CN113809885A

CN113809885A - Compressor and air conditioner and automobile with same

Info

Publication number: CN113809885A
Application number: CN202111040292.8A
Authority: CN
Inventors: 杨玉明; 陈玉辉; 叶文腾; 钟瑞兴
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-09-06
Filing date: 2021-09-06
Publication date: 2021-12-17

Abstract

The invention discloses a compressor, and an air conditioner and an automobile with the same. The compressor comprises a motor cylinder, a first-stage impeller, a first-stage diffuser, a motor assembly and a second-stage diffuser. One end of the motor cylinder is provided with a cooling air inlet, and the other end of the motor cylinder is provided with a cooling air outlet. And the first-stage impeller, the first-stage diffuser, the motor assembly and the second-stage diffuser form a cooling gas flow channel communicated with the cooling gas inlet and the cooling gas outlet. Compressed cooling gas is input from the outside to efficiently cool a rotor, a stator, supporting parts of the rotor and the like of the compressor. Therefore, faults such as demagnetization of the motor, high-temperature failure of the bearing and the like can be effectively prevented, and the operation stability, negative pressure capacity and service time of the compressor are improved. Particularly, after the back of the first-stage impeller is provided with the coaxially rotating turbine, the turbine can also drive the motor rotor to rotate so as to reduce the power consumption of the compressor and also reduce the temperature of the cooling gas so as to bring away more heat.

Description

Compressor and air conditioner and automobile with same

Technical Field

The invention mainly relates to a fluid conveying machine, in particular to a compressor with high cooling efficiency, an air conditioner with the compressor and an automobile with the compressor.

Background

With the continuous development and progress of science and technology, all industries strive to move towards higher and more distant targets. In recent years, with the rise of energy cost and the increase of environmental protection requirements, energy conservation and environmental protection have become important issues to be ignored. The water vapor compressor is widely used in industry by virtue of the characteristics of high efficiency, energy conservation, environmental friendliness and the like, and the domestic water vapor compressor is widely applied to the industries of salt making, environmental protection, distillation, food, pharmacy, drying and the like at present. The water as the fourth-generation refrigerant has the advantages of environmental protection, easily obtained raw materials, low cost, good safety, high stability, large latent heat of gasification and the like, and can completely meet the requirement of environmental protection. However, water also has some non-negligible limitations as a refrigerant, and due to low molecular weight, large specific volume and high adiabatic index of water vapor, the water vapor system is determined to have the limitations of small pressure difference, large pressure ratio, small refrigerating capacity per unit capacity, large volume flow, high exhaust temperature and the like, and accordingly higher requirements are put forward on the water vapor compressor. The current water vapor compressors on the market are mainly classified into screw type, twisted lobe roots type and centrifugal type. The screw type steam compressor has good stability and high pressure ratio, but the volume flow is limited, and the screw type steam compressor can be used for systems with small flow and large pressure ratio; the Roots compressor has small vibration and simple structure, but has small pressure specific flow, and is commonly used in systems with medium and small refrigeration capacity and large temperature rise; the centrifugal water vapor compressor has large volume flow, but the single-stage pressure ratio is small, so the problem of temperature rise of the compressor is prominent.

Therefore, how to improve the safety and reliability of the existing centrifugal steam compressor in high-temperature resistance and long-term operation under a large-flow working condition has become an important technical problem in the industry.

Disclosure of Invention

The invention provides a compressor, an air conditioner with the compressor and an automobile, and aims to solve the problem of how to improve the high temperature resistance and the long-term running safety and reliability of the conventional centrifugal water vapor compressor under the working condition of high flow.

The invention provides a compressor which comprises a motor cylinder, a first-stage impeller, a first-stage diffuser, a motor assembly and a second-stage diffuser. And one end of the motor cylinder is provided with a cooling gas inlet, the other end of the motor cylinder is provided with a cooling gas outlet, and the primary impeller, the primary diffuser, the motor assembly and the secondary diffuser form a cooling gas flow channel communicated with the cooling gas inlet and the cooling gas outlet.

Preferably, one side of the first-stage impeller, which faces the first-stage diffuser, is an integrated and coaxially arranged turbine.

Preferably, the motor assembly comprises an axial bearing, a thrust disc, a bearing support, a first-stage radial bearing, a second-stage radial bearing, a motor stator and a motor rotor.

Preferably, the cooling air flow channel comprises a compressed air storage cavity which is annularly arranged between the motor cylinder and the first-stage diffuser, and the cooling air inlet is communicated with the compressed air storage cavity.

Preferably, the cooling air flow channel further comprises: the cooling air circulation system comprises a turbine driving annular compressed air cavity, an air inlet, a radial gap, a cooling air flow channel, a gap between a motor stator, a motor cylinder and a motor rotor, a cooling air flow channel, a cooling air discharge flow channel, a cooling air outlet and a cooling air outlet, wherein the turbine driving annular compressed air cavity is arranged in a first-stage diffuser and communicated with a compressed air storage cavity, the air inlet is communicated with the turbine driving annular compressed air cavity, the radial gap is communicated with an exhaust port of the turbine and encircled between a thrust plate and the first-stage diffuser, the gap is communicated with the radial gap and communicated with the first-stage diffuser and the bearing support, the cooling air flow channel of the first-stage radial bearing, the gap is arranged between the motor stator, the motor cylinder and the motor rotor, the cooling air flow channel of the second-stage radial bearing, the cooling air discharge flow channel is arranged in the second-stage diffuser, and the cooling air outlet is communicated with the cooling air discharge flow channel.

Preferably, the compressed gas storage cavity is communicated with the turbine driving annular compressed gas cavity through a plurality of gas guide holes which are annularly and uniformly distributed on the first-stage diffuser.

Preferably, the end surface of the first-stage diffuser facing the axial bearing is uniformly provided with a plurality of radial first-stage diffuser flow grooves, and the end surface of the bearing support facing the axial bearing is uniformly provided with a plurality of radial bearing support flow grooves.

Preferably, the cooling channels of the first-stage radial bearing and the second-stage radial bearing are respectively an annular flow groove arranged on the end face of the radial bearing shell facing the outer end of the motor rotor and a plurality of axial cooling air channels communicated with the annular flow groove, and the axial cooling air channels are communicated with gaps among the motor stator, the motor cylinder and the motor rotor; the annular flow groove of the primary radial bearing is communicated with the flow groove of the bearing support.

Preferably, a plurality of radial secondary diffuser flow grooves are uniformly distributed in the secondary diffuser, and the annular flow grooves of the secondary radial bearing and the cooling gas outlet are communicated through the secondary diffuser flow grooves.

Preferably, the first-stage diffuser is made of a first-stage diffuser body and a first-stage sealing plate in a split mode, and an annular groove formed in the inner side face of the first-stage sealing plate and the first-stage diffuser body form the turbine driving annular compression air cavity.

Preferably, the motor cylinder is further provided with an inlet and an outlet of cooling liquid, the inner wall of the motor cylinder is matched with the water cooling jacket to form a spiral cooling liquid flow channel, and the through-flow sectional area of the cooling flow channel is 50-100mm²And the length of the cooling liquid flow channel is not shorter than the axial length of the silicon steel sheet on the motor stator.

The invention provides an air conditioner, which comprises the compressor.

The invention provides an automobile which comprises the compressor.

The compressor provided by the invention circularly cools the rotor, the stator, the supporting parts of the rotor and the like of the compressor by inputting compressed cooling gas from the outside, and is assisted by the enhanced cooling of cooling liquid, so as to realize the high-efficiency cooling of the compressor. Particularly, the back of the first-stage impeller is provided with the turbine which coaxially rotates, when compressed cooling gas is led out to enter the turbine from the cooling gas flow channel, the turbine drives the rotor to rotate in the same direction, the power consumption of the motor of the compressor can be reduced, and most importantly, the compressed cooling gas is expanded through the turbine to release heat, so that the gas temperature is reduced. And then when cooling air flows through the inside of the bearing and the driving motor, more bearings and heat generated in the motor operation process can be taken away, so that the faults of demagnetization of the motor, high-temperature failure of the bearings and the like can be effectively prevented, the operation stability of the compressor is effectively improved, and the negative pressure capacity and the service time of the compressor are improved.

Drawings

FIG. 1 is a schematic diagram of a cross-sectional structure of a centrifugal water vapor compressor according to an embodiment of the present invention;

FIG. 2 is a schematic view of the projection from F-F in FIG. 1;

FIG. 3 is a schematic view of the projection from A-A in FIG. 1;

FIG. 4 is a sectional view taken along line B-B in FIG. 1;

FIG. 5 is a sectional view taken along the direction C-C in FIG. 1;

FIG. 6 is a sectional view taken along line D-D in FIG. 1;

fig. 7 is a schematic sectional view taken along line E-E in fig. 1.

Detailed Description

The invention is further described with reference to the following figures and examples.

As shown in fig. 1, the present invention provides an embodiment of a compressor: a centrifugal water vapor compressor comprises a first-stage volute 1, a first-stage impeller 2, a first-stage diffuser 3, an axial bearing 4, a first-stage radial bearing 5, a second-stage radial bearing 6, a bearing support 7, a thrust disc 8, a motor cylinder 9, a motor stator 10, a motor rotor 11, a second-stage sealing plate 17, a second-stage diffuser 12, a second-stage volute 13, a second-stage impeller 14, locking screws and the like. The left end of the motor cylinder 9 is provided with a cooling air inlet 15 and the right end is provided with a cooling air outlet 16. A cooling air flow channel communicated with a cooling air inlet 15 and a cooling air outlet 16 is formed among the first-stage impeller 2, the first-stage diffuser 3, the axial bearing 4, the thrust disc 8, the bearing support 7, the first-stage radial bearing 5, the second-stage radial bearing 6, the motor stator 10, the motor rotor 11 and the second-stage diffuser 12. In this embodiment, the first-stage impeller 2 is an integral turbine 20 coaxially arranged on one side facing the first-stage diffuser 3. The first-stage impeller 2 and the turbine can be manufactured separately and then assembled into a whole as required. And the first-stage diffuser 3 is manufactured by the first-stage diffuser body and the first-stage sealing plate 18 in a split mode and then is combined into a whole. Referring to fig. 2, a turbine-driving annular compression air chamber is formed between an annular groove 19 formed on an inner side surface of the primary seal plate 18 and the primary diffuser body. The secondary diffuser 12 is made of a secondary diffuser body and a secondary sealing plate 17 in a split manner and then combined into a whole.

As shown in fig. 1, the cooling air flow channel according to the present invention includes: the compressed gas storage cavity 21 is annularly arranged between the motor cylinder 9 and the first-stage diffuser 3 in the radial direction, and the cooling gas inlet 15 is communicated with the compressed gas storage cavity 21. The cooling air flow channel also comprises the following components which are sequentially communicated: a turbine driving annular compressed air cavity which is arranged in the first-stage diffuser 3 and communicated with a compressed air storage cavity 21, an air inlet of a turbine 20 which is communicated with the turbine driving annular compressed air cavity, a surrounding radial gap between a thrust disc 8 and the first-stage diffuser 3 which are communicated with an exhaust port of the turbine, a first-stage diffuser 3 which is communicated with the radial gap, a gap between the axial bearing 4, the thrust disc 8 and a bearing support 7, a cooling air flow channel of the first-stage radial bearing 5, a gap between the motor stator 10, the motor cylinder 9 and the motor rotor 11, a cooling air flow channel of the second-stage radial bearing 6, a cooling air discharge flow channel arranged in the second-stage diffuser 12, and a cooling air outlet 16 which is communicated with the cooling air discharge flow channel. Referring to fig. 3, further, the compressed air storage chamber 21 is communicated with the turbine driving annular compressed air chamber through eight air guide holes 22 annularly and uniformly distributed on the body of the first-stage diffuser 3. As shown in fig. 4, four radial first-stage diffuser flow grooves 23 are uniformly distributed on the end surface of the first-stage diffuser 3 facing the axial bearing 4. As shown in fig. 5 and 6, four radial bearing support flow grooves 24 are uniformly distributed on the end surface of the bearing support 7 facing the axial bearing 4.

The cooling flow channel of the first-stage radial bearing 5 is as follows: the first-stage radial bearing 5 is provided with an annular flow groove 26 facing the end face of the radial bearing housing at the left end of the motor rotor 11, and eight axial cooling air flow channels 25 communicated with the annular flow groove 26. And the cooling flow path of the secondary radial bearing 6 is: the secondary radial bearing 6 is provided with an annular flow groove 31 facing the end face of the radial bearing housing at the right end of the motor rotor 11, and eight axial cooling air flow channels 32 communicating with the annular flow groove 31. Axial

cooling air channels

25 and 32 of the first-stage radial bearing and the second-stage radial bearing 5 and 6 are communicated with gaps between the motor stator 10 and the motor cylinder 9 and between the motor rotor 11. The annular flow groove 26 of the primary radial bearing 5 communicates with the bearing support flow groove 24, and the eight axial cooling gas flow passages 25 of the primary radial bearing 5 communicate with the annular flow groove 26. As shown in fig. 6 and 7, four radial second-stage diffuser flow grooves 27 are uniformly distributed in the second-stage diffuser 12, the second-stage diffuser flow grooves 27 communicate the annular flow groove 31 of the second-stage radial bearing 6 with the four cooling air outlets 16 at the right end of the motor cylinder 9, and eight axial cooling air flow channels 32 of the second-stage radial bearing 6 communicate with the annular flow groove 31.

As shown in fig. 1, the cooling of the compressor of the present invention mainly consists of liquid cooling and air cooling. Wherein, the motor cylinder 9 is provided with a cooling gas inlet and outlet, and is also provided with a cooling liquid inlet 28 and a cooling liquid outlet 29, a cooling liquid flow passage 30 is formed by matching the motor cylinder and a water cooling jacket at the position corresponding to the motor stator 10, the cooling liquid flow passage is distributed spirally and is used for cooling silicon steel sheets of the motor stator by the circulation of cooling liquid, and the flow area of the cooling liquid flow passage is 50-100mm²Preferably, the length of the cooling liquid flow channel is not shorter than the length of the motor stator silicon steel sheet. Interference fit is adopted between the motor cylinder and the water cooling jacket. The motor stator is fixed inside the motor cylinder in an interference connection mode. In addition, the first-stage diffuser 3 and the second-stage diffuser 12 are fixed on the motor cylinder 9 through screw connection; the first-stage and second-

stage sealing plates

18 and 17 are also fixed on the first-stage and second-stage diffusers through screw connection; the same-stage sealing plate 18 on the outer circle of the hub of the assembly of the first-stage impeller turbine is sealed in a comb sealing mode; the first-stage radial bearing and the second-stage radial bearing 5 and 6 are respectively arranged on the bearing support 7 and the second-stage diffuser 12, the first-stage radial bearing and the second-stage radial bearing support the motor rotor 11 to rotate, axial supporting and positioning are realized through the two axial bearings 4 to prevent the motor rotor from generating axial movement, and the two axial bearings are respectively arranged on the first-stage diffuser and the bearing support through screw connection.

Referring to fig. 1, the cooling gas of the present invention flows as follows: firstly, the externally introduced compressed cooling gas enters the compressed gas storage cavity 21 through the cooling gas inlet 15 arranged on the motor cylinder 9, then flows through the turbine to drive the annular compressed gas cavity, then flows through the turbine 20, enters the cavity between the first-stage diffusion flow groove 23 and the bearing support 7 through the radial gap between the first-stage diffuser 3 and the thrust plate 8, then flows through the first-stage radial bearing 5 to enter the cavity and the gap between the motor rotor 11 and the motor cylinder 9 and the motor stator 10, then flows through the second-stage radial bearing 6, and finally is discharged from the four cooling gas outlets 16 through the second-stage diffuser flow groove 27, so as to achieve the purpose of cooling the compressor. Wherein, the air guide holes 22 evenly distributed on the body of the first-stage diffuser 3 can lead the compressed cooling air to be evenly discharged to the turbine 20, thereby ensuring the operation stability of the turbine. The gas flowing through the turbine driving annular compressed air cavity enters the inlet flow passage of the turbine 20, the flow passage is not too wide, so that the speed of the compressed cooling air flow can be sufficiently increased through the flow passage to drive the turbine 20 to operate efficiently, the width of the flow passage is preferably 3-10mm, and the flow passage is determined according to the power difference of the compressor. When the compressed cooling air flows through the turbine 20, on one hand, the high-speed flowing cooling air drives the turbine to rotate at a high speed, and further drives the coaxially rotating motor rotor 11 to rotate, so that the power consumption of the motor is reduced. On the other hand, the cooling gas is expanded by the turbine to release heat, so that the temperature of the cooling gas is reduced, and the cooling is more facilitated. The externally introduced compressed cooling air enters from the left end of the compressor and passes through the cooling air flow channel, one path of the cooling air takes away heat of relevant parts of the compressor and cools the parts, and finally the cooling air is discharged from the right end of the compressor, so that the compressor is efficiently cooled. Especially, the turbine which is coaxially connected and rotates is arranged on the back of the first-stage impeller, so that the power consumption of the motor of the compressor can be reduced, the temperature of cooling gas can be reduced, more bearings and heat generated by the motor in the operation process can be taken away, the fault problems of demagnetization of the motor, high-temperature failure of the bearings and the like can be effectively prevented, the operation stability of the compressor is effectively improved, and the negative pressure capacity and the service time of the compressor are improved.

The invention also provides an air conditioner, which is provided with the compressor provided by the invention. The invention also provides an automobile which is provided with the compressor provided by the invention.

The above description is only exemplary of the present invention and should not be taken as limiting the invention, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The utility model provides a compressor, includes the motor barrel, one-level impeller, one-level diffuser, motor element, second grade diffuser, its characterized in that, the one end of motor barrel is equipped with the cooling gas entry and the other end is equipped with the cooling gas export, one-level impeller, one-level diffuser, motor element, constitute the intercommunication among the second grade diffuser the cooling gas entry and the cooling gas export the cooling gas runner.

2. The compressor of claim 1, wherein a side of the first-stage impeller facing the first-stage diffuser is a coaxially disposed turbine.

3. The compressor of claim 2, wherein the motor assembly includes an axial bearing, a thrust disk, a bearing support, a primary radial bearing, a secondary radial bearing, a motor stator, and a motor rotor.

4. The compressor of claim 3 wherein said cooling gas flowpath includes a compressed gas receiver chamber disposed annularly between said motor cylinder and said one-stage diffuser, said cooling gas inlet communicating with said compressed gas receiver chamber.

5. The compressor of claim 4 wherein said cooling airflow path further comprises, in series: the turbine driving annular compressed air cavity is arranged in the first-stage diffuser and communicated with the compressed air storage cavity, the air inlet of the turbine is communicated with the turbine driving annular compressed air cavity, the radial gap between the thrust disk and the first-stage diffuser is communicated with the exhaust port of the turbine, the gap between the first-stage diffuser and the bearing support is communicated with the radial gap, the cooling air flow channel of the first-stage radial bearing, the gap between the motor stator and the motor cylinder as well as the motor rotor, and the cooling air flow channel of the second-stage radial bearing is arranged in the cooling air discharge flow channel of the second-stage diffuser and is communicated with the cooling air outlet of the cooling air discharge flow channel.

6. The compressor as claimed in claim 5, wherein said compressed gas storage chamber is communicated with said turbine-driving annular compressed gas chamber through a plurality of gas guide holes annularly and uniformly distributed in said one-stage diffuser.

7. The compressor of claim 5, wherein the end surface of the one-stage diffuser facing the axial bearing is provided with a plurality of radial one-stage diffuser flow grooves, and the end surface of the bearing support facing the axial bearing is provided with a plurality of radial bearing support flow grooves.

8. The compressor of claim 7, wherein the cooling channels of the primary and secondary radial bearings are respectively: the axial cooling air flow channels are communicated with gaps among the motor stator, the motor cylinder and the motor rotor; the annular flow groove of the primary radial bearing is communicated with the flow groove of the bearing support.

9. The compressor of claim 8, wherein a plurality of radial second diffuser flow slots are provided in the second diffuser, the second diffuser flow slots communicating the annular flow slot of the second radial bearing with the cooling air outlet.

10. The compressor as claimed in claim 5, wherein the first-stage diffuser is formed by a first-stage diffuser body and a first-stage sealing plate separately, and the annular groove formed on the inner end surface of the first-stage sealing plate and the first-stage diffuser body form the turbine-driving annular compression air chamber therebetween.

11. The compressor as claimed in claim 3, wherein the motor cylinder is further provided with an inlet and an outlet for the cooling liquid, the inner wall of the motor cylinder and the water cooling jacket cooperate to form a spiral cooling liquid flow passage, and the cross-sectional flow area of the cooling liquid flow passage is 50-100mm²And the length of the cooling liquid flow channel is not shorter than the axial length of a silicon steel sheet on the motor stator.

12. An air conditioner characterized by comprising the compressor according to any one of claims 1 to 11.

13. An automobile comprising the compressor according to any one of claims 1 to 11.