CN107664143B - Compressor and air conditioner with same - Google Patents
Compressor and air conditioner with same Download PDFInfo
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- CN107664143B CN107664143B CN201710962857.5A CN201710962857A CN107664143B CN 107664143 B CN107664143 B CN 107664143B CN 201710962857 A CN201710962857 A CN 201710962857A CN 107664143 B CN107664143 B CN 107664143B
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- bearing
- cooling
- stator
- compressor
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- 238000001816 cooling Methods 0.000 claims abstract description 118
- 230000006835 compression Effects 0.000 claims abstract description 58
- 238000007906 compression Methods 0.000 claims abstract description 58
- 239000003507 refrigerant Substances 0.000 claims description 38
- 230000000712 assembly Effects 0.000 claims description 10
- 238000000429 assembly Methods 0.000 claims description 10
- 239000002826 coolant Substances 0.000 claims description 10
- 239000000110 cooling liquid Substances 0.000 claims description 9
- 239000012809 cooling fluid Substances 0.000 claims description 3
- 239000007789 gas Substances 0.000 description 35
- 238000005461 lubrication Methods 0.000 description 14
- 230000000694 effects Effects 0.000 description 6
- 238000004891 communication Methods 0.000 description 5
- 239000000112 cooling gas Substances 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000012545 processing Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 239000000725 suspension Substances 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/5806—Cooling the drive system
Abstract
The application provides a compressor and an air conditioner with the same. The compressor according to the present application includes: the motor comprises a motor shell and a cooling channel arranged in the motor shell; the first compression part is arranged at the first end of the motor, the first compression part comprises a first shell and a first diffuser connected with the first shell, a motor air return port is arranged on the first diffuser, and the cooling channel is communicated with the first compression part through the motor air return port. The compressor can reduce the external air return pipeline and the leakage point.
Description
Technical Field
The application relates to the field of air conditioning equipment, in particular to a compressor and an air conditioner with the same.
Background
In a refrigeration centrifugal compressor, cooling of the motor is generally performed by a refrigerant. It is common practice to introduce a cooling refrigerant into the motor and to directly return the motor return air to the evaporator or intermediate economizer of the refrigeration system. Fig. 1 shows a motor muffler connection structure, in which a motor muffler 2 'is externally arranged and connected with a motor through a first connection point 1', and the motor muffler 2 'is connected with an evaporator or an intermediate economizer through a second connection point 5'. Wherein, motor muffler 2' is fixed through first fixed bolster not 3' and second fixed bolster 4 '. The motor cooling mode is added with an external connecting pipeline for supplying refrigerant, so that the whole structure is complex, the cost is high, and potential hidden trouble points are increased due to the increase of the connecting pipeline, and the whole reliability is affected.
Furthermore, oilless and cost-effective are the directions of development of refrigeration centrifugal compressors, such as: the magnetic suspension centrifugal compressor, the air suspension centrifugal compressor and the refrigerant lubrication bearing centrifugal compressor can well realize oilless because a huge oil way system is removed and only refrigerant working media exist in the whole compressor. However, in the prior art, the return air of these types of compressors is also connected back to the evaporator and the flash evaporator, and this structure naturally also has the problems of complex system structure and high cost.
Disclosure of Invention
The application aims to provide a compressor capable of reducing connecting pipelines and an air conditioner with the same.
The present application provides a compressor, comprising: the motor comprises a motor shell and a cooling channel arranged in the motor shell; the first compression part is arranged at the first end of the motor, the first compression part comprises a first shell and a first diffuser connected with the first shell, a motor air return port is arranged on the first diffuser, and the cooling channel is communicated with the first compression part through the motor air return port.
Optionally, one end of the motor air return port, which is close to the motor, is a first end, one end of the motor air return port, which is close to the first compression part, is a second end, a connecting line between the first end of the motor air return port and the second end is a first connecting line, a first included angle is formed between the first connecting line and a normal vertical surface where a rotation axis of the motor is located, and on the normal vertical surface, the distance between the first end of the motor air return port and the rotation axis is smaller than the distance between the second end of the motor air return port and the rotation axis.
Optionally, the first included angle has a value ranging from 15 ° to 35 °.
Optionally, the first connecting line has a second included angle with an axial vertical surface where the rotation axis of the motor is located, and on the axial vertical surface, a distance between the first end of the air return opening of the motor and the rotation axis is smaller than a distance between the second end of the air return opening of the motor and the rotation axis.
Optionally, the second included angle ranges from 55 ° to 75 °.
Optionally, the motor air return port is a plurality of, and sets up on first circumference interval in proper order, and the center of first circumference is located the axis of rotation of motor.
Optionally, the motor air return ports are uniformly arranged at intervals on the first circumference, and a third included angle is formed by connecting the centers of two adjacent motor air return ports with the center of the first circumference, and the value range of the third included angle is 12-30 degrees.
Optionally, the motor further comprises a stator, the stator is arranged in the motor shell and fixedly connected with the motor shell, the cooling channel comprises a first cooling section, the first cooling section is located on the inner wall of the motor shell and corresponds to the stator in position, and an opening of the first cooling section faces the stator.
Optionally, the first cooling section is a helical section extending helically along the axial direction of the stator.
Optionally, a motor coolant inlet is provided on the motor housing at a position corresponding to the stator in communication with the first cooling section.
Optionally, the motor further comprises: the rotor is positioned in the stator, and the cooling channel further comprises a second cooling section, wherein the second cooling section comprises a gap between the rotor and the stator.
Optionally, the motor further comprises a bearing assembly, the bearing assembly comprising: the bearing, the cooling channel still includes the bearing cooling section that sets up on the bearing and supplies the coolant to pass through.
Optionally, a bearing cooling fluid inlet communicated with the bearing cooling section is arranged on the motor shell at a position corresponding to the bearing.
Optionally, the two bearing assemblies are arranged on two sides of the stator in a one-to-one correspondence, and the bearing cooling liquid inlets are arranged corresponding to the bearing assemblies far away from the first compression part.
Optionally, the motor further comprises a stator, a rotor and a bearing, wherein the stator is arranged in the motor shell and fixedly connected with the motor shell, the cooling channel comprises a first cooling section, the first cooling section is positioned on the inner wall of the motor shell and is correspondingly arranged with the stator, and an opening of the first cooling section faces the stator; the rotor is positioned in the stator, the cooling channel further comprises a second cooling section, and the second cooling section comprises a gap between the rotor and the stator; the cooling channel also comprises a bearing cooling section which is arranged on the bearing and used for the cooling refrigerant to pass through; at least one part of refrigerant flows out from the motor air return port after sequentially passing through the first cooling section and the second cooling section, and at least one other part of refrigerant flows out from the motor air return port after sequentially passing through the bearing cooling section on the bearing far away from the motor air return port, the second cooling section and the bearing cooling section on the bearing near the motor air return port.
Optionally, the compressor further comprises a second compression part, and the second compression part is arranged at the second end of the motor.
According to another aspect of the present application, there is provided an air conditioner including a compressor, which is the above-mentioned compressor.
According to the compressor and the air conditioner with the same, the motor air return port is arranged on the first diffuser, so that the air return cooled by the motor enters the first compression part through the motor air return port, the built-in exhaust of the motor can be realized, the air return pipe is not required to be arranged outside the motor, the external space is saved, the problems of the increase of the complexity and the high cost of the overall structure caused by the air return pipe of the external motor are avoided, and the problems of the increase of potential hidden trouble points caused by the increase of connecting pipelines and the influence on the overall reliability are avoided.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
FIG. 1 is a schematic diagram of a prior art motor connected to an air return structure via an external motor air return duct;
FIG. 2 is a schematic cross-sectional structure of a compressor according to the present application;
FIG. 3 is a schematic cross-sectional view of a first diffuser of a compressor according to the present application;
FIG. 4 is a schematic side view of a first diffuser of a compressor according to the present application;
FIG. 5 is a schematic diagram of a front view of a first diffuser of a compressor according to the present application;
fig. 6 is a schematic perspective view of a first diffuser of a compressor according to the present application.
Reference numerals illustrate:
the prior art comprises the following steps:
1', a first connection point; 2', a motor muffler; 3', a first fixed bracket; 4', a second fixed bracket; 5', a second connection point;
the application comprises the following steps:
1. a motor housing; 2. a first housing; 3. a first impeller; 4. a first diffuser; 5. a motor return air port; 6. a stator; 10. a rotor; 11. a mounting plate; 12. a second diffuser; 13. a second impeller; 14. a second housing; 15. a bearing; 71. a first cooling section; 72. a second cooling section; 73. a bearing cooling section; 81. a motor cooling liquid inlet; 82. and a bearing cooling liquid inlet.
Description of the embodiments
The application will be described in detail below with reference to the drawings in connection with embodiments.
As shown in fig. 2 and 6, according to an embodiment of the present application, a compressor includes a motor including a motor housing 1 and a cooling passage provided in the motor housing 1, and a first compression part. The first compression part is arranged at the first end of the motor, and comprises a first shell 2 and a first diffuser 4 connected with the first shell 2, a motor return air port 5 is arranged on the first diffuser 4, and a cooling channel is communicated with the first compression part through the motor return air port 5.
Through set up motor return air port 5 on first diffuser 4, make the return air after the motor cooling get into in the first compression portion through motor return air port 5, can realize the built-in exhaust of motor like this, and need not at the outer muffler of installing of motor, saved the outer space, avoided the problem that the increase overall structure complexity, the cost is high that external motor return air pipe caused, and avoided increasing because connecting line increases, the potential hidden danger point that causes increases, influences the problem of overall reliability.
The first compression part further includes a first impeller 3, the first impeller 3 being disposed in the first housing 2, and compression of the gas is achieved by rotation of the first impeller 3. For the motor cooled by adopting the refrigerant, the temperature of the motor winding is generally 30 ℃ and the temperature difference of heat transfer is considered to be 10 ℃ in the cooling process, and the gas in the motor cavity is generally only 20 ℃, so that the temperature of the gas in the motor cavity is low for other parts in the compressor, which are higher than the temperature of the gas in the motor cavity, is a good cold source. The motor air return port 5 is internally arranged, so that the air after cooling the motor is discharged into the first compression part, the cold source can be reused, and the air entering the first compression part reduces the temperature of the air discharged from the air outlet of the first impeller 3 in the first compression part, and effectively reduces the air flow noise; on the other hand, due to the reduction of the gas temperature, the power consumption in the subsequent gas compression is reduced, which is beneficial to saving energy.
The structure can be applied to any compressor adopting a refrigerant cooling motor or a compressor adopting a refrigerant lubrication bearing, and is particularly suitable for more than two stages of double-head impeller oilless centrifugal compressors.
Optionally, in this embodiment, the compressor further includes a second compression portion, and the second compression portion is disposed at a second end of the motor. The second compression part is connected with the first compression part, and the exhaust gas compressed by the first compression part can enter the second compression part and be discharged after being compressed again in the second compression part.
As shown in fig. 2, the motor further includes a stator 6, a rotating shaft, and a rotor 10.
The stator 6 is provided in the motor housing 1 and is fixed to the inner wall of the motor housing 1. The cooling channel comprises a first cooling section 71, the first cooling section 71 being located on the inner wall of the motor housing 1 and being located in correspondence with the stator 6, the opening of the first cooling section 71 being directed towards the stator 6. The first cooling section 71 is used for passing the refrigerant, so that the refrigerant can cool down the stator 6.
Alternatively, the first cooling section 71 is a spiral section that extends spirally in the axial direction of the stator 6. The helical 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 the present embodiment, a motor coolant inlet 81 communicating with the first cooling section 71 is provided at a position on the motor housing 1 corresponding to the stator 6 to introduce a refrigerant into the cooling passage.
The rotating shaft is rotatably arranged in the motor housing 1 and is connected with the motor housing 1 through a bearing assembly. The bearing assembly is used for supporting the rotating shaft, so that the rotating shaft can rotate.
The specific configuration of the bearing assembly may be determined as desired, for example, the bearing assembly including the mounting plate 11 and the bearing 15. Wherein, mounting panel 11 is used for installing and supporting bearing 15, and mounting panel 11 is fixed to be set up in 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 according to the stress condition. The bearing 15 can be a refrigerant lubrication bearing, a sliding bearing, a rolling bearing, a magnetic suspension bearing and the use of the refrigerant lubrication bearing, so that an oil-free environment is created for the whole compressor, and pollution and heat exchange cannot be caused when the gas of each part enters the main stream gas.
Alternatively, in the present embodiment, the bearing 15 is a refrigerant lubricated bearing, and a bearing cooling section 73 penetrating in the axial direction of the bearing 15 is provided thereon, the bearing cooling section 73 being for passing a refrigerant for cooling and lubrication. The cooling channel comprises the bearing cooling section 73.
The number of bearing cooling segments 73 may be plural as needed, and may be arranged at intervals in the circumferential direction of the bearing 15.
In this embodiment, there are two bearing assemblies and are arranged at intervals, with the stator 6 being located between the two bearing assemblies. The shaft passes through the two bearing assemblies.
The bearing cooling section 73 is arranged between the refrigerant lubrication bearings of the two bearing assemblies, and refrigerant gas can take away heat generated in the working process of the bearings through the part of channels, wherein the refrigerant lubrication bearings far away from the first compression part are main bearings of the compressor, namely: the bearing bears 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 part is a secondary bearing of the compressor and only bears the radial force of the rotor shaft system. Therefore, in terms of working principle, the main bearing generates a larger amount of heat than the secondary bearing.
Optionally, a bearing cooling fluid inlet 82 is provided on the motor housing 1 at a position corresponding to the bearing 15, which communicates with the bearing cooling section 73, for the entry of cooling refrigerant for the bearing.
Because the two bearing assemblies are located at two sides of the stator 6 in a one-to-one correspondence manner, and the heating value of one bearing is larger than that of the other bearing, the bearing cooling liquid inlet 82 is arranged corresponding to the bearing assembly far away from the first compression part, the bearing assembly far away from the first compression part is the main bearing, and the cooling effect can be ensured by the arrangement of the bearing cooling liquid inlet 82 corresponding to the bearing assembly.
The rotor 10 is disposed on the rotation shaft and rotates with the rotation 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 gap is the second cooling section 72 of the cooling channel.
The first diffuser 4 of the first compression part is connected to the motor housing 1, and the first housing 2 of the first compression part is connected to the motor housing 1. The first impeller 3 is located at a first end of the motor and is arranged within the first housing 2. Specifically, the first impeller 3 is connected to the rotation shaft and is rotatable with the rotation shaft. The first impeller 3 discharges the compressed gas into the volute of the first housing 2 through the gas outlet.
With reference to fig. 3, the motor air return port 5 is arranged on the first diffuser 4, so that the cooling air return of the motor is communicated with the air outlet of the first impeller 3, and directly enters the first compression part to cool the compressed air, thereby realizing the reutilization of low-temperature air cold energy in the motor, reducing exhaust noise, omitting the connection of an external motor air return pipeline, simplifying the system and reducing the cost, and further, the whole centrifugal compressor obtains higher cost performance.
The motor air return openings 5 on the first diffuser 4 may be arranged in a plurality of intervals along the circumferential direction of the first diffuser 4, for example, the plurality of motor air return openings 5 are sequentially arranged on a first circumference at intervals, wherein the center of the first circumference is located on the rotation axis of the motor.
Preferably, as shown in fig. 5, the motor air return ports 5 are uniformly arranged at intervals on the first circumference, and a third included angle gamma is formed by connecting the centers of two adjacent motor air return ports 5 with the center of the first circumference, and the value of the third included angle gamma ranges from 12 degrees to 30 degrees. Like this motor return air port 5 evenly spaced sets up to satisfy motor displacement demand and make the even air inlet of first compression portion simultaneously, and the quantity of motor return air port 5 can be according to the air input determination.
The value of the third included angle mainly considers the uniformity of the flow speed and mixing of the return air flow and the manufacturability of processing, and the smaller the angle is, the more the number of circumferential return air ports is, the easier the return air flow is mixed with the main air flow, but the larger the processing amount is, and vice versa.
Alternatively, as shown in fig. 3, 4 and 6, the motor return air port 5 extends obliquely, i.e. the center line of the motor return air port 5 forms an angle with the axis of the rotating shaft (i.e. the rotation axis of the motor). In other words, one end of the motor air return opening 5, which is close to the motor, is a first end, one end of the motor air return opening 5, which is close to the first compression part, is a second end, a connecting line between the first end of the motor air return opening 5 and the second end is a first connecting line, a first included angle alpha is formed between the first connecting line and a normal vertical surface (vertical surface perpendicular to the rotation axis) where the rotation axis of the motor is located, and on the normal vertical surface, the distance between the first end of the motor air return opening 5 and the rotation axis is smaller than the distance between the second end of the motor air return opening 5 and the rotation axis. Therefore, the air flow direction of the motor return air entering the first compression part is closer to the air outlet direction of the first impeller 3, the influence of the motor return air on the air outlet of the first impeller 3 is reduced, and the air flow fluctuation is reduced.
The first included angle alpha has a value ranging from 15 degrees to 35 degrees. The value of the first included angle alpha mainly considers the air flow mixing performance and the air return hole processing manufacturability. The smaller the angle, the less the return air interferes with the main air flow, the better the performance, but the poor the processing manufacturability and vice versa.
Optionally, in this embodiment, the first connection line of each motor air return opening 5 has a second included angle β with an axial vertical plane (a vertical plane parallel to the rotation axis) where the rotation axis of the motor is located, and on the axial vertical plane, a distance between the first end of the motor air return opening 5 and the rotation axis is smaller than a distance between the second end of the motor air return opening 5 and the rotation axis. This makes the spiral air intake structure of a plurality of motor return air ports 5, can adapt to the gas compression direction of spiral case more.
The value of the second included angle beta ranges from 55 degrees to 75 degrees. The value of the second included angle beta is mainly selected by taking the main airflow flowing angle into consideration, and the flowing angle of the return airflow and the flowing angle of the main airflow can be basically consistent in the angle range.
The communication between the motor air return port 5 and the air outlet of the first impeller 3 may be direct communication or indirect communication, for example, the motor air return port 5 is directly in communication with the volute of the first compression part. Moreover, the angles formed by the motor air return opening 5 and other reference lines or reference surfaces are set in such a way that the spiral direction of the air flow formed by the motor air return opening 5 (in the clockwise direction or the anticlockwise direction of the motor rotation) is always the same as the direction of the motor rotation.
As shown in fig. 2, the second compression portion includes a second casing 14, a second impeller 13 provided in the second casing 14, and a second diffuser 12 connected to the second casing 14. The second diffuser 12 is connected to the second end of the motor housing 1. The second housing 14 is connected to the second diffuser 12. The second impeller 13 is disposed within the second housing 14 and is connected to the second end of the shaft and rotates with the shaft. The gas discharged from the first compression part enters the second compression part for recompression so as to meet the compression requirement.
This two-stage or more's double-end sets up impeller oilless centrifugal compressor's motor return air structure fully plays the advantage of refrigerant lubrication bearing, and combine motor cooling temperature control state, place motor return air port 5 on the diffuser of preceding stage (first diffuser 4 in this embodiment) in, the main bearing (the bearing of keeping away from first diffuser 4) cooling gas mixes the back with motor cooling gas and passes through secondary bearing (the bearing of being close to first diffuser 4), fully mix with preceding stage compression portion main air current, realize preceding stage main stream gas density increase, the temperature reduces, effectively reduce the effect of air current noise, simultaneously, because air current temperature drops, next stage compression power consumption will reduce, thereby improve compressor efficiency. Meanwhile, an external connection loop of a motor is omitted, system leakage points are reduced, and the purpose of improving the cost performance of the compressor is achieved.
As shown in fig. 2. When the compressor works, the air compressed by the first compression part of the previous stage is discharged through the volute and then led to the air suction port of the second compression part of the next stage. Therefore, if the temperature of the gas of the previous stage can be reduced, microscopic molecular motion in the gas can be weakened, and compression power consumption of the next stage can be reduced after entering the next stage.
The motor return air structure combines motor cooling control, namely: the temperature of the gas after the motor is cooled is lower than that of the compressed gas of the previous stage, so that when the return gas of the motor is mixed with the main flow gas exhausted by the impeller of the previous stage, the temperature of the gas tends to be reduced, and the noise reduction effect is realized.
According to the measures and effects of cooling the motor commonly used in the prior art, the motor return air temperature is only 20 ℃, which is very beneficial to the efficient operation of the motor, so that the motor return air structure of the embodiment is completely feasible to implement according to the motor return air temperature level in the prior art.
According to another aspect of the present application, there is provided an air conditioner including a compressor, which is the above-mentioned compressor.
The compressor of the air conditioner is provided with a plurality of inclined channels (namely a motor return air port 5) on the diffuser of the first-stage compression part (namely a first diffuser 4 in the embodiment) and close to the outlet side of the first-stage impeller hub (namely the air outlet of the first impeller 3), so that motor return air is built-in, an external return air pipeline is reduced, and hidden danger points are reduced. The size of the channels is determined according to the motor air return quantity and the flow rate.
As shown in fig. 2, the cooling and return air process of the compressor is as follows:
the cooling passage of the motor comprises a plurality of parts such as a first cooling section 71, a second cooling section 72, a bearing cooling section 73, and connecting parts therebetween, etc. A spiral cooling channel is arranged between the stator and the motor housing 1, and the spiral cooling channel is the first cooling section 71. The air gap between the stator and the rotor is the second cooling section 72. The cooling and lubricating channel arranged on the refrigerant lubricating bearing is the bearing cooling section 73. The motor cooling liquid inlet 81 and the bearing cooling liquid inlet 82 are arranged on the motor shell 1 and are used for introducing refrigerant into the cooling channel. Wherein, motor coolant inlet 81 is located one side of stator, and bearing coolant inlet 82 is located the position that the motor casing corresponds the main bearing.
In operation, as shown in fig. 2, the refrigerant liquid entering from the motor coolant inlet 81 flows through the first cooling section 71 between the stator 6 and the motor housing 1 in a spiral manner, takes away heat from the stator 6, changes into gas, and then enters the right-hand end (right-hand end in fig. 2) chamber of the stator 6. After the refrigerant liquid entering from the bearing cooling liquid inlet 82 enters a channel formed by the mounting plate 11 of the main refrigerant lubrication bearing and the second diffuser 12, the refrigerant liquid passes through the bearing cooling section 73 on the main refrigerant lubrication bearing (the bearing far away from the motor return air port 5), and after the bearing heats, the refrigerant liquid becomes gas, and the gas enters a right end cavity of the stator 6 and is mixed with the gas after cooling the motor stator 6.
The mixed gas flows through the air gap between the stator 6 and the rotor 10 (namely, the second cooling section 72) from right to left (in fig. 2) to enter the left end (the left end in fig. 2) chamber of the stator, takes away the heat of the rotor 10, then enters the bearing cooling section 73 of the secondary refrigerant lubrication bearing (the bearing close to the motor air return port 5), takes away the heat of the secondary bearing, further enters the channel formed by the first diffuser 4 and the mounting plate 11 of the secondary refrigerant lubrication bearing, finally is mixed with the main air flow in the first compression part through the motor air return port 5 arranged in the first diffuser, reduces the temperature of the main air flow, and is introduced into the second compression part at the right end in fig. 2 through an external pipeline or other channels.
It should be noted that: on the hub outlet side of the second diffuser 12, which is close to the second impeller 13, there is no return air port as provided for the first diffuser 4, but rather a completely closed state.
In summary, for the above-mentioned double-end setting impeller oilless centrifugal compressor with more than two stages, this kind of built-in return air structure fully plays the advantage of refrigerant lubrication bearing to combine motor cooling temperature control state, through arranging motor return air port 5 on the diffuser of preceding stage in, main bearing cooling gas and motor cooling gas mix the back and pass through the secondary bearing, fully mix with preceding stage main air current, realize that preceding stage main air current density increases, and the temperature reduces, effectively reduces the air current noise, simultaneously, because air current temperature drops, next stage compression power consumption will reduce, thereby improve compressor efficiency. Meanwhile, an external connection loop of an external motor is omitted, system leakage points are reduced, and the purpose of improving the cost performance of the compressor is achieved.
The compressor and the air conditioner with the compressor have the following technical effects:
the problems of complex system and leakage caused by the additional addition of an external air return pipeline of a motor in the prior art are solved. The connection of an external motor return air pipeline is omitted, the cost is reduced, and the assembly efficiency and the cost performance of the compressor are improved.
The low-temperature gas cold energy recycling of the motor cavity is achieved, the comprehensive utilization rate is high, the low-temperature gas is mixed with the gas of the pneumatic flow channel, the gas flow density is increased, sound waves consume sound energy among high-density molecules, the gas flow noise is reduced, the gas inlet temperature of the lower-stage impeller is effectively reduced through the low-temperature gas mixed with the gas of the pneumatic flow channel, the compressor is reduced, and the compressor energy efficiency is improved.
The advantages of oilless centrifugal compressor and motor temperature control are utilized, and the motor return air loop is arranged in the oilless centrifugal compressor, so that the whole compressor and the external pipelines of the unit are concise, and the oilless centrifugal compressor can produce good effects in noise reduction, efficiency improvement, bearing cooling, system pipeline optimization, leakage point reduction and reliability improvement.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (15)
1. A compressor, comprising:
the motor comprises a motor shell (1) and a cooling channel arranged in the motor shell (1);
the first compression part is arranged at the first end of the motor and comprises a first shell (2) and a first diffuser (4) connected with the first shell (2), a motor air return port (5) is arranged on the first diffuser (4), and the cooling channel is communicated with the first compression part through the motor air return port (5);
the motor further comprises a stator (6), the stator (6) is arranged in the motor housing (1) and is fixedly connected with the motor housing (1), the cooling channel comprises a first cooling section (71), the first cooling section (71) is located on the inner wall of the motor housing (1) and is correspondingly arranged with the stator (6), an opening of the first cooling section (71) faces the stator (6), and the first cooling section (71) is a spiral section extending along the axial spiral of the stator (6).
2. The compressor of claim 1, wherein an end of the motor return air port (5) close to the motor is a first end, an end of the motor return air port (5) close to the first compression portion is a second end, a connecting line between the first end and the second end of the motor return air port (5) is a first connecting line, a first included angle is formed between the first connecting line and a normal vertical plane where a rotation axis of the motor is located, and on the normal vertical plane, a distance between the first end of the motor return air port (5) and the rotation axis is smaller than a distance between the second end of the motor return air port (5) and the rotation axis.
3. The compressor of claim 2, wherein the first included angle has a value in the range of 15 ° to 35 °.
4. The compressor of claim 2, wherein the first connection line has a second angle with an axial vertical plane in which the motor rotation axis is located, and wherein on the axial vertical plane a distance from the rotation axis of the first end of the motor return opening (5) is smaller than a distance from the rotation axis of the second end of the motor return opening (5).
5. The compressor of claim 4, wherein the second included angle has a value in the range of 55 ° to 75 °.
6. A compressor according to any one of claims 1-5, characterized in that the motor return openings (5) are a plurality and are arranged at successive intervals on a first circumference, the centre of which is located on the rotational axis of the motor.
7. The compressor of claim 6, wherein the motor air return openings (5) are uniformly arranged at intervals on the first circumference, and a third included angle is formed by connecting the centers of two adjacent motor air return openings (5) with the center of the first circumference, and the value of the third included angle ranges from 12 degrees to 30 degrees.
8. Compressor according to claim 1, characterized in that a motor coolant inlet (81) communicating with the first cooling section (71) is provided on the motor housing (1) at a position corresponding to the stator (6).
9. The compressor of claim 1, wherein the motor further comprises:
-a rotor (10), the rotor (10) being located within the stator (6), the cooling channel further comprising a second cooling section (72), the second cooling section (72) comprising a gap between the rotor (10) and the stator (6).
10. The compressor of claim 1, wherein the motor further comprises a bearing assembly comprising:
the bearing (15) is characterized in that the cooling channel further comprises a bearing cooling section (73) which is arranged on the bearing (15) and is used for cooling refrigerant to pass through.
11. Compressor according to claim 10, characterized in that a bearing cooling fluid inlet (82) communicating with the bearing cooling section (73) is provided on the motor housing (1) at a position corresponding to the bearing (15).
12. Compressor according to claim 10, wherein the number of bearing assemblies is two and arranged on both sides of the stator (6) in a one-to-one correspondence, the bearing cooling liquid inlets (82) being arranged in correspondence of the bearing assemblies remote from the first compression section.
13. The compressor according to claim 1, characterized in that the motor further comprises a stator (6), a rotor (10) and a bearing (15), the stator (6) being arranged in the motor housing (1) and being fixedly connected to the motor housing (1), the cooling channel comprising a first cooling section (71), the first cooling section (71) being located on an inner wall of the motor housing (1) and being arranged in a position corresponding to the stator (6), the opening of the first cooling section (71) being directed towards the stator (6); -the rotor (10) is located within the stator (6), the cooling channel further comprising a second cooling section (72), the second cooling section (72) comprising a gap between the rotor (10) and the stator (6); the cooling channel also comprises a bearing cooling section (73) which is arranged on the bearing (15) and is used for the cooling refrigerant to pass through;
the cooling medium is introduced into the motor, at least one part of the cooling medium sequentially passes through the first cooling section (71) and the second cooling section (72) and then flows out of the motor air return port (5), and at least one other part of the cooling medium sequentially passes through the bearing cooling section (73) on the bearing (15) far away from the motor air return port (5), the second cooling section (72) and the bearing cooling section (73) on the bearing (15) close to the motor air return port (5) and then flows out of the motor air return port (5).
14. The compressor of claim 1, further comprising a second compression portion disposed at a second end of the motor.
15. An air conditioner comprising a compressor as claimed in any one of claims 1 to 14.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710962857.5A CN107664143B (en) | 2017-10-16 | 2017-10-16 | Compressor and air conditioner with same |
| PCT/CN2017/119425 WO2019075921A1 (en) | 2017-10-16 | 2017-12-28 | Compressor and air conditioner having same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710962857.5A CN107664143B (en) | 2017-10-16 | 2017-10-16 | Compressor and air conditioner with same |
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| Publication Number | Publication Date |
|---|---|
| CN107664143A CN107664143A (en) | 2018-02-06 |
| CN107664143B true CN107664143B (en) | 2023-10-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710962857.5A Active CN107664143B (en) | 2017-10-16 | 2017-10-16 | Compressor and air conditioner with same |
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| Country | Link |
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| CN (1) | CN107664143B (en) |
| WO (1) | WO2019075921A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102545555B1 (en) * | 2018-06-12 | 2023-06-20 | 엘지전자 주식회사 | Centrifugal Compressor |
| KR102545557B1 (en) * | 2018-06-12 | 2023-06-21 | 엘지전자 주식회사 | Centrifugal Compressor |
| JP7204524B2 (en) | 2019-02-25 | 2023-01-16 | 三菱重工コンプレッサ株式会社 | compressor |
| CN111795072B (en) * | 2019-04-09 | 2022-01-25 | 青岛海尔智能技术研发有限公司 | Gas bearing gas supply device and motor |
| CN112780583B (en) * | 2021-02-04 | 2023-04-07 | 北京稳力科技有限公司 | Fuel cell stack and two-stage centrifugal compressor |
| CN112983848B (en) * | 2021-02-04 | 2023-02-10 | 北京稳力科技有限公司 | Fuel cell stack and gas supply device |
| CN113883069B (en) * | 2021-09-09 | 2024-01-12 | 鑫磊压缩机股份有限公司 | Multistage compressor adopting magnetic planetary rotor shafting to accelerate |
| CN115405536A (en) * | 2022-10-31 | 2022-11-29 | 季华实验室 | Magnetic suspension double-suction centrifugal compressor |
| CN117006073A (en) * | 2023-08-22 | 2023-11-07 | 苏州氢启新能源科技有限公司 | Self-pressurizing cooling hydrogen fuel cell air compressor |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2019075921A1 (en) | 2019-04-25 |
| CN107664143A (en) | 2018-02-06 |
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