WO2019075921A1

WO2019075921A1 - Compressor and air conditioner having same

Info

Publication number: WO2019075921A1
Application number: PCT/CN2017/119425
Authority: WO
Inventors: 刘华; 钟瑞兴; 张治平; 蒋楠; 陈玉辉; 刘增岳; 雷连冬
Original assignee: 格力电器（武汉）有限公司; 珠海格力电器股份有限公司
Priority date: 2017-10-16
Filing date: 2017-12-28
Publication date: 2019-04-25
Also published as: CN107664143A; CN107664143B

Abstract

A compressor and an air conditioner having same. The compressor comprises: a motor, comprising a motor housing (1) and a cooling channel provided in the motor housing (1); and a first compression part provided at a first end of the motor, the first compression part comprising a first housing (2) and a first diffuser (4) connected to the first housing (2), the first diffuser (4) being provided with an air return port (5), and the cooling channel being in communication with the first compression part by means of the air return port (5). The compressor can reduce external air return pipelines and reduce leakage points.

Description

Compressor and air conditioner having the same

The present application is based on the Chinese application No. 201710962857.5 , filed on October 16, 2017 , and the priority of which is hereby incorporated by reference.

Technical field

The present disclosure relates to the field of air conditioning equipment, and in particular to a compressor and an air conditioner having the same.

Background technique

In a refrigeration centrifugal compressor, the cooling of the motor is usually cooled by a refrigerant. It is common practice to pass a cooling refrigerant into the motor and return the return air of the motor directly to the evaporator or intermediate economizer of the refrigeration system. Figure 1 is a motor return pipe connection structure, the motor return pipe 2' is external, it is connected to the motor through the first connection point 1', the motor return pipe 2' passes through the second connection point 5' and the evaporator or the intermediate economizer connection. Among them, the motor return pipe 2' is fixed by the first fixing bracket 3' and the second fixing bracket 4'. The cooling method of the motor has an external connecting pipe for supplying the refrigerant, which results in a complicated overall structure and high cost, and the number of potential hidden points increases due to the increase of the connecting pipe, which affects the overall reliability.

In addition, oil-free and cost-effective are the development direction of refrigeration centrifugal compressors, such as: magnetic suspension centrifugal compressors, gas suspension centrifugal compressors and refrigerant-lubricated bearing centrifugal compressors, due to the removal of the huge oil system, the entire compressor interior Only the refrigerant medium can be used to achieve oil-free. However, in the prior art, the return air of these types of compressors is also connected to the evaporator and the flasher. This structure naturally also has the problems of complicated structure and high cost of the system described above.

Summary of the invention

The present disclosure is directed to providing a compressor capable of reducing a connecting line and an air conditioner having the same.

The present disclosure provides a compressor including: a motor including a motor housing and a cooling passage disposed in the motor housing;

a first compression portion is disposed at the first end of the motor, the first compression portion includes a first housing and a first diffuser coupled to the first housing, the first diffuser is provided with a return air port, and the cooling passage is passed The air return port is in communication with the first compression portion.

Further, the end of the air return port close to the motor is a first end, and the end of the air return port close to the first compression portion is a second end, and the connection between the first end and the second end of the air return port is a first connection, the first connection a first angle between the line and a vertical plane of the axis of rotation of the motor;

The distance between the first end of the air return port and the axis of rotation is less than the distance between the second end of the air return port and the axis of rotation.

Further, wherein the first angle ranges from 15° to 35°.

Further, wherein the first connection line has a second angle with a plane defined by the motor rotation axis and the first connection midpoint;

The projection length of the first end of the air return port from the rotation axis in the vertical plane of the rotation axis is smaller than the projection length of the distance between the second end of the air return port and the rotation axis in the vertical plane of the rotation axis.

Further, wherein the second angle ranges from 55° to 75°.

Further, wherein there are a plurality of air return ports, and are sequentially spaced apart on the first circumference, the center of the first circumference is located on the rotation axis of the motor.

Further, wherein the air return ports are evenly spaced on the first circumference, and a line connecting the centers of the two adjacent air return ports and the center of the first circumference forms a third angle, and the third angle ranges from 12°. Up to 30°.

Further, the motor further includes a stator disposed in the motor housing and fixedly connected to the motor housing, the cooling passage includes a first cooling section, and the first cooling section is disposed on the inner wall of the motor housing and corresponds to the stator The position of the first cooling section faces the stator.

Further, wherein the first cooling section is a spiral section extending helically in the axial direction of the stator.

Further, the compressor further includes a motor coolant inlet, the motor coolant inlet is in communication with the first cooling section, and is located on the motor housing corresponding to the position of the stator.

Further, wherein the motor further comprises:

The rotor, the rotor is located in the stator, the cooling passage further includes a second cooling section, and the second cooling section includes a gap between the rotor and the stator.

Further, wherein the motor further comprises a bearing assembly, the bearing assembly comprises a bearing, and the cooling passage further comprises a bearing cooling section disposed on the bearing for the passage of the cooling refrigerant.

Further, the compressor further includes a bearing coolant inlet, the bearing coolant inlet is in communication with the bearing cooling section, and is located on the motor housing corresponding to the position of the bearing.

Further, wherein the motor further comprises a stator, the stator is disposed in the motor housing, and is fixedly connected to the motor housing, the bearing assembly is two, and are respectively disposed on two sides of the stator, and the bearing coolant inlet corresponds to away from the first The bearing assembly of the compression section is set.

Further, the motor further includes a stator, a rotor and a bearing, the stator is disposed in the motor housing, and is fixedly connected to the motor housing, the cooling passage includes a first cooling section, and the first cooling section is located on an inner wall of the motor housing And the position is corresponding to the stator, the opening of the first cooling section faces the stator; the rotor is located in the stator, the cooling channel further comprises a second cooling section, the second cooling section comprises a gap between the rotor and the stator; and the cooling channel further comprises a bearing disposed at the bearing a cooling section of the bearing through which the cooling refrigerant passes;

a refrigerant is introduced into the motor, at least a part of the refrigerant passes through the first cooling section and the second cooling section, and then flows out from the air return port, and at least another part of the refrigerant sequentially passes through the third cooling section, the second cooling section, and the bearing on the bearing remote from the air return port. The third cooling section on the bearing near the air return port flows out from the air return port.

Further, wherein the compressor further comprises a second compression portion, the second compression portion is disposed at the second end of the motor, the first compression portion is for achieving one-stage compression, and the second compression portion is for achieving secondary compression.

Further, wherein the first compression portion further comprises a first impeller, the air return port is obliquely disposed, and the inclination angle enables the return air direction to follow the flow direction of the airflow in the first impeller.

According to another aspect of the present disclosure, an air conditioner including a compressor having a compressor as described above is provided.

According to the compressor of the present disclosure and the air conditioner having the same, by providing a return air port on the first diffuser, the return air of the motor after cooling is passed through the air return port into the first compression portion, so that the built-in exhaust of the motor can be realized. There is no need to install a return air pipe outside the motor, which saves the external space, avoids the problem of increasing the overall structural complexity and high cost caused by the external motor return pipe, and avoids the potential hidden danger points caused by the increase of the connecting pipe, affecting the whole Reliability issues.

DRAWINGS

The accompanying drawings, which are incorporated in the claims of the claims In the drawing:

1 is a schematic structural view of a prior art motor connected to a return air structure through an external motor return air pipe;

2 is a cross-sectional structural view of a compressor according to the present disclosure;

3 is a cross-sectional structural view of a first diffuser of a compressor according to the present disclosure;

4 is a side elevational view showing the first diffuser of the compressor according to the present disclosure;

Figure 5 is a front elevational view showing the first diffuser of the compressor according to the present disclosure;

6 is a schematic perspective view of a first diffuser of a compressor according to the present disclosure.

Description of the reference signs:

1', first connection point; 2', motor return air pipe; 3', first fixed bracket; 4', second fixed bracket; 5', second connection point;

1. Motor housing; 2. First housing; 3. First impeller; 4. First diffuser; 5. Return air inlet; 6. Stator; 10. Rotor; a diffuser; 13, a second impeller; 14, a second casing; 15, a bearing; 71, a first cooling section; 72, a second cooling section; 73, a bearing cooling section; 81, a motor coolant inlet; Bearing coolant inlet.

Detailed ways

The present disclosure will be described in detail below with reference to the drawings and embodiments.

As shown in FIGS. 2 and 6, according to an embodiment of the present disclosure, the compressor includes a motor and a first compression portion, and the motor includes a motor housing 1 and a cooling passage disposed in the motor housing 1. The first compression portion is disposed at the first end of the motor, and the first compression portion includes a first housing 2, a first diffuser 4 connected to the first housing 2, and the first diffuser 4 is provided with a return air inlet 5 The cooling passage communicates with the first compression portion through the air return port 5.

By providing the air return port 5 on the first diffuser 4, the return air for cooling the motor enters the first compression portion through the air return port 5, so that the built-in exhaust of the motor can be realized without installing a return air pipe outside the motor. The utility model saves the external space, avoids the problem of increasing the overall structural complexity and high cost caused by the external motor return air pipe, and avoids the problem that the potential hidden danger points are increased due to the increase of the connecting pipelines, which affects the overall reliability.

The first compression portion further includes a first impeller 3, and the first impeller 3 is disposed in the first casing 2, and compression of the gas is achieved by the rotation of the first impeller 3. For the motor cooled by the refrigerant, because the refrigerant has the characteristics of large unit mass cooling capacity, the motor winding temperature is generally 30 ° C during the cooling process. Considering the heat transfer temperature difference of 10 ° C, the motor cavity gas is generally only 20 ° C. For other parts of the compressor that are hotter than others, the low temperature of the gas in the motor cavity is a very good source of cold. The gas after cooling the motor is discharged into the first compression portion through the built-in air return port 5, so that the cold source can be reused, and the gas entering the first compression portion reduces the air outlet of the first impeller 3 in the first compression portion. The temperature of the gas effectively reduces the airflow noise; on the other hand, due to the decrease of the gas temperature, the power consumption in the subsequent gas compression is reduced, which is conducive to energy conservation.

Moreover, after the return air that has cooled the motor through the air return port 5 enters the first compression portion, the gas density in the compression chamber of the first compression portion increases, the number of gas molecules increases, and collision between gas molecules can be increased. In order to increase the friction between the gas molecules and the energy loss, thereby playing the role of collision noise reduction, which can reduce the noise generated when the compressor works.

The structure can be applied to any compressor that uses a refrigerant cooling motor or a compressor that uses a refrigerant to lubricate the bearing, and is particularly suitable for a two-stage double-headed impeller-free oil-free centrifugal compressor.

Optionally, in this embodiment, the compressor further includes a second compression portion, and the second compression portion is disposed at the second end of the motor. The second compression unit is connected to the first compression unit, and the exhaust gas compressed by the first compression unit can enter the second compression unit, and is compressed again in the second compression unit and then discharged.

As shown in FIG. 2, the motor further includes a stator 6, a rotating shaft and a rotor 10.

The stator 6 is disposed in the motor housing 1 and is fixed to the inner wall of the motor housing 1. The cooling passage includes a first cooling section 71 which is provided on the inner wall of the motor housing 1 at a position corresponding to the stator 6, and the opening of the first cooling section 71 faces the stator 6. The first cooling section 71 is for passing the refrigerant to enable the refrigerant to cool and cool the stator 6.

Alternatively, the first cooling section 71 is a spiral section that spirals in the axial direction of the stator 6. The spiral extension of the first cooling section 71 can effectively increase the length, area and time of contact between the refrigerant and the stator, thereby achieving sufficient cooling of the stator 6.

In this embodiment, the compressor further includes a motor coolant inlet 81, and the motor coolant inlet 81 is in communication with the first cooling section 71, and is located on the motor housing 1 corresponding to the position of the stator 6 to pass through the cooling passage. Into the refrigerant.

The rotating shaft is rotatably disposed in the motor housing 1 and is coupled to the motor housing 1 through a bearing assembly. The bearing assembly is used to support the rotating shaft so that the rotating shaft can be rotated.

The specific structure of the bearing assembly can be determined as needed, for example, the bearing assembly includes the mounting plate 11 and the bearing 15. Among them, the mounting plate 11 is used for mounting and supporting the bearing 15, and the mounting plate 11 is fixedly disposed in the motor housing 1.

The bearing 15 is mounted on the mounting plate 11, and the bearing 15 may be a deep groove ball bearing, a tapered roller bearing or the like depending on the force. The bearing 15 can be a refrigerant lubricated bearing, which can be a sliding bearing, a rolling bearing, a magnetic suspension bearing or a refrigerant lubricated bearing, which creates an oil-free environment for the entire compressor, and the gas of each component enters the mainstream gas. It does not cause pollution and heat transfer.

Alternatively, in the present embodiment, the bearing 15 is a refrigerant-lubricated bearing provided with a bearing cooling section 73 penetrating in the axial direction of the bearing 15, which is used for the passage of cooling and lubricating refrigerant. The cooling passage includes the bearing cooling section 73.

It should be noted that the bearing cooling sections 73 may be plural as needed, and are disposed at intervals in the circumferential direction of the bearing 15.

In the present embodiment, the bearing assembly is two and spaced apart, and the stator 6 is located between the two bearing assemblies. The shaft passes through two bearing assemblies.

The refrigerant-lubricated bearing of the two bearing assemblies has a bearing cooling section 73 in the middle, through which the refrigerant gas can take away the heat generated by the bearing working process, wherein the refrigerant-lubricated bearing away from the first compression part is the main bearing of the compressor. That is, the bearing bears both the radial force of the rotor shaft system and the axial force of the rotor shaft system, and the refrigerant lubrication bearing close to the first compression portion is the secondary bearing of the compressor, and only bears the radial force of the rotor shaft system. . Therefore, from the working principle, the main bearing generates more heat than the secondary bearing.

Optionally, the compressor further includes a bearing coolant inlet 82 that communicates with the bearing cooling section 73 and is located on the motor housing 1 corresponding to the bearing 15 for the cooling refrigerant of the bearing to enter.

Since the bearing assembly is two and disposed on both sides of the stator 6, and one of the bearings generates more heat than the other bearing, the bearing coolant inlet 82 is disposed corresponding to the bearing assembly away from the first compression portion, away from the first The bearing assembly of a compression portion is a main bearing, and the bearing coolant inlet 82 is provided corresponding to it to ensure a cooling effect.

The rotor 10 is disposed on the rotating shaft and rotates with the rotating shaft. The rotor 10 is located between two bearing assemblies. There is a gap between the outer diameter of the rotor 10 and the inner diameter of the stator 6, which is the second cooling section 72 of the cooling passage.

The first diffuser 4 of the first compression portion is connected to the motor housing 1, and the first housing 2 of the first compression portion is connected to the motor housing 1. The first impeller 3 is located at the first end of the motor and is disposed within the first housing 2. Specifically, the first impeller 3 is coupled to the rotating shaft and is rotatable with the rotating shaft. The first impeller 3 discharges the compressed gas into the volute of the first casing 2 through the air outlet.

As shown in FIG. 3, by providing the air return port 5 on the first diffuser 4, the cooling air return of the motor is communicated with the air outlet of the first impeller 3, and the return air gas directly enters the first compression portion, and the compressed gas is directly compressed. By cooling, the internal low-temperature gas cooling of the motor can be reused, the exhaust noise can be reduced, and the external motor return line connection can be omitted, so that the system is simple and low-cost, so that the entire centrifugal compressor can obtain higher cost performance.

The plurality of air return ports 5 on the first diffuser 4 may be disposed at intervals along the circumferential direction of the first diffuser 4, for example, a plurality of air return ports 5 are sequentially spaced apart on the first circumference, wherein the first circumference The center of the circle is located on the axis of rotation of the motor.

Preferably, as shown in FIG. 5, the air return ports 5 are evenly spaced on the first circumference, and the lines connecting the centers of the two adjacent air return ports 5 and the center of the first circumference form a third angle γ, the third The angle γ ranges from 12° to 30°. Thus, the air return ports 5 are evenly spaced to meet the motor exhaust demand while simultaneously making the first compression portion uniformly intake, and the number of the air return ports 5 can be determined according to the intake air amount.

The value of the third angle mainly considers the flow rate of the return air flow and the uniformity of the mixing and the processability of the processing. The smaller the angle, the more the number of circumferential return ports is, the easier it is to mix with the main air flow, but the larger the processing volume ,vice versa.

Alternatively, as shown in Figures 3, 4 and 6, the air return port 5 extends obliquely, i.e., the center line of the air return port 5 has an angle with the axis of the rotating shaft (i.e., the axis of rotation of the motor). In other words, the end of the air return port 5 near the motor is the first end, and the end of the air return port 5 near the first compression portion is the second end, and the connection between the first end and the second end of the air return port 5 is the first connection. The first line has a first angle α between the vertical plane of the motor axis of rotation (the vertical plane perpendicular to the axis of rotation in FIG. 4). Moreover, the distance between the first end of the air return port 5 and the axis of rotation is smaller than the distance between the second end of the air return port 5 and the axis of rotation. In this way, when the motor returns to the first compression portion, the airflow direction is closer to the air outlet direction of the first impeller 3, thereby reducing the influence of the motor return air on the air output of the first impeller 3, and reducing the airflow fluctuation.

The first angle α ranges from 15° to 35°. The value of the first angle α mainly considers the airflow mixing performance and the return hole processing processability. If the angle is too small, the smaller the interference of the return air to the main airflow, the better the performance, but the processing technique is poor, and vice versa.

Optionally, in the embodiment, the first connection line of each air return port 5 has a second angle β between the motor rotation axis and the plane determined by the midpoint of the first connection line. Moreover, the projection length of the first end of the air return port 5 from the rotation axis in the vertical plane of the rotation axis is smaller than the projection length of the distance between the second end of the air return port 5 and the rotation axis in the vertical plane of the rotation axis. This makes the plurality of air return ports 5 constitute a spiral air intake structure, and can be more adapted to the gas compression direction of the volute.

The second angle β ranges from 55° to 75°. The value of the second angle β is mainly selected by considering the flow angle of the main air flow, and the angle range can make the flow angle of the return air flow substantially coincide with the flow angle of the main air flow.

It should be noted that the air inlet 5 and the air outlet of the first impeller 3 may be in direct communication or indirect communication. For example, the air outlet 5 directly communicates with the volute of the first compression portion. Moreover, the respective angles formed by the air return port 5 and other reference lines or reference surfaces are set in the spiral direction of the air flow formed by the air return port 5 (clockwise or counterclockwise direction of the motor rotation) and the direction of rotation of the motor. The same settings are made.

In an embodiment of the invention, the compressor is a centrifugal compressor, the first compression portion further includes a first impeller 3, the return air port 5 is inclined, and the inclination angle enables the return air direction to follow the air flow in the first impeller 3. The flow direction is such that the flow of air flowing out from the second end of the air return port 5 is consistent with the direction of the air flow at the corresponding position in the first impeller 3, thereby reducing the interference and impact of the cooling return air on the impeller.

As shown in FIG. 2, the first compression portion and the second compression portion are included, the first compression portion is used to implement the first-stage compression, and the second compression portion is used to implement the second-stage compression. The second compression portion includes a second housing 14, a second impeller 13 disposed in the second housing 14, and a second diffuser 12 coupled to the second housing 14. The second diffuser 12 is coupled to the second end of the motor housing 1. The second housing 14 is coupled to the second diffuser 12. The second impeller 13 is disposed in the second housing 14 and is coupled to the second end of the rotating shaft and rotates with the rotating shaft. The gas discharged from the first compression portion enters the second compression portion to be compressed again to meet the compression demand.

The motor returning structure of the two-stage double-headed impeller-free oil-free centrifugal compressor fully utilizes the advantages of the refrigerant-lubricated bearing, and in combination with the motor cooling temperature control state, the air-return port 5 is built in the diffuser of the previous stage ( In the present embodiment, on the first diffuser 4), the main bearing (the bearing away from the first diffuser 4) is mixed with the cooling gas of the motor and passed through the secondary bearing (the bearing close to the first diffuser 4). It is fully mixed with the main airflow of the first-stage compression section to increase the density of the mainstream gas in the front stage, reduce the temperature, and effectively reduce the effect of airflow noise. At the same time, due to the temperature drop of the airflow, the compression power consumption of the next stage will be reduced, thereby improving the compressor. efficiency. At the same time, the external connection circuit of the motor is omitted, the leakage point of the system is reduced, and the purpose of improving the cost performance of the compressor is achieved.

as shown in picture 2. When the compressor is in operation, the gas compressed by the first compression portion of the previous stage is discharged through the volute and then led to the suction port of the second compression portion of the next stage. Therefore, if the temperature of the gas in the first stage can be lowered, the microscopic molecular motion in the gas will be weakened, and after entering the next stage, the compression power consumption of the next stage will be reduced.

The motor return air structure as described above combines the control of the motor cooling, that is, the temperature of the gas after the motor is cooled is lower than the temperature of the compressed gas of the previous stage, so that when the return gas of the motor is mixed with the mainstream gas discharged from the impeller of the previous stage, There is a cooling trend to achieve noise reduction.

According to the measures and effects of the common motor cooling in the prior art, the return air temperature of the motor is generally only 20 ° C. This temperature is very advantageous for the efficient operation of the motor. Therefore, according to the prior art motor return air temperature level, the motor of the present embodiment is implemented. The structure is completely feasible.

The compressor of the air conditioner is in the diffuser of the first stage compression section (ie, the first diffuser 4 in this embodiment), near the outlet side of the first impeller hub (ie, the outlet of the first impeller 3), and the circumference A plurality of inclined channels (ie, the air return port 5) are provided, so that the motor is reinstated and built in, which reduces the external return air line and reduces the hidden danger point. The size of these channels is determined by the amount of return air and the flow rate of the motor.

As shown in Figure 2, the cooling and returning process of the compressor is as follows:

The cooling passage of the motor includes a plurality of portions such as a first cooling section 71, a second cooling section 72, a bearing cooling section 73, and a connecting portion therebetween. Wherein, there is a spiral cooling channel between the stator and the motor housing 1, and the spiral cooling channel is the first cooling section 71. The air gap passage between the stator and the rotor is the second cooling section 72. The cooling and lubricating passage provided on the refrigerant-lubricated bearing is the bearing cooling section 73. A motor coolant inlet 81 and a bearing coolant inlet 82 are provided in the motor housing 1 for introducing refrigerant into the cooling passage. Wherein, the motor coolant inlet 81 is located at one side of the stator, and the bearing coolant inlet 82 is located at a position corresponding to the main bearing of the motor housing.

As shown in FIG. 2, during operation, the refrigerant liquid entering from the motor coolant inlet 81 first flows through the first cooling section 71 between the stator 6 and the motor casing 1 in a spiral manner, taking away the heat of the stator 6 and changing The gas is then passed to the chamber at the right end of the stator 6 (the right end in Figure 2). After the refrigerant liquid entering from the bearing coolant inlet 82 enters the passage formed by the mounting plate 11 of the main refrigerant lubricating bearing and the second diffuser 12, the bearing cooling section on the bearing (the bearing away from the return port 5) is lubricated by the main refrigerant. 73. After the bearing is heated, the gas enters into the right end chamber of the stator 6 and mixes with the gas after cooling the stator 6 of the motor.

After mixing, the gas flows in a right-to-left direction (from right to left in Fig. 2) through an air gap between the stator 6 and the rotor 10 (i.e., the second cooling section 72) to the left end of the stator (left end in Fig. 2) The chamber takes away the heat of the rotor 10, and then enters the bearing cooling section 73 of the secondary refrigerant lubricated bearing (the bearing close to the return port 5), takes away the secondary bearing heat, and then enters the first diffuser 4 and the secondary refrigerant lubricated bearing. The passage formed by the mounting plate 11 is finally mixed with the main airflow in the first compression portion through the air return port 5 provided in the first diffuser to reduce the temperature of the main airflow, and then introduced into the right end of FIG. 2 through an external pipe or other passage. In the second compression section.

It should be noted that on the hub outlet side of the second diffuser 12 near the second impeller 13, there is no return air port as provided by the first diffuser 4, but a completely closed state.

In summary, for the two-stage double-headed impeller oil-free centrifugal compressor, this built-in return air structure fully exploits the advantages of the refrigerant-lubricated bearing, and combines the motor cooling temperature control state by incorporating the air return port 5 in In the diffuser of the previous stage, the main bearing cooling gas is mixed with the motor cooling gas and passed through the secondary bearing to be fully mixed with the primary airflow of the previous stage to increase the density of the pre-stage mainstream gas, lower the temperature, and effectively reduce the airflow noise. As the temperature of the airflow drops, the compression power consumption of the next stage will be reduced, thereby improving the energy efficiency of the compressor. At the same time, the external connection circuit of the external motor is omitted, and the leakage point of the system is reduced, thereby achieving the purpose of improving the cost performance of the compressor.

The compressor according to the present disclosure and the air conditioner having the same have the following technical effects:

Solving the problem of system complexity and leakage caused by the addition of the external return air line of the motor. Eliminate the external motor return line connection, reduce costs, improve assembly efficiency and compressor cost performance.

The low-temperature gas cooling capacity of the motor cavity is reused, and the comprehensive utilization rate is high. The low-temperature gas is mixed with the pneumatic flow channel gas, and the airflow density is increased, so that the sound wave consumes sound energy between the high-density molecules, reduces the airflow noise, and passes the low-temperature gas and the pneumatic flow. The gas mixing makes it effective to reduce the inlet temperature of the lower impeller, reduce the compressor, and improve the energy efficiency of the compressor.

Utilizing the advantages of oil-free centrifugal compressor and motor temperature control, the internal compressor return line is made simple, so that the external pipeline of the whole compressor and unit is simple, reducing noise, improving efficiency, cooling the bearing, optimizing the system piping, and reducing Both the leak point and the reliability of the improvement can produce good results.

The above description is only a preferred embodiment of the present disclosure, and is not intended to limit the disclosure, and various changes and modifications may be made to the present disclosure. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and scope of the present disclosure are intended to be included within the scope of the present disclosure.

Claims

A compressor, comprising:

a motor comprising a motor housing (1) and a cooling passage disposed in the motor housing (1);

a first compression portion disposed at a first end of the motor, the first compression portion including a first housing (2) and a first diffuser (4) coupled to the first housing (2) The first diffuser (4) is provided with a gas return port (5), and the cooling passage communicates with the first compression portion through the air return port (5).
The compressor according to claim 1, wherein one end of the air return port (5) adjacent to the motor is a first end, and one end of the air return port (5) adjacent to the first compressing portion is a second end. a line connecting the first end and the second end of the air return port (5) is a first line, and the first line has a first angle with a vertical plane of the rotation axis of the motor;

The distance between the first end of the air return port (5) and the rotation axis is smaller than the distance between the second end of the air return port (5) and the rotation axis.
The compressor according to claim 2, wherein said first included angle ranges from 15° to 35°.
The compressor according to claim 2, wherein said first wire has a second angle between said motor rotation axis and a plane defined by a midpoint of said first line;

a projection length of the first end of the air return port (5) and the rotation axis in a vertical plane of the rotation axis is smaller than a distance between the second end of the air return port (5) and the rotation axis The projection length in the vertical plane of the axis of rotation.
The compressor according to claim 4, wherein said second included angle ranges from 55° to 75°.
A compressor according to claim 1, wherein said air return ports (5) are plural and are sequentially spaced apart on a first circumference, the center of said first circumference being located on a rotational axis of said motor.
The compressor according to claim 6, wherein said air return ports (5) are evenly spaced on said first circumference, and centers of adjacent two of said air return ports (5) and said first circumference The line of the center forms a third angle, and the third angle ranges from 12° to 30°.
The compressor according to claim 1, wherein said motor further comprises a stator (6), said stator (6) being disposed in said motor housing (1), and said motor housing (1) a fixed connection, the cooling passage comprising a first cooling section (71), the first cooling section (71) being provided on an inner wall of the motor housing (1) corresponding to the stator (6) The opening of the first cooling section (71) faces the stator (6).
The compressor according to claim 8, wherein said first cooling section (71) is a spiral section extending helically in the axial direction of said stator (6).
The compressor according to claim 8, further comprising a motor coolant inlet (81), said motor coolant inlet (81) being in communication with said first cooling section (71) and located in said motor housing ( 1) The position corresponding to the stator (6).
The compressor of claim 8 wherein said motor further comprises:

a rotor (10), the rotor (10) being located in the stator (6), the cooling passage further comprising a second cooling section (72), the second cooling section (72) comprising the rotor (10) And a gap between the stator (6).
A compressor according to claim 1, wherein said motor further comprises a bearing assembly, said bearing assembly comprising a bearing (15), said cooling passage further comprising a bearing disposed on said bearing (15) for cooling refrigerant to pass therethrough Cooling section (73).
The compressor according to claim 12, further comprising a bearing coolant inlet (82), said bearing coolant inlet (82) being in communication with said bearing cooling section (73) and located in said motor housing (1) ) corresponds to the position of the bearing (15).
The compressor according to claim 13, wherein said motor further comprises a stator (6), said stator (6) being disposed in said motor housing (1), and said motor housing (1) A fixed connection, the bearing assembly being two, and respectively disposed on both sides of the stator (6), the bearing coolant inlet (82) being disposed corresponding to a bearing assembly remote from the first compression portion.
The compressor according to claim 1, wherein said motor further comprises a stator (6), a rotor (10) and a bearing (15), said stator (6) being disposed in said motor housing (1), And fixedly connected to the motor housing (1), the cooling passage includes a first cooling section (71), the first cooling section (71) is located on an inner wall of the motor housing (1) and a position corresponding to the stator (6), an opening of the first cooling section (71) faces the stator (6); the rotor (10) is located in the stator (6), and the cooling passage is further A second cooling section (72) is included, the second cooling section (72) including a gap between the rotor (10) and the stator (6); the cooling passage further comprising a bearing (15) disposed a bearing cooling section (73) for cooling refrigerant to pass through;

a refrigerant is introduced into the motor, and at least a portion of the refrigerant flows out of the air return port (5) through the first cooling section (71) and the second cooling section (72), at least another part of the refrigerant The refrigerant sequentially passes through the third cooling section (73) on the bearing (15) remote from the air return port (5), the second cooling section (72), and the proximity to the air return port (5) The third cooling section (73) on the bearing (15) then flows out of the air return port (5).
The compressor according to claim 1, wherein said compressor further comprises a second compression portion, said second compression portion being disposed at a second end of said motor, said first compression portion for achieving one-stage compression The second compression portion is used to implement secondary compression.
The compressor according to claim 1, wherein said first compression portion further comprises a first impeller (3), said air return port (5) being obliquely disposed, and an inclination angle enabling said return air direction to follow said first The direction of flow of the airflow in the impeller (3).
An air conditioner comprising the compressor of claim 1.