CN107588005B - Compressor, compressor parallel system and multi-split heat exchange system - Google Patents
Compressor, compressor parallel system and multi-split heat exchange system Download PDFInfo
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- CN107588005B CN107588005B CN201710800302.0A CN201710800302A CN107588005B CN 107588005 B CN107588005 B CN 107588005B CN 201710800302 A CN201710800302 A CN 201710800302A CN 107588005 B CN107588005 B CN 107588005B
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Abstract
The application provides a compressor, a compressor parallel system and a multi-split heat exchange system. Wherein, the compressor includes the casing and sets up the bent axle in the casing, and the compressor still includes: the first magnetic suspension bearing is arranged in the shell; the second magnetic suspension bearing is arranged in the shell, and the first magnetic suspension bearing and the second magnetic suspension bearing are respectively arranged at two ends of the crankshaft. The application effectively solves the problems of easy abrasion and easy noise generation of the crankshaft when the compressor runs at high speed in the prior art.
Description
Technical Field
The application relates to the technical field of compressors, in particular to a compressor, a compressor parallel system and a multi-split heat exchange system.
Background
In the prior art, the crankshaft of the compressor is connected to the housing by conventional bearings. Therefore, in the operation process of the compressor, mechanical abrasion occurs between the crankshaft and the conventional bearing, which not only affects the working efficiency of the compressor and shortens the service life of the crankshaft or the conventional bearing, reduces the working reliability of the compressor, but also causes noise or vibration in the operation process of the compressor, and causes poor user experience.
Disclosure of Invention
The application mainly aims to provide a compressor, a compressor parallel system and a multi-split heat exchange system, which are used for solving the problems that a crankshaft is easy to wear and noise are easy to generate when the compressor runs at a high speed in the prior art.
In order to achieve the above object, according to one aspect of the present application, there is provided a compressor including a housing and a crankshaft disposed in the housing, the compressor further comprising: the first magnetic suspension bearing is arranged in the shell; the second magnetic suspension bearing is arranged in the shell, and the first magnetic suspension bearing and the second magnetic suspension bearing are respectively arranged at two ends of the crankshaft.
Further, the compressor further includes: and the crankshaft is arranged on the third magnetic suspension bearing, and the third magnetic suspension bearing is positioned between the first magnetic suspension bearing and the second magnetic suspension bearing.
Further, the compressor further includes: the upper bracket is arranged in the shell and sleeved outside the crankshaft, the upper bracket is provided with a first bearing mounting hole, and the first magnetic suspension bearing is arranged at the first bearing mounting hole.
Further, the first magnetic suspension bearing comprises a first magnetic suspension rotor and a first magnetic suspension stator sleeved outside the first magnetic suspension rotor, a gap L is reserved between the first magnetic suspension stator and the first magnetic suspension rotor, the first magnetic suspension rotor is sleeved on the crankshaft, and the first magnetic suspension stator is installed at the first bearing installation hole.
Further, the compressor further includes: the lower bracket is arranged in the shell and sleeved outside the crankshaft, and comprises a lower bracket main body and a second bearing mounting hole arranged on the end face of the lower bracket main body, and the second magnetic suspension bearing is arranged at the second bearing mounting hole.
Further, the second magnetic suspension bearing comprises a second magnetic suspension rotor and a second magnetic suspension stator, a gap L is reserved between the second magnetic suspension rotor and the second magnetic suspension stator, the second magnetic suspension rotor is sleeved on the crankshaft, the second magnetic suspension stator is installed at the second bearing installation hole, and the second magnetic suspension stator is arranged in the movement direction of the second magnetic suspension rotor.
Further, the compressor further includes: the end cover is connected with the lower support body, the second magnetic suspension bearing is arranged between the end cover and the lower support body, and the end faces of the second magnetic suspension rotor and the second magnetic suspension stator, which are close to the end cover, are flush and have a preset distance with the end cover.
Further, the lower bracket is also provided with a third bearing mounting hole, and the third magnetic suspension bearing is arranged at the third bearing mounting hole.
Further, the third magnetic suspension bearing comprises a third magnetic suspension rotor and a third magnetic suspension stator sleeved outside the third magnetic suspension rotor, a gap L is reserved between the third magnetic suspension stator and the third magnetic suspension rotor, the third magnetic suspension rotor is sleeved on the crankshaft, and the third magnetic suspension stator is installed at the third bearing installation hole.
Further, the gap L is less than 0.6mm.
Further, the compressor further includes: the air suction pipe is communicated with the shell, the air suction pipe is arranged on one side, close to the neck of the crankshaft, of the first magnetic suspension bearing, and the second magnetic suspension bearing is arranged at the tail of the crankshaft.
Further, the compressor further includes: and the bearing structure is arranged on the crankshaft and is positioned between the first magnetic suspension bearing and the second magnetic suspension bearing.
According to another aspect of the present application, there is provided a compressor parallel system including: the gas-liquid separator comprises a first gas outlet and a first gas inlet; a plurality of filters; the compressors are all the compressors, the second air inlets of the compressors are all communicated with the first air outlets of the gas-liquid separators through the filters, and the second air outlets of the compressors are all communicated with the first air inlets of the gas-liquid separators.
According to another aspect of the present application, there is provided a multi-split heat exchange system, including the above-mentioned compressor parallel system, the gas-liquid separator of the compressor parallel system further includes a third gas outlet and a third gas inlet, the third gas inlet is communicated with the first gas outlet, and the multi-split heat exchange system further includes: the condenser, when the multi-split heat exchange system carries on refrigeration, the inlet end of the condenser is linked with the second air outlet of each compressor in the parallel system of compressors, the outlet end of the condenser is linked with the first air inlet of the gas-liquid separator; and when the multi-split heat exchange system performs refrigeration, the inlet end of the evaporator is communicated with the third air outlet of the gas-liquid separator, and the outlet end of the evaporator is communicated with the third air inlet of the gas-liquid separator.
By applying the technical scheme of the application, in the running process of the compressor, the first magnetic suspension bearing and the second magnetic suspension bearing play a role in supporting and positioning the crankshaft, and the radial and axial movement of the crankshaft relative to the shell in the rotating process is prevented. Therefore, the first magnetic suspension bearing and the second magnetic suspension bearing support and position the crankshaft in the shell, so that mechanical abrasion (such as mechanical abrasion of the crankshaft) of the compressor in the high-speed operation process is reduced, the compressor is ensured to have higher reliability when the crankshaft is operated at a high speed, and further the high-frequency energy efficiency of the compressor is improved. Meanwhile, the compressor reduces energy loss, improves the working efficiency of the compressor and prolongs the service life.
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 shows a cross-sectional view of an embodiment one of a compressor according to the present application;
FIG. 2 shows an enlarged schematic view at A of the compressor of FIG. 1;
FIG. 3 shows an enlarged schematic view of the compressor of FIG. 1 at B;
FIG. 4 shows an enlarged schematic view of the compressor of FIG. 1 at C;
fig. 5 shows a cross-sectional view of a second embodiment of a compressor according to the present application;
FIG. 6 shows a schematic diagram of the compressor of the present application applied to a compressor parallel system; and
fig. 7 shows a schematic diagram of the compressor applied to the multi-split heat exchange system.
Wherein the above figures include the following reference numerals:
10. a housing; 20. a crankshaft; 30. a first magnetic suspension bearing; 31. a first magnetic levitation rotor; 32. a first magnetic levitation stator; 40. a second magnetic suspension bearing; 41. a second magnetic levitation rotor; 42. a second magnetic levitation stator; 50. a third magnetic suspension bearing; 51. a third magnetic levitation rotor; 52. a third magnetic levitation stator; 60. an upper bracket; 61. a first bearing mounting hole; 70. a lower bracket; 71. a second bearing mounting hole; 72. a third bearing mounting hole; 73. a lower bracket main body; 80. an air suction pipe; 90. an end cap; 100. a bearing structure; 110. a gas-liquid separator; 111. a first air outlet; 112. a first air inlet; 113. a third air outlet; 114. a third air inlet; 120. a filter; 130. a compressor; 131. a second air inlet; 132. a second air outlet; 140. a condenser; 141. an inlet end; 142. an outlet end; 150. an evaporator; 151. an entry end; 152. a discharge end; 160. a fixed scroll; 170. an orbiting scroll; 180. a reservoir; 190. a four-way valve; 200. and a motor.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
It is noted that all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs unless otherwise indicated.
In the present application, unless otherwise indicated, terms of orientation such as "upper" and "lower" are used generally with respect to the orientation shown in the drawings or to the vertical, vertical or gravitational orientation; also, for ease of understanding and description, "left, right" is generally directed to the left, right as shown in the drawings; "inner and outer" refer to inner and outer relative to the outline of the components themselves, but the above-described orientation terms are not intended to limit the present application.
As shown in fig. 1 to 7, the application provides a compressor, a parallel system of compressors and a multi-split heat exchange system.
Example 1
As shown in fig. 1, the compressor of the first embodiment includes a housing 10 and a crankshaft 20 disposed in the housing 10, and further includes a first magnetic bearing 30 and a second magnetic bearing 40. Wherein a first magnetic bearing 30 is arranged within the housing 10. The second magnetic bearing 40 is disposed in the housing 10, and the first magnetic bearing 30 and the second magnetic bearing 40 are disposed at two ends of the crankshaft 20, respectively.
During the operation of the compressor, the first magnetic suspension bearing 30 and the second magnetic suspension bearing 40 play a role in supporting and positioning the crankshaft 20, and prevent the radial and axial movement of the crankshaft 20 relative to the housing 10 during the rotation process. In this way, the first magnetic suspension bearing 30 and the second magnetic suspension bearing 40 support and position the crankshaft 20 in the housing, so that mechanical abrasion (such as mechanical abrasion of the crankshaft 20) in the high-speed operation process of the compressor is reduced, higher reliability of the compressor is ensured when the crankshaft 20 operates at high speed, and further high-frequency energy efficiency of the compressor is improved. Meanwhile, the compressor reduces energy loss, improves the working efficiency of the compressor and prolongs the service life.
As shown in fig. 1, the compressor further includes a third magnetic bearing 50. Wherein the crankshaft 20 is disposed on a third magnetic bearing 50, and the third magnetic bearing 50 is located between the first magnetic bearing 30 and the second magnetic bearing 40. In this way, the crankshaft 20 is supported and positioned by the first magnetic suspension bearing 30, the second magnetic suspension bearing 40 and the third magnetic suspension bearing 50, so that not only can the crankshaft 20 be fully ensured not to be displaced or moved in the radial and axial directions in the rotation process, but also the crankshaft 20 can be ensured not to mechanically rub with the supporting structure (three magnetic suspension bearings) in the rotation process, thereby reducing energy loss, improving the working efficiency of the compressor and prolonging the service life of the crankshaft 20. In addition, the first magnetic bearing 30, the second magnetic bearing 40 and the third magnetic bearing 50 do not need to be lubricated by a compressor design oil path, so that the oil separation system structural design of the compressor is omitted, and the structure of the compressor is simplified.
As shown in fig. 1 and 4, the compressor further includes an upper bracket 60. Wherein, the upper bracket 60 is disposed in the housing 10 and sleeved outside the crankshaft 20, the upper bracket 60 has a first bearing mounting hole 61, and the first magnetic suspension bearing 30 is mounted at the first bearing mounting hole 61. Thus, the crankshaft 20 is supported and positioned by the first magnetic bearing 30, and the first magnetic bearing 30 is mounted on the upper bracket 60, the crankshaft 20 is mounted in the housing 10 by the upper bracket 60. The above arrangement makes the structural layout in the housing 10 of the compressor more reasonable and compact, and makes the installation and positioning of the crankshaft 20 simpler and easier.
As shown in fig. 1 and 4, the first magnetic suspension bearing 30 includes a first magnetic suspension rotor 31 and a first magnetic suspension stator 32 sleeved outside the first magnetic suspension rotor 31, a gap L is provided between the first magnetic suspension stator 32 and the first magnetic suspension rotor 31, the first magnetic suspension rotor 31 is sleeved on the crankshaft 20, and the first magnetic suspension stator 32 is installed at the first bearing installation hole 61. The arrangement ensures that the first magnetic suspension bearing 30 operates normally, and further plays a role in radial positioning of the crankshaft 20.
Specifically, the first magnetic levitation rotor 31 is interference-fitted with the crankshaft 20 to ensure that the first magnetic levitation rotor 31 rotates together with the crankshaft 20, and the first magnetic levitation stator 32 is interference-mounted on the upper bracket 60. In this way, the clearance L does not change during the smooth running of the crankshaft 20, thereby achieving the purpose of not generating mechanical friction loss and power consumption when the crankshaft 20 rotates at a high speed. In addition, the above arrangement can reduce the difficulty of assembling the whole compressor, that is, the coaxiality of the left and right ends of the crankshaft 20 is ensured when the whole compressor is assembled.
As shown in fig. 1 and 2, the compressor further includes a lower bracket 70. Wherein, the lower bracket 70 is disposed inside the housing 10 and sleeved outside the crankshaft 20, the lower bracket 70 includes a lower bracket body 73 and a second bearing mounting hole 71 disposed on an end surface of the lower bracket body 73, and the second magnetic suspension bearing 40 is mounted at the second bearing mounting hole 71. In this way, the crankshaft 20 is supported and positioned by the second magnetic bearing 40, and the second magnetic bearing 40 is mounted on the lower bracket 70, and the crankshaft 20 is mounted in the housing 10 by the upper bracket 60 and the lower bracket 70. The above arrangement makes the structural layout in the housing 10 of the compressor more reasonable and compact, and makes the installation and positioning of the crankshaft 20 simpler and easier.
As shown in fig. 1 and 2, the second magnetic bearing 40 includes a second magnetic levitation rotor 41 and a second magnetic levitation stator 42, a gap L is provided between the second magnetic levitation rotor 41 and the second magnetic levitation stator 42, the second magnetic levitation rotor 41 is sleeved on the crankshaft 20, the second magnetic levitation stator 42 is mounted at the second bearing mounting hole 71, and the second magnetic levitation stator 42 is disposed in the movement direction of the second magnetic levitation rotor 41. The structure is simple and easy to process.
Specifically, the second magnetic levitation rotor 41 is interference-fitted with the crankshaft 20 to ensure that the second magnetic levitation rotor 41 rotates together with the crankshaft 20, and the second magnetic levitation stator 42 is interference-mounted on the lower bracket 70. During the rotation of the crankshaft 20, the second magnetic suspension stator 42 can play a role in shielding and positioning the second magnetic suspension rotor 41, prevent the second magnetic suspension rotor 41 from shifting in the axial direction, further prevent the crankshaft 20 from shifting in the axial direction, and play a role in positioning the crankshaft 20 in the axial direction.
As shown in fig. 2, the compressor further includes an end cover 90. Wherein the end cover 90 is connected to the lower bracket body 73, the second magnetic bearing 40 is disposed between the end cover 90 and the lower bracket body 73, and the second magnetic levitation rotor 41 is spaced apart from the end cover 90 by a predetermined distance. In this way, the above arrangement can further prevent the movement of the crankshaft 20 in the axial direction, and perform a better positioning function for the crankshaft 20. Meanwhile, the arrangement of the preset distance can ensure that the second magnetic suspension rotor 41 cannot interfere with the movement of the end cover 90 in the movement process of the crankshaft 20, and the reliability of the internal structure of the compressor is improved.
As shown in fig. 3, the lower bracket 70 further has a third bearing mounting hole 72, and the third magnetic bearing 50 is mounted at the third bearing mounting hole 72. The structure is simple and easy to assemble.
As shown in fig. 3, the third magnetic bearing 50 includes a third magnetic suspension rotor 51 and a third magnetic suspension stator 52 sleeved outside the third magnetic suspension rotor 51, a gap L is provided between the third magnetic suspension stator 52 and the third magnetic suspension rotor 51, the third magnetic suspension rotor 51 is sleeved on the crankshaft 20, and the third magnetic suspension stator 52 is mounted at the third bearing mounting hole 72. The above arrangement can ensure the normal operation of the third magnetic suspension bearing 50, thereby playing a role in radial positioning of the crankshaft 20.
Specifically, the third magnetic levitation rotor 51 is interference-fitted with the crankshaft 20 to ensure that the third magnetic levitation rotor 51 rotates with the crankshaft 20, and the third magnetic levitation stator 52 is interference-mounted on the upper bracket 60. When the compressor is in an initial state or the rotation speed of the crankshaft 20 is low, the gap L between the first magnetic suspension stator 32 and the first magnetic suspension rotor 31 is unchanged, the gap L between the third magnetic suspension stator 52 and the third magnetic suspension rotor 51 is unchanged, and the crankshaft 20 is at an initial position, and at the moment, the control current in the compressor is zero. When the crankshaft 20 is shifted to the initial position due to external disturbance or high-speed rotation, the gap L between the first magnetic levitation stator 32 and the first magnetic levitation rotor 31 or the gap L between the third magnetic levitation stator 52 and the third magnetic levitation rotor 51 is changed, and the displacement sensor transmits the change to the controller, and the controller adjusts the current values on the first magnetic levitation stator 32 and the third magnetic levitation stator 52 through the power amplifier, so that the stator current on the side of the gap increase is increased, the stator current on the side of the gap decrease is decreased, thereby generating a larger electromagnetic force on the stator with the increased current, and the gap L is restored to the initial value, thereby returning the crankshaft 20 to the initial equilibrium position.
In the compressor of the first embodiment, the clearance L is less than 0.6mm. The above numerical range can ensure the normal use of the first magnetic bearing 30, the second magnetic bearing 40 and the third magnetic bearing 50, and further has supporting and positioning effects on the crankshaft 20.
As shown in fig. 1, the compressor further includes a suction pipe 80. Wherein, the air suction pipe 80 is communicated with the shell 10, the air suction pipe 80 is arranged at one side close to the neck of the crankshaft 20, the first magnetic suspension bearing 30 is arranged at the neck, and the second magnetic suspension bearing 40 is arranged at the tail of the crankshaft 20. Thus, magnetic bearings are provided at the neck, tail and middle of the crankshaft 20 of the compressor. The first magnetic suspension bearing 30 and the third magnetic suspension bearing 50 respectively positioned at the neck and the middle are used for supporting and positioning the crankshaft 20 in the radial direction, so as to prevent the crankshaft 20 from moving in the radial direction, and the second magnetic suspension bearing 40 positioned at the tail is used for supporting and positioning the crankshaft 20 in the axial direction, so that the axial movement of the crankshaft 20 in the running process is prevented from influencing the normal use of the compressor. And further, the stress of the crankshaft 20 is more uniform, and the structural strength of the crankshaft 20 is improved.
As shown in fig. 1, the compressor further includes a fixed scroll 160, an orbiting scroll 170, and a motor 200. Wherein, the fixed scroll 160 and the movable scroll 170 are engaged with each other, and the crankshaft 20 is fixed to the rotor of the motor 200. During the operation of the compressor, the crankshaft 20 is rotated by the motor 200, and the crankshaft 20 drives the movable scroll 170 to rotate, the fixed scroll 160 engaged with the movable scroll 170 compresses the low-temperature and low-pressure refrigerant gas sucked by the suction pipe 80 into high-temperature and high-pressure refrigerant gas, and then the refrigerant gas is discharged into the casing 10 of the compressor through the gas outlet at the center of the fixed scroll 160, and the refrigerant gas is discharged from the gas outlet pipe of the casing 10 to the outside of the compressor after passing through the stator of the motor 200.
As shown in fig. 6, the present application also provides a parallel compressor system including a gas-liquid separator 110, a plurality of filters 120, and a plurality of compressors 130. Wherein the gas-liquid separator 110 includes a first gas outlet 111 and a first gas inlet 112. Each compressor 130 is the above-mentioned compressor, the second air inlet 131 of each compressor 130 is communicated with the first air outlet 111 of the gas-liquid separator 110 via the filter 120, and the second air outlet 132 of each compressor 130 is communicated with the first air inlet 112 of the gas-liquid separator 110. Compared with the prior art, the compressor parallel system has no traditional shafting lubricating structure design, the system oil component structure design can be omitted, the oil return function and logic control are reduced, and the failure rate of the compressor parallel system due to system oil return or compressor oil balancing failure is further reduced.
Optionally, the compressor parallel system further comprises a valve structure. As shown in fig. 6, in the compressor parallel system of the first embodiment, the valve structure is a four-way valve 190. The refrigerant gas discharged from the second gas outlet 132 of the compressor 130 enters the gas-liquid separator 110 after passing through the four-way valve 190, and the low-temperature low-pressure refrigerant gas discharged from the first gas outlet 111 of the gas-liquid separator 110 enters the second gas inlet 131 of the compressor 130 after passing through the four-way valve 190, and is discharged from the second gas outlet 132 again after being compressed in the compressor 130, and the cycle is continuously performed. Thus, the four-way valve 190 can ensure the correct flow of the refrigerant gas and ensure the normal operation of the parallel system of the compressor.
It should be noted that the type of the valve structure is not limited thereto. Optionally, the valve structure is a two-way valve or a three-way valve, so long as the correct flow direction of the refrigerant gas can be ensured.
As shown in fig. 7, the present application further provides a multi-split heat exchange system, which includes the above-mentioned compressor parallel system, the gas-liquid separator 110 of the compressor parallel system further includes a third gas outlet 113 and a third gas inlet 114, the third gas inlet 114 is communicated with the first gas outlet 111, and the multi-split heat exchange system further includes a condenser 140, an evaporator 150 and a liquid reservoir 180. When the multi-split heat exchange system performs refrigeration, the inlet end 141 of the condenser 140 is communicated with the second air outlet 132 of each compressor 130 in the parallel system of compressors, and the outlet end 142 of the condenser 140 is communicated with the first air inlet 112 of the gas-liquid separator 110. Meanwhile, the third gas outlet 113 of the gas-liquid separator 110 is connected to the inlet end 151 of the evaporator 150 via the accumulator 180, and the outlet end 152 of the evaporator 150 is connected to the third gas inlet 114 of the gas-liquid separator 110. Therefore, the multi-split heat exchange system adopting the compressor parallel system can reduce the oil return structure design of the system, simplify the structure design of the system, and further reduce the faults of the system caused by oil return or oil equalization failure of the compressors.
Example two
The compressor of the second embodiment differs from that of the first embodiment in that: the compressors are different in structure.
As shown in fig. 5, in the present embodiment, the compressor further includes a bearing structure 100. Wherein the bearing structure 100 is disposed on the crankshaft 20, the bearing structure 100 being located between the first magnetic bearing 30 and the second magnetic bearing 40. Thus, during normal operation of the compressor, the first magnetic suspension bearing 30 and the bearing structure 100 play a role in radial positioning of the crankshaft 20, and the second magnetic suspension bearing 40 plays a role in axial positioning of the crankshaft 20, so that displacement or movement of the crankshaft 20 in radial and axial directions is not generated during rotation.
From the above description, it can be seen that the above embodiments of the present application achieve the following technical effects:
in the operation process of the compressor, the first magnetic suspension bearing and the second magnetic suspension bearing play a role in supporting and positioning the crankshaft, and the radial and axial movement of the crankshaft relative to the shell in the rotation process is prevented. Therefore, the first magnetic suspension bearing and the second magnetic suspension bearing support and position the crankshaft in the shell, so that mechanical abrasion (such as mechanical abrasion of the crankshaft) of the compressor in the high-speed operation process is reduced, the compressor is ensured to have higher reliability when the crankshaft is operated at a high speed, and further the high-frequency energy efficiency of the compressor is improved. Meanwhile, the compressor reduces energy loss, improves the working efficiency of the compressor and prolongs the service life.
It will be apparent that the embodiments described above are merely some, but not all, embodiments of the application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present application without making any inventive effort, shall fall within the scope of the present application.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein.
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 (12)
1. A compressor comprising a housing (10) and a crankshaft (20) arranged in the housing (10), characterized in that the compressor further comprises:
a first magnetic suspension bearing (30) disposed within the housing (10);
the second magnetic suspension bearing (40) is arranged in the shell (10), and the first magnetic suspension bearing (30) and the second magnetic suspension bearing (40) are respectively arranged at two ends of the crankshaft (20);
the upper bracket (60) is arranged in the shell (10) and sleeved outside the crankshaft (20), the upper bracket (60) is provided with a first bearing mounting hole (61), and the first magnetic suspension bearing (30) is mounted at the first bearing mounting hole (61);
a third magnetic bearing (50), the crankshaft (20) is arranged on the third magnetic bearing (50), and the third magnetic bearing (50) is positioned between the first magnetic bearing (30) and the second magnetic bearing (40);
the first magnetic suspension bearing (30), the second magnetic suspension bearing (40) and the third magnetic suspension bearing (50) do not need the designed oil way of the compressor to lubricate the compressor.
2. The compressor of claim 1, wherein the first magnetic suspension bearing (30) comprises a first magnetic suspension rotor (31) and a first magnetic suspension stator (32) sleeved outside the first magnetic suspension rotor (31), a gap L is formed between the first magnetic suspension stator (32) and the first magnetic suspension rotor (31), the first magnetic suspension rotor (31) is sleeved on the crankshaft (20), and the first magnetic suspension stator (32) is installed at the first bearing installation hole (61).
3. The compressor of claim 1, further comprising:
the lower support (70) is arranged in the shell (10) and sleeved outside the crankshaft (20), the lower support (70) comprises a lower support body (73) and a second bearing mounting hole (71) arranged on the end face of the lower support body (73), and the second magnetic suspension bearing (40) is mounted at the second bearing mounting hole (71).
4. A compressor according to claim 3, wherein the second magnetic suspension bearing (40) comprises a second magnetic suspension rotor (41) and a second magnetic suspension stator (42), a gap L is provided between the second magnetic suspension rotor (41) and the second magnetic suspension stator (42), the second magnetic suspension rotor (41) is sleeved on the crankshaft (20), the second magnetic suspension stator (42) is mounted at the second bearing mounting hole (71), and the second magnetic suspension stator (42) is arranged in the movement direction of the second magnetic suspension rotor (41).
5. The compressor of claim 4, further comprising:
the end cover (90) is connected with the lower support main body (73), the second magnetic suspension bearing (40) is arranged between the end cover (90) and the lower support main body (73), and the second magnetic suspension rotor (41) and the second magnetic suspension stator (42) are close to the end face parallel and level of the end cover (90) and have a preset distance with the end cover (90).
6. A compressor according to claim 3, wherein the lower bracket (70) further has a third bearing mounting hole (72), the third magnetic bearing (50) being mounted at the third bearing mounting hole (72).
7. The compressor of claim 6, wherein the third magnetic suspension bearing (50) includes a third magnetic suspension rotor (51) and a third magnetic suspension stator (52) sleeved outside the third magnetic suspension rotor (51), a gap L is provided between the third magnetic suspension stator (52) and the third magnetic suspension rotor (51), the third magnetic suspension rotor (51) is sleeved on the crankshaft (20), and the third magnetic suspension stator (52) is mounted at the third bearing mounting hole (72).
8. The compressor of claim 2 or 4 or 7, wherein the gap L is less than 0.6mm.
9. The compressor of claim 1, further comprising:
the air suction pipe (80) is communicated with the shell (10), the air suction pipe (80) is arranged on one side close to the neck of the crankshaft (20), the first magnetic suspension bearing (30) is arranged on the neck, and the second magnetic suspension bearing (40) is arranged at the tail of the crankshaft (20).
10. The compressor of claim 1, further comprising:
and a bearing structure (100) disposed on the crankshaft (20), the bearing structure (100) being located between the first magnetic bearing (30) and the second magnetic bearing (40).
11. A compressor parallel system, the compressor parallel system comprising:
a gas-liquid separator (110) comprising a first gas outlet (111) and a first gas inlet (112);
a plurality of filters (120);
-a plurality of compressors (130), each of the compressors (130) being a compressor according to any of claims 1 to 10, the second air inlet (131) of each of the compressors (130) being in communication with the first air outlet (111) of the gas-liquid separator (110) via the filter (120), the second air outlet (132) of each of the compressors (130) being in communication with the first air inlet (112) of the gas-liquid separator (110).
12. A multi-split heat exchange system, comprising the compressor parallel system of claim 11, wherein the gas-liquid separator (110) of the compressor parallel system further comprises a third gas outlet (113) and a third gas inlet (114), and the third gas inlet (114) is communicated with the first gas outlet (111), and further comprising:
the condenser (140), when the multi-split heat exchange system heats, the inlet end (141) of the condenser (140) is communicated with the second air outlet (132) of each compressor (130) in the compressor parallel system, and the outlet end (142) of the condenser (140) is communicated with the first air inlet (112) of the gas-liquid separator (110);
and when the multi-split heat exchange system heats, the inlet end (151) of the evaporator (150) is communicated with the third air outlet (113) of the gas-liquid separator (110), and the outlet end (152) of the evaporator (150) is communicated with the third air inlet (114) of the gas-liquid separator (110).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710800302.0A CN107588005B (en) | 2017-09-06 | 2017-09-06 | Compressor, compressor parallel system and multi-split heat exchange system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710800302.0A CN107588005B (en) | 2017-09-06 | 2017-09-06 | Compressor, compressor parallel system and multi-split heat exchange system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107588005A CN107588005A (en) | 2018-01-16 |
| CN107588005B true CN107588005B (en) | 2023-08-25 |
Family
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| CN109668354B (en) * | 2019-02-12 | 2023-07-25 | 珠海格力电器股份有限公司 | Refrigerant circulation system for preventing abrasion of gas bearing for compressor and control method thereof |
| CN110242535A (en) * | 2019-07-09 | 2019-09-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and heat exchange equipment |
| CN113417884B (en) * | 2021-05-28 | 2022-04-12 | 海拓宾未来工业集团有限公司 | Pure oilless air suspension compressor based on horizontal axis magnetic suspension |
| CN115076211B (en) * | 2022-07-28 | 2023-08-18 | 潍柴动力股份有限公司 | Crankshaft system and control method |
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| CN1945940A (en) * | 2006-07-18 | 2007-04-11 | 沈阳工业大学 | Integrated permanent magnet rotor magnetic suspension high speed motor |
| CN101126395A (en) * | 2007-09-07 | 2008-02-20 | 苏州昆拓冷机有限公司 | Magnetic levitation axial flow compressor |
| CN203722518U (en) * | 2012-12-26 | 2014-07-16 | Skf磁性机械技术公司 | Hybrid magnetic suspension of a rotor |
| CN106468268A (en) * | 2015-08-17 | 2017-03-01 | 财团法人工业技术研究院 | Magnetic suspension rotor mechanism |
| CN207195195U (en) * | 2017-09-06 | 2018-04-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, compressor parallel system and multi-connected machine heat-exchange system |
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| CN1945940A (en) * | 2006-07-18 | 2007-04-11 | 沈阳工业大学 | Integrated permanent magnet rotor magnetic suspension high speed motor |
| CN101126395A (en) * | 2007-09-07 | 2008-02-20 | 苏州昆拓冷机有限公司 | Magnetic levitation axial flow compressor |
| CN203722518U (en) * | 2012-12-26 | 2014-07-16 | Skf磁性机械技术公司 | Hybrid magnetic suspension of a rotor |
| CN106468268A (en) * | 2015-08-17 | 2017-03-01 | 财团法人工业技术研究院 | Magnetic suspension rotor mechanism |
| CN207195195U (en) * | 2017-09-06 | 2018-04-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, compressor parallel system and multi-connected machine heat-exchange system |
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