are coaxially designed, the additional radial size is not increased, and on the other hand, the cooling flow channel and the rotor are coaxially designed; and on the other hand, the cooling medium is used for forcibly exchanging heat with the rotor, so that the heat dissipation efficiency of the rotor can be effectively improved, material deformation or permanent magnet demagnetization caused by high temperature of the rotor can be avoided, and the service life of the compressor is prolonged.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air compressor equipment, in particular to a compressor and an air compressor system. BACKGROUND

[0002] The magnetic suspension compressor or air compressor mainly comprises a motor stator, a rotor, a magnetic suspension bearing, an impeller, a volute, an expander and the like, and the compressor mainly works by the rotor rotating at high speed to drive the impeller to compress air. However, the rotor is prone to high temperature during high-speed rotation, and when the temperature reaches the required value of the rotor part material, the part is prone to deformation and the permanent magnet is demagnetized, which affects the normal work of the compressor. Due to the unique structure design of the rotor, there is not enough space for heat dissipation arrangement design, so the heat dissipation of the high-speed rotor has always been a difficult problem. SUMMARY

[0003] The present application aims to at least solve the problem of difficult heat dissipation of the rotor. The purpose is achieved in the following way:

[0004] The first aspect of the present application provides a compressor, comprising: a shell assembly, the inside of the shell assembly defining a cavity; an input pipe and an output pipe, fixedly arranged opposite to the shell assembly; a rotor, rotatably arranged in the cavity, the rotor being provided with a cooling flow channel, the rotor having an axial direction and a radial direction, the cooling flow channel penetrating through the rotor along the axial direction; along the axial direction, the input pipe and the output pipe are respectively arranged at both ends of the rotor and are rotatable relative to the rotor, and are respectively connected to both ends of the cooling flow channel, the input pipe being used for being connected to an external cooling system and inputting cooling medium into the cooling flow channel, and the cooling medium in the cooling flow channel being capable of being discharged through the output pipe.

[0005] According to the compressor of the present application, by arranging the axial penetrating cooling flow channel in the rotor, on the one hand, no additional heat dissipation device needs to be added in the inside of the shell assembly, the cooling flow channel is coaxially designed with the rotor, without increasing the additional radial dimension, adapting to the compact structure of the existing magnetic suspension compressor, so that the overall structure of the compressor can remain compact, on the other hand, the cooling medium is forced to exchange heat with the rotor, which can effectively improve the heat dissipation efficiency of the rotor, avoid the material deformation (such as impeller dynamic balance destruction) or permanent magnet demagnetization of the rotor caused by high temperature, and prolong the service life of the compressor.

[0006] In addition, the compressor according to the present application can also have the following additional technical features:

[0007] In some embodiments of the present application, the input pipe and the rotor are sealed by a first sealing structure, and / or the output pipe and the rotor are sealed by a first sealing structure. In some embodiments of the present application, the input pipe and the output pipe are respectively inserted into the interior of the cooling flow channel, and the first sealing structure is in the form of a ring, one of the first sealing structures is arranged on the circumferential outer surface of the input pipe and in the cooling flow channel, and the other of the first sealing structures is arranged on the circumferential outer surface of the output pipe and in the cooling flow channel.

[0008] In some embodiments of the present application, the first sealing structure is configured as a sealing ring.

[0009] In some embodiments of the present application, the number of the sealing rings is multiple, and the multiple sealing rings are arranged in sequence along the axial direction.

[0010] In some embodiments of the present application, the first sealing structure is configured as multiple first comb teeth, and the multiple first comb teeth are arranged in sequence along the axial direction and are arranged in sequence along the radial direction and away from the inner circumferential surface of the cooling flow channel.

[0011] In some embodiments of the present application, the compressor further comprises:

[0012] a first impeller, the first impeller being provided with a first through hole, the first through hole penetrating the first impeller along the axial direction;

[0013] a second impeller, the second impeller being provided with a second through hole, the second through hole penetrating the second impeller along the axial direction;

[0014] wherein one end of the rotor is arranged in the first through hole and fixedly connected with the first impeller, and the other end of the rotor is arranged in the second through hole and fixedly connected with the second impeller.

[0015] In some embodiments of the present application, along the axial direction, one end of the first impeller away from the second impeller is provided with a first sealing surface, the input pipe is provided with a first sealing portion, and the first sealing surface and the first sealing portion are arranged oppositely.

[0016] one end of the second impeller away from the first impeller is provided with a second sealing surface, the output pipe is provided with a second sealing portion, and the second sealing surface and the second sealing portion are arranged oppositely.

[0017] second sealing structures are respectively arranged between the first sealing surface and the first sealing portion and between the second sealing surface and the second sealing portion.

[0018] In some embodiments of the present application, a plurality of first sealing protrusions are annularly formed on the first sealing portion and coaxially arranged with the input pipe, and the plurality of first sealing protrusions are sequentially and spacedly arranged along the radial direction;

[0019] A plurality of second sealing protrusions are annularly formed on the first sealing surface and coaxially arranged with the first impeller, and the plurality of second sealing protrusions are sequentially and spacedly arranged along the radial direction;

[0020] Wherein, the plurality of first sealing protrusions and the plurality of second sealing protrusions are sequentially and alternately arranged along the radial direction, and a first sealing gap is defined between the first sealing portion and the first sealing surface.

[0021] In some embodiments of the present application, the second sealing structure further comprises a plurality of first sealing comb teeth;

[0022] The plurality of first sealing comb teeth are arranged on the end surface of the first sealing protrusion towards the first sealing surface and sequentially and spacedly arranged along the radial direction; and / or, the plurality of first sealing comb teeth are arranged on the end surface of the second sealing protrusion towards the first sealing portion and sequentially and spacedly arranged along the radial direction.

[0023] In some embodiments of the present application, the second sealing structure comprises:

[0024] A plurality of third sealing protrusions are annularly formed on the second sealing portion and coaxially arranged with the output pipe, and the plurality of third sealing protrusions are sequentially and spacedly arranged along the radial direction;

[0025] A plurality of fourth sealing protrusions are annularly formed on the second sealing surface and coaxially arranged with the second impeller, and the plurality of fourth sealing protrusions are sequentially and spacedly arranged along the radial direction;

[0026] Wherein, the plurality of third sealing protrusions and the plurality of fourth sealing protrusions are sequentially and alternately arranged along the radial direction, and a second sealing gap is defined between the second sealing portion and the second sealing surface.

[0027] In some embodiments of the present application, the second sealing structure further comprises a plurality of second sealing comb teeth;

[0028] The plurality of second sealing comb teeth are arranged on the end surface of the third sealing protrusion towards the second sealing surface and sequentially and spacedly arranged along the radial direction; and / or, the plurality of second sealing comb teeth are arranged on the end surface of the fourth sealing protrusion towards the second sealing portion and sequentially and spacedly arranged along the radial direction.

[0029] In some embodiments of the present application, the diameter of the first sealing portion gradually increases from the first sealing portion to the first sealing surface;

[0030] And / or, the diameter of the second sealing part gradually increases from the second sealing part to the second sealing surface.

[0031] In some embodiments of the present application, the compressor further comprises a connecting member, and the input pipe and the output pipe are fixedly connected to the casing assembly through the connecting member respectively.

[0032] In some embodiments of the present application, the casing assembly comprises a casing, a first volute and a second volute, the casing is connected to the first volute and the second volute at two ends along the axial direction respectively, the first volute has a first inlet, the second volute has a second inlet, one connecting member is located in the first inlet and connected to the first volute and the input pipe respectively, and another connecting member is located in the second inlet and connected to the second volute and the output pipe respectively.

[0033] The second aspect of the present application further provides an air compressor system, which comprises the compressor of the first aspect. BRIEF DESCRIPTION OF DRAWINGS

[0034] Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The accompanying drawings are included to provide a better understanding of the preferred embodiments, and are not to be considered limitations of the present application. Moreover, in the drawings, like reference numerals refer to similar components, and:

[0035] Wherein:

[0036] Figure 1 Fig. 1 is a schematic view of a part of the structure of a compressor according to an embodiment of the present application;

[0037] Figure 2 Fig. 2 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application; Figure 1 Fig. 3 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application;

[0038] Figure 3 Fig. 4 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application; Figure 1 Fig. 5 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application;

[0039] Figure 4 Fig. 6 is a schematic view of a part of the structure of a compressor according to another embodiment of the present application;

[0040] Figure 5 Fig. 7 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application; Figure 4 Fig. 8 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application;

[0041] Figure 6 Fig. 9 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application; Figure 4 Fig. 10 is a schematic view of a part of the structure of the compressor according to the embodiment of the present application;

[0042] Figure 7 Fig. 8 is a partial enlarged schematic view of a cross-sectional structure of a compressor according to another embodiment of the present application;

[0043] Figure 8 Fig. 9 is a partial enlarged schematic view of a cross-sectional structure of a compressor according to another embodiment of the present application; Figure 5 Fig. 10 is a partial enlarged schematic view of a cross-sectional structure of a compressor according to another embodiment of the present application;

[0044] Figure 9 Fig. 11 is a partial enlarged schematic view of a cross-sectional structure of a compressor according to another embodiment of the present application; Figure 6 Fig. 12 is a partial enlarged schematic view of a cross-sectional structure of a compressor according to another embodiment of the present application;

[0045] Figure 10 Fig. 13 is a schematic view of a structure of a connecting member according to an embodiment of the present application.

[0046] In the drawings, the following signs represent the following:

[0047] 100, compressor;

[0048] 120, casing assembly; 1209, cavity; 121, casing; 1221, first volute; 1222, first-stage intake port; 1231, second volute; 1232, second-stage intake port;

[0049] 213, rotor; 21301, cooling flow channel; 21302, inlet; 21303, outlet;

[0050] 391, first sealing structure; 3911, sealing ring; 3912, first comb tooth;

[0051] 392, second sealing structure; 3921, first sealing protrusion; 3922, second sealing protrusion; 3923, first sealing comb tooth; 3924, first sealing gap; 3925, third sealing protrusion; 3926, fourth sealing protrusion; 3927, second sealing comb tooth; 3928, second sealing gap; 3929, sealing cavity;

[0052] 210, first impeller; 2100, first through hole; 21102, first sealing surface; 2101, first segment; 2102, second segment; 2103, first positioning step surface;

[0053] 211, second impeller; 2110, second through hole; 21101, second sealing surface; 2111, third segment; 2112, fourth segment; 2113, second positioning step surface;

[0054] 393, connecting member; 3931, first mounting portion; 3932, second mounting portion; 3933, support portion;

[0055] 394, input pipe; 3941, first sealing portion;

[0056] 395, output pipe; 3951, second sealing portion. DETAILED DESCRIPTION

[0057] Exemplary embodiments of the present application will be described herein below with reference to the accompanying drawings. While exemplary embodiments of the present application are illustrated, it is to be understood that the application is not limited to the embodiments described herein, but can be practiced with variation of them without departing from the spirit of the present application. Rather, these embodiments are included to more fully describe the present application and to convey the scope of the application to those skilled in the art.

[0058] It is to be understood that the terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises", "comprising", "includes", "including" and "has" are to be construed to be inclusive (i.e., to mean "including, but not limited to"), unless otherwise indicated as being term of exclusivity by context. Methods recited herein can be carried out in any order that is practicable unless otherwise indicated herein or otherwise clearly contradicted by context.

[0059] Although the terms first, second, third, etc. can be used herein to describe various elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as "first", "second", and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

[0060] In this application, unless expressly specified and limited otherwise, the terms "mounting", "connecting", "connecting", "fixing" and the like should be understood broadly, for example, can be fixed connection, can also be detachable connection, or integral; can be mechanical connection, can also be electrical connection or communication with each other; can be directly connected, can also be indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise expressly limited. 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.

[0061] For the sake of description, spatially relative terms are used herein for describing an element's or feature's relationship to another element or feature as illustrated in the figures. Such relative terms include "internal," "external," "inwardly," "outwardly," "lower," "bottom," "top," "upper," and the like. These spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "below" or "beneath" other elements or features would then be oriented "above" or "over" the other elements or features. Thus, the example term "below" can encompass both an orientation of above and below. The devices can be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

[0062] The present application provides a compressor 100, as shown in Figure 1 , Figure 2 and Figure 3 The compressor 100 includes a casing assembly 120, an input pipe 394, an output pipe 395 and a rotor 213. The casing assembly 120 defines an internal cavity 1209 for accommodating the rotor 213 and other components such as a motor and an impeller in the compressor 100, and provides mounting space for the rotor 213 and other components, and provides space for the impeller to perform gas compression. The input pipe 394 and the output pipe 395 are flat tubular members made of materials with high strength, for example, the input pipe 394 and the output pipe 395 can be metal tubular members with high strength, corrosion resistance, good sealing and pressure resistance. The input pipe 394 and the output pipe 395 are fixedly arranged opposite to the casing assembly 120. In other embodiments, the input pipe 394 and the output pipe 395 can include a straight pipe section and an elbow pipe section, wherein the straight pipe section is located at one end facing the rotor and cooperates with the rotor.

[0063] The rotor 213 is rotatably arranged in the internal cavity 1209. The outer periphery of the rotor 213 can be provided with permanent magnets, which are part of the rotor 213 in the motor of the compressor 100, and cooperate with the motor stator in the motor to drive the rotor 213 to rotate relative to the casing assembly 120 in the internal cavity 1209. In this embodiment, the rotor 213 is configured as a hollow tubular member. The rotor 213 has an internal cooling flow channel 21301 formed therein. The rotor 213 has an axial direction and a radial direction. The cooling flow channel 21301 extends through the rotor 213 along the axial direction. The cooling flow channel 21301 has an inlet and an outlet formed at two ends along the axial direction. The input pipe 394 and the output pipe 395 are arranged at the two ends of the rotor 213 along the axial direction. The input pipe 394 is opposite and communicates with the inlet, and the output pipe 395 is opposite and communicates with the outlet.

[0064] The input pipe 394 and the output pipe 395 are respectively used for external cooling supply system, the external cooling supply system sends the low-temperature cooling liquid into the rotor 213 cooling flow channel 21301 through the input pipe 394, the cooling medium is fully contacted with the inner wall of the rotor 213 when flowing through the cooling flow channel 21301, absorbs the heat of the rotor 213, reduces the temperature of the rotor 213, and the cooling medium after absorbing heat flows out of the cooling flow channel 21301 through the output pipe 395, so that the effective heat dissipation of the rotor 213 is realized.

[0065] The cooling medium flowing out of the cooling flow channel 21301 from the output pipe 395 can be transported to the heat dissipation device of the cooling system and recycled after releasing heat. Liquid cooling medium or gas cooling medium can be introduced into the cooling flow channel 21301, which can be selected according to the heat dissipation requirement.

[0066] Compared with the traditional compressor 100, the rotor 213 is compact in structure, and there is not enough space to arrange the heat dissipation fin or fan, which causes the rotor 213 to be difficult to dissipate heat. The compressor 100 provided by the application sets the axial through cooling flow channel 21301 in the rotor 213, on the one hand, without adding devices for heat dissipation in the interior of the shell assembly, the cooling flow channel 21301 is coaxial with the rotor 213, without increasing the additional radial dimension, adapting to the compact structure of the existing magnetic suspension compressor 100, so that the overall structure of the compressor 100 can remain compact, on the other hand, the cooling medium is forced to exchange heat with the rotor 213, which can effectively improve the heat dissipation efficiency of the rotor 213, avoid material deformation (such as damage of impeller dynamic balance) or demagnetization of permanent magnet caused by high temperature of the rotor 213, and prolong the service life of the compressor 100.

[0067] In some embodiments, please refer to Figure 1 , Figure 2 and Figure 3 The compressor 100 further comprises a first sealing structure 391, and the first sealing structure 391 is arranged between the input pipe 394 and the rotor 213 and between the output pipe 395 and the rotor 213 respectively, the gap between the input pipe 394 and the cooling flow channel 21301 and the gap between the output pipe 395 and the cooling flow channel 21301 are sealed by the first sealing structure 391, and the leakage of the cooling medium in the cooling flow channel 21301 is reduced.

[0068] Since the rotor 213 is in a relative rotating relationship with the input pipe 394 and the output pipe 395, the sealing between the input pipe 394, the output pipe 395 and the cooling flow channel 21301 needs to be realized to prevent the leakage of the cooling medium in the cooling flow channel 21301. The first sealing structure 391 provided by the application can be provided in multiple structural forms based on different sealing modes, and different sealing modes will be described in detail below.

[0069] In some embodiments, the input pipe 394 is inserted into the interior of the liquid cooling flow channel from the inlet of the liquid cooling flow channel, and the output pipe 395 is inserted into the interior of the liquid cooling flow channel from the outlet of the liquid cooling flow channel. The input pipe 394 and the output pipe 395 are coaxially arranged with the rotor 213. The structure of the liquid cooling flow channel is cylindrical, and the liquid cooling flow channel is coaxial with the rotor 213. The first sealing structure 391 is annular, and is arranged outside the input pipe 394 or the output pipe 395 and between the inner circumferential surface of the liquid cooling flow channel and the outer circumferential surface of the input pipe 394 or the output pipe 395. Thus, the first sealing structure 391 seals the gap between the input pipe 394 and the inner circumferential surface of the liquid cooling flow channel, reducing the leakage of the cooling medium in the interior of the liquid cooling flow channel from the gap between the input pipe 394 and the inner circumferential surface of the liquid cooling flow channel, or the first sealing structure 391 seals the gap between the output pipe 395 and the inner circumferential surface of the liquid cooling flow channel, reducing the leakage of the cooling medium in the interior of the liquid cooling flow channel from the gap between the output pipe 395 and the inner circumferential surface of the liquid cooling flow channel.

[0070] In some exemplary embodiments, as shown in Figure 1 , Figure 2 and Figure 3 , the first sealing structure 391 is a sealing ring 3911. The input pipe 394 and the output pipe 395 are respectively sleeved with the sealing ring 3911. The input pipe 394 is fixedly connected with the sealing ring 3911 sleeved on the outer circumferential surface thereof, and the output pipe 395 is fixedly connected with the sealing ring 3911 sleeved on the outer circumferential surface thereof. When the rotor 213 rotates, the sealing ring 3911 is fixed relative to the input pipe 394 or the output pipe 395. The sealing ring 3911 is compressed between the outer wall of the output pipe 395 or the input pipe 394 and the inner wall of the cooling flow channel 21301, generating a radial pre-tightening force to prevent leakage of the cooling medium.

[0071] Further, the first sealing structure 391 can include multiple sealing rings 3911 arranged in sequence in the axial direction. When a single sealing ring 3911 fails due to wear or aging, the remaining sealing rings 3911 can still maintain basic sealing performance, forming a stepped protection and reducing the leakage rate. In addition, the axial stiffness distribution of the multiple sealing rings 3911 is more uniform, which can suppress the vibration of the rotor 213 at the critical speed.

[0072] In this embodiment, the sealing ring 3911 can be an O-shaped sealing ring 3911. The O-shaped ring generates an initial sealing force through radial compression. When the system pressure rises, the sealing ring 3911 is squeezed to the high-pressure side, further increasing the sealing specific pressure, which can further enhance the sealing effect. In addition, the circular cross-section of the O-shaped sealing ring 3911 makes the stress distribution uniform during compression, avoiding the risk of tearing caused by stress concentration at the corners of rectangular or square sealing rings 3911.

[0073] The sealing ring 3911 can also adopt other structures, such as a lip-shaped sealing ring 3911, the lip of which forms a line contact seal with the inner circumferential surface of the cooling flow channel 21301, which can effectively reduce the frictional resistance compared with the O-shaped sealing ring 3911, and when the lip-shaped sealing ring 3911 wears, the wear can be automatically compensated by the elasticity of the lip, which is more suitable for the rotor 213 of the magnetic suspension compressor 100 rotating at high speed. Among them, if the sealing ring 3911 adopts a lip-shaped sealing ring 3911, the main body structure of the lip-shaped sealing ring 3911 can be made of rubber material, so that the main body structure of the lip-shaped sealing ring 3911 has better elastic deformation capability, and polytetrafluoroethylene is used as the sealing lip on the main body structure, so that the sealing ring 3911 has low friction and high elasticity.

[0074] In some other exemplary embodiments, as shown in Figure 7 The first sealing structure 391 is configured as a plurality of first comb teeth 3912, which are sequentially and spacedly arranged in the axial direction, and a sealing cavity 3929 is formed between any two adjacent first comb teeth 3912. The first comb teeth 3912 are spacedly arranged along the radial direction with the inner circumferential surface of the cooling flow channel 21301, so that the first sealing structure 391 and the inner circumferential surface of the cooling flow channel 21301 form a labyrinth sealing gap with alternatingly changed flow channel cross-sectional size. When the cooling medium in the cooling flow channel 21301 enters the labyrinth gap, the flow rate increases sharply due to the sudden reduction of the flow channel cross-sectional area between the first comb teeth 3912 and the inner circumferential surface of the cooling flow channel 21301, and the pressure energy of the cooling medium is converted into kinetic energy. The fluid forms a strong vortex in the sealing cavity 3929 between the teeth, the kinetic energy is converted into heat energy through viscous friction, and the pressure is gradually reduced, thereby reducing the leakage of the cooling medium in the cooling flow channel 21301. In this embodiment, the labyrinth sealing gap is used to realize the non-contact sealing between the output pipe 395 and the inner circumferential surface of the liquid cooling flow channel. On the basis of realizing the sealing, there is no frictional contact between the rotor 213 and the input pipe 394 and the output pipe 395, which can reduce the wear of the rotor 213 or the output pipe 395 and the input pipe 394 due to friction, and is beneficial to improve the durability of each component.

[0075] In some embodiments, the distance between the first comb teeth 3912 and the inner circumferential surface of the cooling flow channel 21301 in the radial direction is 0.05mm-0.2mm, for example, the distance between the first comb teeth 3912 and the inner circumferential surface of the cooling flow channel 21301 in the radial direction can be set to 0.05mm, 0.08mm, 0.1mm, 0.12mm, 0.15mm, 0.16mm, 0.18mm, 0.19mm, 0.2mm, etc.

[0076] In this embodiment, please refer to Figure 1 , Figure 2 and Figure 3As shown, the compressor 100 further comprises a first impeller 210 and a second impeller 211.

[0077] The first impeller 210 is provided with a first through hole 2100 penetrating through two ends of the first impeller 210 in the axial direction, the first through hole 2100 comprises a first section 2101 and a second section 2102 extending in the axial direction, the first section 2101 communicates with the second section 2102, and the inner diameter of the first section 2101 is greater than that of the second section 2102, the second section 2102 is located at one end of the first section 2101 away from the rotor 213. A first positioning step surface 2103 is formed between the first section 2101 and the second section 2102, one end of the rotor 213 is inserted into the first section 2101 and fixedly connected with the first impeller 210, and the other end of the rotor 213 abuts against the first positioning step surface 2103 in the axial direction, so that the first positioning step surface 2103 is used to realize the positioning of the rotor 213 and the first impeller 210 in the axial direction. The inner diameter of the second section 2102 is equal to that of the liquid cooling flow channel, and the first sealing structure 391 is arranged radially opposite to the inner circumferential surface of the cooling flow channel 21301 and the inner circumferential surface of the second section 2102, so that the inner circumferential surface of the cooling flow channel 21301 and the inner circumferential surface of the second section 2102 together constitute the above-mentioned labyrinth seal gap.

[0078] The second impeller 211 is provided with a second through hole 2110 penetrating through two ends of the second impeller 211 in the axial direction, the second through hole 2110 comprises a third section 2111 and a fourth section 2112 extending in the axial direction, the third section 2111 communicates with the fourth section 2112, and the inner diameter of the third section 2111 is greater than that of the fourth section 2112, the fourth section 2112 is located at one end of the third section 2111 away from the rotor 213. A second positioning step surface 2113 is formed between the third section 2111 and the fourth section 2112, the other end of the rotor 213 is inserted into the third section 2111 and fixedly connected with the second impeller 211, and the other end of the rotor 213 abuts against the second positioning step surface 2113 in the axial direction, so that the second positioning step surface 2113 is used to realize the positioning of the rotor 213 and the second impeller 211 in the axial direction. The inner diameter of the fourth section 2112 is equal to that of the liquid cooling flow channel, and the first sealing structure 391 is arranged radially opposite to the inner circumferential surface of the cooling flow channel 21301 and the inner circumferential surface of the fourth section 2112, so that the inner circumferential surface of the cooling flow channel 21301 and the inner circumferential surface of the fourth section 2112 together constitute the above-mentioned labyrinth seal gap.

[0079] In some embodiments, please refer to Figure 4 , Figure 5 and Figure 6As shown, the housing assembly 120 includes a housing 121, a first volute 1221 and a second volute 1231. The two ends of the housing 121 along the axial direction are connected to the first volute 1221 and the second volute 1231 respectively. The first volute 1221 has a primary air inlet 1222 and the second volute 1231 has a secondary air inlet 1232.

[0080] like Figure 8 and Figure 9 As shown, the first impeller 210 is located inside the first volute 1221. The first impeller 210 has a first sealing surface 21102 at one end facing the first-stage air inlet 1222 along the axial direction. The first sealing surface 21102 extends in the radial direction. The input pipe 394 is provided with a first sealing part 3941. Along the axial direction, the first sealing surface 21102 is disposed opposite to the first sealing part 3941. A second sealing structure 392 is provided between the first sealing surface 21102 and the first sealing part 3941. The second sealing structure 392 can achieve sealing in the radial direction between the input pipe 394 and the first impeller 210. On the leakage path of the cooling medium in the liquid cooling channel, the first sealing structure 391 between the input pipe 394 and the inner circumferential surface of the liquid cooling channel forms a first seal in the circumferential direction. The second sealing structure 392 between the first sealing surface 21102 and the first sealing part 3941 achieves a second seal in the radial direction. By using the two sealing structures, the probability of leakage of the cooling medium inside the cooling channel 21301 is further reduced.

[0081] Furthermore, the second impeller 211 is located inside the second volute 1231, and the second impeller 211 is provided with a second sealing surface 21101 at one end facing the secondary air inlet 1232 along the axial direction, and the second sealing surface 21101 extends in the radial direction. The output pipe 395 is provided with a second sealing part 3951. Along the axial direction, the second sealing surface 21101 is disposed opposite to the second sealing part 3951. A second sealing structure 392 is also provided between the second sealing surface 21101 and the second sealing part 3951. The second sealing structure 392 can achieve sealing in the radial direction of the output pipe 395 and the second impeller 211. On the leakage path of the cooling medium in the liquid cooling channel, the first sealing structure 391 between the output pipe 395 and the inner circumferential surface of the liquid cooling channel forms a first seal in the circumferential direction. The second sealing structure 392 between the second sealing surface 21101 and the second sealing part 3951 achieves a second seal in the radial direction. By using the two sealing structures, the probability of leakage of the cooling medium inside the cooling channel 21301 is further reduced.

[0082] In some embodiments, such as Figure 8As shown, the second sealing structure 392 includes a plurality of first sealing protrusions 3921 and a plurality of second sealing protrusions 3922, both of which are annular stepped protrusion structures.

[0083] Specifically, the first sealing part 3941 is provided with the first sealing protrusions 3921 at one end thereof in the axial direction, and the first sealing protrusions 3921 are coaxially arranged with the input pipe 394, a plurality of first sealing protrusions 3921 are sequentially and spacedly arranged in the radial direction, and a plurality of concentric annular arrangements are formed. The first sealing surface 21102 is provided with the second sealing protrusions 3922, and the second sealing protrusions 3922 are coaxially arranged with the first impeller 210, a plurality of second sealing protrusions 3922 are sequentially and spacedly arranged in the radial direction, and a plurality of concentric annular arrangements are formed.

[0084] Among them, a plurality of first sealing protrusions 3921 and a plurality of second sealing protrusions 3922 are sequentially and alternately arranged in the radial direction, and a first sealing gap 3924 is defined between the first sealing part 3941 and the first sealing surface 21102. The first sealing gap 3924 is a labyrinth channel formed by the alternating protrusions, which further reduces the leakage of the cooling medium in the liquid cooling flow channel.

[0085] In some embodiments, as shown, Figure 8 As shown, the second sealing structure 392 further includes a plurality of first sealing comb teeth 3923, and the end faces of the first sealing protrusions 3921 and the second sealing protrusions 3922 towards the first sealing surface 21102 and the first sealing part 3941 are respectively provided with a plurality of first sealing comb teeth 3923, and the plurality of first sealing comb teeth 3923 are sequentially and spacedly arranged in the radial direction. The first sealing comb teeth 3923 are annular, and the first sealing comb teeth 3923, the first sealing protrusions 3921, the second sealing protrusions 3922, the first impeller 210 and the input pipe 394 are coaxially arranged, and the plurality of first sealing comb teeth 3923 are sequentially and spacedly arranged in the axial direction and arranged in a concentric annular manner. In the radial direction, a sealing cavity 3929 is formed between any two adjacent first sealing comb teeth 3923, and a labyrinth sealing gap with alternating sudden changes in flow area is formed between the first sealing surface 21102 and the first sealing part 3941. When the cooling medium in the cooling flow channel 21301 enters the labyrinth sealing gap, the flow velocity increases sharply due to the sudden reduction in flow area, the pressure energy of the cooling medium is converted into kinetic energy, and a strong vortex is formed in the sealing cavity 3929 between the first sealing comb teeth 3923. The kinetic energy is converted into heat energy through viscous friction, and the pressure is gradually reduced, thereby further reducing the leakage of the cooling medium in the cooling flow channel 21301.

[0086] In some embodiments, as shown, Figure 9As shown, the second sealing structure 392 further comprises a plurality of third sealing protrusions 3925 and a plurality of fourth sealing protrusions 3926, both of which are annular stepped protrusion structures.

[0087] Specifically, the second sealing part 3951 is provided with the third sealing protrusions 3925 at one end thereof in the axial direction, and the third sealing protrusions 3925 are coaxially arranged with the output pipe 395, and a plurality of third sealing protrusions 3925 are arranged in a plurality of concentric annular arrangements in sequence and at intervals in the radial direction. The second sealing surface 21101 is provided with the fourth sealing protrusions 3926, and the fourth sealing protrusions 3926 are coaxially arranged with the second impeller 211, and a plurality of fourth sealing protrusions 3926 are arranged in a plurality of concentric annular arrangements in sequence and at intervals in the radial direction.

[0088] Among them, a plurality of third sealing protrusions 3925 and a plurality of fourth sealing protrusions 3926 are arranged in sequence and at intervals in the radial direction, and a second sealing gap 3928 is defined between the second sealing part 3951 and the second sealing surface 21101. The second sealing gap 3928 is a labyrinth channel formed by alternating protrusions at right angles, which further reduces the leakage of the cooling medium in the liquid cooling flow channel.

[0089] In some embodiments, as shown in Figure 9 As shown, the second sealing structure 392 further comprises a plurality of second sealing comb teeth 3927, and the end faces of the third sealing protrusions 3925 and the fourth sealing protrusions 3926 towards the second sealing surface 21101 and the second sealing part 3951 are each provided with a plurality of second sealing comb teeth 3927, and a plurality of second sealing comb teeth 3927 are arranged in sequence and at intervals in the radial direction. The second sealing comb teeth 3927 are annular, and the second sealing comb teeth 3927, the third sealing protrusions 3925, the fourth sealing protrusions 3926, the second impeller 211 and the output pipe 395 are coaxially arranged, and a plurality of second sealing comb teeth 3927 are arranged in sequence and at intervals in the axial direction and arranged in concentric annular arrangements. In the radial direction, a sealing cavity 3929 is formed between any two adjacent second sealing comb teeth 3927, and a labyrinth sealing gap with alternating sudden changes in flow area is formed between the second sealing surface 21101 and the second sealing part 3951. When the cooling medium in the cooling flow channel 21301 enters the labyrinth sealing gap, the flow rate increases sharply due to the sudden reduction in flow area, and the pressure energy of the cooling medium is converted into kinetic energy. Strong vortex flow is formed in the sealing cavities 3929 between the second sealing comb teeth 3927, and the kinetic energy is converted into heat energy through viscous friction, and the pressure is gradually reduced, thereby further reducing the leakage of the cooling medium in the cooling flow channel 21301.

[0090] In some embodiments, please refer to Figure 4 , Figure 5 and Figure 6As shown, the diameter of the first sealing portion 3941 gradually increases from the first sealing surface 21102. The input pipe 394 is arranged inside the first-stage air inlet 1222 of the first volute 1221, and the diameter of the first sealing portion 3941 gradually increases, so that the outer peripheral contour of the first sealing portion 3941 has a gradually expanding horn structure in the air inlet direction, which can guide the airflow in the first-stage air inlet 1222 to flow from the center to the circumferential direction, so as to guide the airflow to flow to the blades of the first impeller 210, and prevent turbulence when the airflow flows through the first sealing portion 3941, so that the air inlet of the first-stage air inlet 1222 is smoother.

[0091] The diameter of the second sealing portion 3951 gradually increases from the second sealing surface 21101. The output pipe 395 is arranged inside the second-stage air inlet 1232 of the second volute 1231, and the diameter of the second sealing portion 3951 gradually increases, so that the outer peripheral contour of the second sealing portion 3951 has a gradually expanding horn structure in the air inlet direction, which can guide the airflow in the second-stage air inlet 1232 to flow from the center to the circumferential direction, so as to guide the airflow to flow to the blades of the second impeller 211, and prevent turbulence when the airflow flows through the second sealing portion 3951, so that the air inlet of the second-stage air inlet 1232 is smoother.

[0092] In some embodiments, as shown in Figure 5 and Figure 6 The compressor 100 further comprises a connecting piece 393, and the input pipe 394 and the output pipe 395 are fixedly connected to the housing assembly 120 through a connecting piece 393.

[0093] The first-stage air inlet 1222 is provided with a connecting piece 393, and the connecting piece 393 is fixedly connected to the first volute 1221 through a bolt. The connecting piece 393 is further connected to the input pipe 394, and the connection mode of the connecting piece 393 and the input pipe 394 includes but is not limited to welding, threaded connection, flange connection, clamp connection, and bolt connection. The connecting piece 393 can be arranged in a rod shape or a plate shape.

[0094] In some embodiments, when the connecting piece 393 is in a plate shape, the connecting piece 393 is arranged in parallel with the air inlet direction, and the thickness of the connecting piece 393 increases first and then decreases along the air inlet direction, so that the cross section of the connecting piece 393 has a wing-shaped structure. When the airflow flows through the plate-shaped connecting piece 393, the flow line design of the thickness increasing first and then decreasing can make the airflow flow smoothly along the surface of the connecting piece 393, reduce the boundary layer separation phenomenon, make the air inlet pass through the connecting piece 393 area with lower resistance, and avoid the decrease of air inlet efficiency caused by too large resistance.

[0095] In some embodiments, please refer to Figure 1 , Figure 2 , Figure 3 andFigure 10 As shown, the connecting piece 393 comprises a first mounting portion 3931, a second mounting portion 3932, and a plurality of support portions 3933, the first mounting portion 3931 is annularly arranged outside the second mounting portion 3932, the support portions 3933 extend along the radial direction, the two ends of the support portions 3933 are respectively connected with the outer ring surface of the second mounting portion 3932 and the inner ring surface of the first mounting portion 3931, the second mounting portion 3932 is annularly arranged outside the input pipe 394 and is fixedly connected with the input pipe 394, and the first mounting portion 3931 is fixedly connected with the first volute 1221 by bolts. In the embodiment, the outer ring surface of the first mounting portion 3931 abuts against the inner peripheral surface of the first-stage gas inlet 1222 of the first volute 1221, so that the first volute 1221 is used to limit the connecting piece 393, the second mounting portion 3932 is coaxial with the first mounting portion 3931, and the inner ring surface of the second mounting portion 3932 abuts against the outer peripheral surface of the input pipe 394, so as to realize the radial positioning of the input pipe 394 and improve the matching precision between the input pipe 394 and the first-stage first impeller 210 of the rotor 213. The support portions 3933 are plate-shaped structures, the support portions 3933 are arranged in parallel with the gas inlet direction, and along the gas inlet direction, the thickness of the support portions 3933 first increases and then decreases, so that the cross section of the support portions 3933 has a wing-shaped structure. When the gas flow passes through the plate-shaped support portions 3933, the flow line design that the thickness first increases and then decreases can make the gas flow smoothly along the surface of the connecting piece 393, reduce the boundary layer separation phenomenon, make the gas inlet pass through the connecting piece 393 area with lower resistance, and avoid the decrease of the gas inlet efficiency caused by excessive resistance. The plurality of support portions 3933 are used to jointly support the second mounting portion 3932 and the input pipe 394, so that the connecting piece 393 has high structural strength and ensures the stability of the input pipe 394.

[0096] Understandably, the connecting piece 393 is arranged in the second-stage gas inlet 1232 and is connected with the second volute 1231 and the output pipe 395, and the connecting piece 393 in the second-stage gas inlet 1232 has the same structure as the connecting piece 393 in the first-stage gas inlet 1222, which will not be described herein.

[0097] The compressor 100 provided by the application is a centrifugal air compressor, which can be a single-stage centrifugal air compressor, a multi-stage centrifugal air compressor, or a magnetic suspension centrifugal air compressor. The compressor 100 can also be a centrifugal compressor used in a refrigeration system.

[0098] The compressor 100 further comprises a radial magnetic suspension bearing, an axial magnetic suspension bearing and a motor, the radial magnetic suspension bearing, the axial magnetic suspension bearing and the motor are arranged in the cavity and annularly arranged outside the rotor, the motor is used for driving the rotor to rotate, the radial magnetic suspension bearing and the axial magnetic suspension bearing can drive the rotor to be in a suspended state in the cavity and limit the rotor in the radial direction and the axial direction respectively, so that the rotor rotates in the cavity in a stable suspended state, and the rotor drives the first impeller and the second impeller to rotate to realize gas compression.

[0099] It should be noted that the positions of the output pipe and the input pipe can be interchanged, the input pipe is arranged at one end of the second impeller, and the output pipe is arranged at one end of the first impeller.

[0100] According to the embodiment of the present application, an air compressor system is further provided, and the air compressor system comprises the compressor 100. In the embodiment, the compressor 100 is a magnetic suspension type air compressor, and the air compressor system further comprises a first intercooler, a second intercooler, a first-stage exhaust pipe, a second-stage intake pipe, a second-stage exhaust pipe, a third-stage intake pipe and a third-stage exhaust pipe. The compressor 100 has three-stage compression cavities, the two ends of the first-stage exhaust pipe are communicated with the exhaust end of the first-stage compression cavity and the intake end of the first intercooler respectively, the two ends of the second-stage intake pipe are communicated with the second-stage intake port 1232 and the exhaust end of the first intercooler respectively, the two ends of the second-stage exhaust pipe are communicated with the exhaust end of the second-stage compression cavity and the intake end of the second intercooler respectively, the two ends of the third-stage intake pipe are communicated with the exhaust end of the second intercooler and the suction end of the third-stage compression cavity respectively, and the third-stage exhaust pipe is communicated with the exhaust end of the third-stage compression cavity.

[0101] The above merely describes the preferred embodiments of the present application, but the protection scope of the present application is not limited to this, any changes or replacements within the technical scope disclosed by the present application can be easily thought by those skilled in the art, and should be covered within 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. A compressor, characterized in that, include; A housing assembly, the interior of which defines a cavity; The input and output tubes are fixedly disposed relative to the housing assembly; A rotor is rotatably disposed in the cavity, the rotor is provided with a cooling channel, the rotor has an axial direction and a radial direction, and the cooling channel extends through the rotor along the axial direction; Along the axial direction, the input pipe and the output pipe are respectively located at both ends of the rotor and can rotate relative to the rotor. They are respectively connected to both ends of the cooling channel. The input pipe is used to connect to an external cooling system and input cooling medium into the cooling channel. The cooling medium in the cooling channel can be discharged through the output pipe.

2. The compressor according to claim 1, characterized in that, The compressor further includes a first sealing structure, wherein the input pipe and the rotor are sealed together by the first sealing structure, and / or the output pipe and the rotor are sealed together by the first sealing structure.

3. The compressor according to claim 2, characterized in that, The input pipe and the output pipe are respectively inserted into the interior of the cooling channel. The first sealing structure is an annular structure. One first sealing structure is annularly disposed on the outer circumferential surface of the input pipe and disposed in the cooling channel, and the other first sealing structure is annularly disposed on the outer circumferential surface of the output pipe and disposed in the cooling channel.

4. The compressor according to claim 3, characterized in that, The first sealing structure is configured as a sealing ring.

5. The compressor according to claim 4, characterized in that, The number of sealing rings is multiple, and the multiple sealing rings are arranged sequentially along the axial direction.

6. The compressor according to claim 3, characterized in that, The first sealing structure is configured with a plurality of first comb teeth, which are arranged sequentially at intervals along the axial direction and at intervals from the inner circumferential surface of the cooling channel along the radial direction.

7. The compressor according to any one of claims 1 to 6, characterized in that, The compressor also includes: A first impeller, wherein the first impeller is provided with a first through hole, the first through hole extending through the first impeller along the axial direction; The second impeller has a second through hole, which extends through the second impeller along the axial direction. One end of the rotor passes through the first through hole and is fixedly connected to the first impeller, while the other end of the rotor passes through the second through hole and is fixedly connected to the second impeller.

8. The compressor according to claim 7, characterized in that, Along the axial direction, the first impeller has a first sealing surface at the end opposite to the second impeller, and the input pipe has a first sealing part, with the first sealing surface and the first sealing part being disposed opposite to each other; The second impeller has a second sealing surface at the end opposite to the first impeller, and the output pipe has a second sealing part, with the second sealing surface and the second sealing part being disposed opposite to each other; A second sealing structure is provided between the first sealing surface and the first sealing part, and between the second sealing surface and the second sealing part.

9. The compressor according to claim 8, characterized in that, The second sealing structure includes: Multiple first sealing protrusions are annular and formed in the first sealing portion, and are coaxially arranged with the input pipe. The multiple first sealing protrusions are arranged at intervals along the radial direction. Multiple second sealing protrusions are annular and formed on the first sealing surface, and are coaxially arranged with the first impeller. The multiple second sealing protrusions are arranged at intervals along the radial direction. The plurality of first sealing protrusions and the plurality of second sealing protrusions are alternately arranged along the radial direction, and a first sealing gap is defined between the first sealing portion and the first sealing surface.

10. The compressor according to claim 9, characterized in that, The second sealing structure also includes a plurality of first sealing comb teeth; The plurality of first sealing comb teeth are disposed on the end face of the first sealing protrusion facing the first sealing surface, and are arranged at intervals along the radial direction; and / or, the plurality of first sealing comb teeth are disposed on the end face of the second sealing protrusion facing the first sealing portion, and are arranged at intervals along the radial direction.

11. The compressor according to claim 8, characterized in that, The second sealing structure includes: Multiple third sealing protrusions are annular and formed in the second sealing portion, and are coaxially arranged with the output pipe. The multiple third sealing protrusions are arranged at intervals along the radial direction. Multiple fourth sealing protrusions are annular and formed on the second sealing surface, and are coaxially arranged with the second impeller. The multiple fourth sealing protrusions are arranged at intervals along the radial direction. The plurality of third sealing protrusions and the plurality of fourth sealing protrusions are arranged alternately along the radial direction, and define a second sealing gap between the second sealing portion and the second sealing surface.

12. The compressor according to claim 11, characterized in that, The second sealing structure also includes a plurality of second sealing comb teeth; The plurality of second sealing comb teeth are disposed on the end face of the third sealing protrusion facing the second sealing surface, and are arranged at intervals along the radial direction; and / or, the plurality of second sealing comb teeth are disposed on the end face of the fourth sealing protrusion facing the second sealing portion, and are arranged at intervals along the radial direction.

13. The compressor according to claim 8, characterized in that, The diameter of the first sealing portion gradually increases from the first sealing portion to the first sealing surface; And / or, in the direction from the second sealing portion to the second sealing surface, the diameter of the second sealing portion gradually increases.

14. The compressor according to claim 7, characterized in that, The compressor also includes a connector, and the input pipe and the output pipe are respectively fixedly connected to the housing assembly through one of the connectors.

15. The compressor according to claim 14, characterized in that, The housing assembly includes a housing, a first volute, and a second volute. The housing is connected to the first volute and the second volute at both ends along the axial direction, respectively. The first volute has a primary air inlet, and the second volute has a secondary air inlet. One of the connecting members is located in the primary air inlet and is connected to the first volute and the input pipe, respectively. The other connecting member is located in the secondary air inlet and is connected to the second volute and the output pipe, respectively.

16. An air compressor system, characterized in that, The air compressor system includes the compressor according to any one of claims 1 to 15.

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