CN222315375U - Rotary compressor and refrigeration equipment - Google Patents
Rotary compressor and refrigeration equipment Download PDFInfo
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- CN222315375U CN222315375U CN202421218686.7U CN202421218686U CN222315375U CN 222315375 U CN222315375 U CN 222315375U CN 202421218686 U CN202421218686 U CN 202421218686U CN 222315375 U CN222315375 U CN 222315375U
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- crankshaft
- bracket
- rotary compressor
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 20
- 238000003756 stirring Methods 0.000 claims abstract description 52
- 238000000926 separation method Methods 0.000 claims abstract description 38
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 16
- 239000007788 liquid Substances 0.000 abstract description 21
- 230000000694 effects Effects 0.000 abstract description 17
- 239000003921 oil Substances 0.000 description 103
- 239000003507 refrigerant Substances 0.000 description 44
- 239000000203 mixture Substances 0.000 description 17
- 239000010726 refrigerant oil Substances 0.000 description 11
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 230000017525 heat dissipation Effects 0.000 description 7
- 230000002093 peripheral effect Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 6
- 238000005461 lubrication Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- 239000011324 bead Substances 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
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Abstract
本实用新型公开了旋转式压缩机及制冷设备，涉及压缩机技术领域，旋转式压缩机包括壳体和设于壳体内腔的电机组件、曲轴、支撑组件和油气分离件，电机组件包括定子和转子，定子和壳体连接，转子与曲轴固定连接，曲轴向上凸出转子，支撑组件位于电机组件的上方，支撑组件包括支架和电机轴承，支架和壳体固定连接，电机轴承安装于支架，油气分离件固定安装于转子，油气分离件的搅动板围绕曲轴布置，并朝支架延伸设置。本实用新型的旋转式压缩机能够增强油气分离效果，减少吐油量，使油池的液面稳定。
The utility model discloses a rotary compressor and a refrigeration device, and relates to the technical field of compressors. The rotary compressor includes a housing and a motor assembly, a crankshaft, a support assembly, and an oil-gas separator arranged in the inner cavity of the housing. The motor assembly includes a stator and a rotor, the stator is connected to the housing, the rotor is fixedly connected to the crankshaft, the crankshaft protrudes upward from the rotor, the support assembly is located above the motor assembly, the support assembly includes a bracket and a motor bearing, the bracket is fixedly connected to the housing, the motor bearing is installed on the bracket, the oil-gas separator is fixedly installed on the rotor, and the stirring plate of the oil-gas separator is arranged around the crankshaft and extends toward the bracket. The rotary compressor of the utility model can enhance the oil-gas separation effect, reduce the amount of oil discharge, and stabilize the liquid level of the oil pool.
Description
Technical Field
The utility model relates to the technical field of compressors, in particular to a rotary compressor and refrigeration equipment.
Background
The refrigerating oil provides necessary lubrication, sealing, heat dissipation and other functions for the stable operation of the compressor, and in the working process of the compressor, the refrigerating oil in an oil pool at the bottom of the compressor is conveyed by an oil supply system and is dispersed in an inner cavity of the compressor under the drive of a high-pressure refrigerant, part of the refrigerating oil can be discharged out of the compressor along with the high-pressure refrigerant in an oil drop state and enters a refrigerating system, so that the oil discharge phenomenon is caused, the oil level of the oil pool is further reduced, the lubrication, sealing and heat dissipation performance of the compressor are affected, and vibration and noise are induced. In the related art, the cooling oil in the oil drop state is driven to the inner wall surface of the compressor only by the centrifugal force generated by the rotation of the crankshaft, so that the oil-gas separation is realized, the separation effect is poor, and the oil discharge amount is large.
Disclosure of utility model
The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides the rotary compressor which can enhance the oil-gas separation effect, reduce the oil discharge amount and stabilize the liquid level of the oil pool.
The utility model also provides refrigeration equipment with the rotary compressor.
According to an embodiment of the first aspect of the present utility model, a rotary compressor includes
A housing having an interior cavity;
The motor assembly is arranged in the inner cavity and comprises a stator and a rotor, and the stator is connected with the shell and is arranged on the periphery of the rotor in a surrounding mode;
the crankshaft is fixedly connected with the rotor and protrudes upwards from the rotor;
The support assembly is arranged in the inner cavity and is positioned above the motor assembly, the support assembly comprises a bracket and a motor bearing, the bracket is fixedly connected with the inner wall of the shell, and the motor bearing is arranged on the bracket and is sleeved at the upper end of the crankshaft;
The oil-gas separation piece is fixedly installed on the rotor and located between the rotor and the support, the oil-gas separation piece comprises stirring plates, the stirring plates are arranged around the periphery of the crankshaft, and the stirring plates extend towards the support.
According to the rotary compressor disclosed by the embodiment of the first aspect of the utility model, at least the following beneficial effects are that the oil-gas separation piece is arranged on the rotor, the stirring plate of the oil-gas separation piece rotates along with the rotor, so that gaseous refrigerant and liquid frozen oil above the rotor can be stirred, the density of the frozen oil is higher than that of the gaseous refrigerant, the frozen oil is thrown to the inner peripheral wall of the shell and flows back to the oil pool at the bottom under the action of centrifugal force, and the gaseous refrigerant is further discharged out of the compressor upwards, thereby realizing oil-gas separation, enhancing the oil-gas separation effect, reducing the oil discharge quantity, stabilizing the liquid level of the oil pool and effectively guaranteeing the lubrication, sealing and heat dissipation performance of the compressor.
According to some embodiments of the utility model, the oil-gas separator further comprises a fixing plate, the stirring plate is connected to the outer periphery of the fixing plate, the fixing plate is provided with a avoidance hole, the fixing plate is fixedly connected to the upper end of the rotor, and the crankshaft penetrates through the avoidance hole.
According to some embodiments of the utility model, the fixing plate is provided with a plurality of fixing holes, the plurality of fixing holes are arranged at intervals along the direction around the central axis of the crankshaft, a fastening piece is connected between the fixing plate and the rotor, and the fastening piece penetrates through the fixing holes.
According to some embodiments of the utility model, the fixing plate is further provided with a through hole, the rotor is provided with a rotor channel, the rotor channel penetrates through two ends of the rotor along the direction of the central axis of the crankshaft, and the through hole is communicated with the rotor channel.
According to some embodiments of the utility model, the maximum outer diameter of the oil and gas separator is greater than twice the maximum distance of the inner wall of the rotor channel from the central axis of the crankshaft and less than or equal to the maximum outer diameter of the rotor.
According to some embodiments of the utility model, the stator includes a first core and a coil wound around the first core and protruding from an upper end of the first core, the upper end of the coil being higher than an upper end of the stirring plate in a direction of a central axis of the crankshaft.
According to some embodiments of the utility model, the minimum distance between the bracket and the first iron core along the direction of the central axis of the crankshaft is H 1, and the minimum distance between the bracket and the stirring plate is H 2, so that H 2/H1 is more than or equal to 0.51 and less than or equal to 0.72.
According to some embodiments of the utility model, the minimum distance between the bracket and the first iron core along the direction of the central axis of the crankshaft is H 1, the maximum distance between the upper end of the coil and the first iron core is H 3, and H 3/H1 is more than or equal to 0.8 and less than or equal to 0.95.
According to some embodiments of the utility model, the minimum distance H 1 between the bracket and the first iron core and the maximum distance H 3 between the upper end of the coil and the first iron core meet the condition that H 1-H3 is more than or equal to 2mm.
A refrigeration appliance according to an embodiment of the second aspect of the utility model comprises a rotary compressor according to an embodiment of the first aspect of the utility model.
The refrigeration equipment at least has the advantages that the rotary compressor is adopted in the refrigeration equipment, the oil-gas separation piece is arranged on the rotor, the stirring plate of the oil-gas separation piece rotates along with the rotor, so that gaseous refrigerant and liquid refrigeration oil above the rotor can be stirred, the refrigeration oil is thrown to the inner peripheral wall of the shell and flows back to the oil pool at the bottom under the action of centrifugal force because the density of the refrigeration oil is higher than that of the gaseous refrigerant, and the gaseous refrigerant is further discharged out of the compressor upwards, so that the oil-gas separation effect is realized, the oil-gas separation effect is enhanced, the oil discharge quantity is reduced, the liquid level of the oil pool is stable, and the lubrication, sealing and heat dissipation performance of the compressor are effectively ensured.
Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.
Drawings
The utility model is further described with reference to the accompanying drawings and examples, in which:
FIG. 1 is a sectional view of a rotary compressor in accordance with an embodiment of the present utility model;
FIG. 2 is a partial cross-sectional view of a rotary compressor in accordance with an embodiment of the present utility model;
fig. 3 is an enlarged view at a in fig. 2;
FIG. 4 is a schematic diagram of a configuration of an oil and gas separator in an embodiment of the utility model;
FIG. 5 is a graph showing the relative height of the oil surface as a function of H 2/H1 in an embodiment of the present utility model;
FIG. 6 is a graph showing the relative height of the oil surface as a function of H 3/H1 in an embodiment of the present utility model.
Reference numerals:
the shell 100, the inner cavity 110, the oil pool 120 and the exhaust pipe 130;
The motor assembly 200, the stator 210, the first iron core 211, the first wall 2111, the coil 212, the second wall 2121, the rotor 220, and the rotor channel 221;
The pump body assembly 300, the first cylinder 310, the second cylinder 320, the crankshaft 330, the eccentric portion 331, the center oil hole 332, the upper bearing 340, the lower bearing 350, the piston 360, the partition 370, the muffler 380;
A support assembly 400, a bracket 410, a third wall 411, and a motor bearing 420;
The oil-gas separator 500, the stirring plate 510, the fourth wall 511, the fixing plate 520, the avoiding holes 521, the fixing holes 522, the through holes 523;
A reservoir 600.
Detailed Description
Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.
In the description of the present utility model, it should be understood that references to orientation descriptions such as upper, lower, front, rear, left, right, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description of the present utility model and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present utility model.
In the description of the present utility model, a number means one or more, a number means two or more, and greater than, less than, exceeding, etc. are understood to not include the present number, and above, below, within, etc. are understood to include the present number. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.
In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, mounting, connection, assembly, cooperation, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical solution.
In the working process of the compressor, the refrigerating oil in the bottom oil pool of the compressor is conveyed by an oil supply system and is dispersed in the inner cavity of the compressor under the drive of a high-pressure refrigerant, and the refrigerating oil in an oil drop state and the gas refrigerant form an oil-gas mixture. In the related art, centrifugal force generated by rotation of a crankshaft of a rotary compressor causes oil drops to be beaten to the inner wall surface of a shell of the compressor, and gaseous refrigerant is discharged out of the compressor to enter a refrigerating system under the action of high pressure of the compressor, but oil-gas separation is realized only by virtue of centrifugal force generated by rotation of the crankshaft, the separation effect is poor, and a large amount of oil drops still enter the refrigerating system along with the gaseous refrigerant discharged out of the compressor. The oil level of the oil pool is reduced due to large oil discharge amount, and the lubrication, sealing and heat dissipation performance of the compressor are affected.
For this reason, referring to fig. 1 to 6, the embodiment of the first aspect of the present utility model provides a rotary compressor, which is applied to a refrigeration apparatus, and the refrigeration apparatus may be an air conditioner, a refrigerator, a freezer, a water dispenser, an air-powered water heater, or the like. The rotary compressor is used as a core power component of refrigeration equipment and is mainly used for compressing a refrigerant so as to achieve the aim of heat exchange through refrigerant circulation.
Referring to fig. 1 and 2, it can be appreciated that the rotary compressor includes a housing 100, a motor assembly 200, a crankshaft 330, a support assembly 400, and an oil and gas separator 500. The casing 100 has a substantially cylindrical structure, an inner cavity 110 is formed in the casing 100, the motor assembly 200, the crankshaft 330, the support assembly 400 and the oil-gas separator 500 are all mounted in the inner cavity 110 of the casing 100, and a space for storing the frozen oil, i.e., the oil sump 120, is formed at the bottom of the inner cavity 110 of the casing 100. The side of the rotary compressor housing is provided with a reservoir 600, and the reservoir 600 is used for storing liquid refrigerant. The top of the housing 100 is further provided with a discharge pipe 130, and the discharge pipe 130 is used for discharging the refrigerant to the outside of the compressor.
Referring to fig. 1 and 2, it will be appreciated that the motor assembly 200 is located at a side of the middle portion of the inner cavity of the housing 100 near the upper side and above the oil pool 120, and the motor assembly 200 includes a stator 210 and a rotor 220, wherein the stator 210 is fixedly connected to the inner circumferential wall of the housing 100, and generally, the stator 210 may be fixed to the inner circumferential wall of the housing 100 by welding or interference fit. The stator 210 has an annular structure, the middle part of the stator has a cavity penetrating along the up-down direction, and the rotor 220 is arranged in the cavity in the middle part of the stator 210 and is in running fit with the stator 210, i.e. the stator 210 is wound around the periphery of the rotor 220. The crankshaft 330 is fixedly connected with the rotor 220, the crankshaft 330 penetrates through the rotor 220, and the upper end of the crankshaft 330 protrudes out of the upper end face of the rotor 220, so that the crankshaft 330 can rotate along with the rotor 220.
Referring to fig. 1 and 2, it can be appreciated that the rotary compressor further includes a pump body assembly 300, the pump body assembly 300 is disposed in the inner cavity 110 of the housing 100 and is located below the motor assembly 200, the pump body assembly 300 includes a cylinder, a crankshaft 330, an upper bearing 340, a lower bearing 350, a piston 360 and a muffler 380, the cylinder is fixedly connected to an inner wall of the compressor housing 100, for example, the cylinder is fixed to the inner wall of the housing 100 by welding, so that the connection of the cylinder is stable, and the stability of the cylinder during the operation is improved. It will be readily appreciated that the cylinder is provided with a compression chamber within which the piston 360 is cyclically reciprocated.
Referring to fig. 1 and 2, it can be appreciated that the lower portion of the crankshaft 330 sequentially passes through the muffler 380, the upper bearing 340, the cylinder and the lower bearing 350 from top to bottom, the crankshaft 330 includes an eccentric portion 331, the eccentric portion 331 is located at the lower portion of the crankshaft 330, and the eccentric portion 331 is rotatably connected with the piston 360 of the cylinder. In operation, the rotor 220 rotates, and since the rotor 220 is fixedly connected to the crankshaft 330, the rotor 220 further drives the crankshaft 330 to rotate, thereby completing compression of the refrigerant in the cylinder.
Referring to fig. 1 and 2, it can be understood that the cylinder includes a first cylinder 310 and a second cylinder 320, the first cylinder 310 is located above the second cylinder 320, a partition 370 is disposed between the first cylinder 310 and the second cylinder 320, an upper bearing 340 is disposed above the first cylinder 310, a lower bearing 350 is disposed below the second cylinder 320, the upper bearing 340 and the lower bearing 350 together limit the first cylinder 310 and the second cylinder 320, a piston 360 of the first cylinder 310 is located in a compression chamber of the first cylinder 310, and a piston 360 of the second cylinder 320 is located in a compression chamber of the second cylinder 320. The crankshaft 330 is provided with two eccentric portions 331 corresponding to the first cylinder 310 and the second cylinder 320, and the eccentric portions 331 of the two crankshafts 330 are rotatably connected to the piston 360 of the first cylinder 310 and the piston 360 of the second cylinder 320, respectively. The upper bearing 340 and the lower bearing 350 are both provided with exhaust holes, the exhaust holes of the upper bearing 340 are communicated with the compression cavity of the first cylinder 310, the exhaust holes of the lower bearing 350 are communicated with the compression cavity of the second cylinder 320, the muffler 380 is also provided with air holes, and the liquid reservoir 600 is respectively connected with the air inlet of the first cylinder 310 and the air inlet of the second cylinder 320 through two air inlet pipes, so that the liquid reservoir 600 supplies refrigerant to the compressor.
Referring to fig. 1 and 2, it will be appreciated that the crankshaft 330 is provided with a central oil hole 332, the central oil hole 332 penetrating the crankshaft 330 in the up-down direction, the lower end of the central oil hole 332 communicating with the oil pool 120 below the housing 100, and the upper end of the central oil hole 332 communicating with the cavity of the housing 100 above the motor assembly 200. The lower end inner wall of the center oil hole 332 is provided with a spiral oil vane, which can rotate together with the crankshaft 330. During the operation of the rotary compressor, the rotor 220 and the crankshaft 330 fixedly coupled to the rotor 220 are rotated by the interaction of the stator 210 and the rotor 220, the eccentric portion 331 of the crankshaft 330 drives the piston 360 to rotate in the compression chamber of the cylinder, the refrigerant is compressed into a high-temperature and high-pressure state, then the compressed refrigerant is discharged from the exhaust holes of the lower bearing 350 and the upper bearing 340, and finally discharged to the refrigerating system from the exhaust pipe 130 at the top of the housing 100. During the rotation of the crankshaft 330, the oil vane installed at the central oil hole 332 of the crankshaft 330 rotates together with the crankshaft 330, and under the rotation of the oil vane, the refrigerant oil at the bottom of the casing 100 enters the central oil hole 332 upward and is discharged from the upper end of the crankshaft 330, and then flows downward under the action of gravity, and the refrigerant oil flows back to the oil sump 120 while passing through the motor assembly 200 and the pump body assembly 300, thereby lubricating the components of the motor assembly 200 and the pump body assembly 300, and effectively ensuring lubrication of internal parts of the compressor.
Referring to fig. 1 and 2, it can be appreciated that the rotary compressor further includes a support assembly 400, the support assembly 400 is mounted in the inner cavity 110 of the casing 100 and located above the motor assembly 200, the support assembly 400 includes a bracket 410 and a motor bearing 420, the bracket 410 is fixed on the inner wall of the casing 100 of the rotary compressor by welding or riveting, the motor bearing 420 is mounted on the bracket 410 and sleeved on the upper end of the crankshaft 330, the motor bearing 420 is in running fit with the crankshaft 330, and meanwhile, the motor bearing 420 can provide support and location for the upper end of the crankshaft 330, which is beneficial to improving the coaxiality of the stator 210 and the rotor 220.
Referring to fig. 1 and 4, it can be understood that the oil and gas separator 500 is fixedly installed to the rotor 220 and located between the rotor 220 and the bracket 410, the oil and gas separator 500 includes an agitating plate 510, the agitating plate 510 is disposed around the crankshaft 330 with a certain gap from the crankshaft 330 in a radial direction, the agitating plate 510 extends toward the bracket 410 in a direction of a central axis of the crankshaft 330, that is, the agitating plate 510 extends upward, and the oil and gas separator 500 is fixedly connected to the rotor 220, so that the agitating plate 510 can rotate in synchronization with the rotor 220. The stirring plate 510 can stir the oil-gas mixture of the gaseous refrigerant and the liquid refrigerant above the rotor 220 by the inner wall of the stirring plate 510 in the rotating process, so that the oil-gas mixture can rotate along the stirring plate 510, the refrigerant with higher density than the gaseous refrigerant is thrown to the inner peripheral wall of the shell 100 under the action of centrifugal force, then flows downwards along the inner peripheral wall of the shell 100 or a gap between components, the refrigerant flows through the motor assembly 200 and the pump body assembly 300 in the refluxing process, finally flows back to the oil pool 120 at the bottom of the shell 100, and the gaseous refrigerant with lower density than the liquid refrigerant is discharged out of the rotary compressor upwards, thereby the oil-gas separation piece 500 can separate the liquid refrigerant from the gaseous refrigerant, the oil-gas separation effect is enhanced, the oil spit quantity is reduced, meanwhile, the refrigerant flows back to lubricate the components in the shell 100, and finally falls back to the oil pool 120, so that the liquid level of the oil pool 120 is kept stable.
It can be understood that, by installing the oil-gas separation member 500 on the rotor 220, the stirring plate 510 of the oil-gas separation member 500 follows the rotor 220 to rotate, the refrigerant oil and the gaseous refrigerant will follow the inner side wall of the stirring plate 510 to perform a rotation motion during the rotation of the stirring plate 510, the centrifugal force of the liquid refrigerant with a higher density relative to the gaseous refrigerant is increased along with the continuous rotation of the stirring plate 510, the refrigerant oil will be thrown out of the stirring plate 510 and sputtered toward the inner peripheral wall of the casing 100, finally, the refrigerant oil flows into the oil pool 120 at the bottom of the inner cavity 110 of the casing 100 along with the inner peripheral wall of the casing 100, the refrigerant oil circulation is completed, the centrifugal force of the gaseous refrigerant with a lower density relative to the liquid refrigerant is small, and the gaseous refrigerant is discharged out of the rotary compressor upwards under the action of high temperature and high pressure, thereby the oil-gas separation is enabled to separate the refrigerant and the refrigerant oil in the cavity between the rotor 220 and the bracket 410 more sufficiently, the oil-gas separation effect is enhanced, the oil discharge quantity is reduced, the liquid level of the refrigerant pool 120 is kept stable, the oil can lubricate the inner components of the casing 100 during the backflow process, the heat dissipation performance of the compressor is effectively ensured, and the heat dissipation performance of the compressor is ensured.
Referring to fig. 1 and 4, it can be understood that the oil and gas separator 500 further includes a fixing plate 520, the stirring plate 510 is connected to an outer peripheral edge of the fixing plate 520, and the stirring plate 510 extends toward the direction of the bracket 410, the fixing plate 520 has a circular plate structure, a relief hole 521 is formed in a middle portion of the fixing plate 520, the crankshaft 330 is disposed through the relief hole 521 of the fixing plate 520, and the fixing plate 520 can be fixed to an upper end surface of the rotor 220 by means of screw connection or riveting, so that the oil and gas separator 500 is firmly fixed to the upper end surface of the rotor 220, a contact area between the oil and gas separator 500 and the rotor 220 is increased, the oil and gas separator 500 is tightly attached to the rotor 220 and is installed more firmly, installation stability is improved, and the rotary compressor can be operated stably.
Referring to fig. 1 and 4, it may be understood that the fixing plate 520 is provided with a plurality of fixing holes 522, the plurality of fixing holes 522 are arranged at intervals along a direction around the central axis, specifically, six fixing holes 522 are arranged at equal intervals along the circumferential direction with the avoiding hole 521 of the fixing plate 520 as the center, the upper end surface of the rotor 220 is provided with corresponding mounting holes of the fixing hole 522, a fastening piece is connected between the fixing plate 520 and the rotor 220, the fastening piece passes through the fixing hole 522, and the fastening piece may be a screw or a rivet, and the screw or the rivet passes through the fixing hole 522 to fix the fixing plate 520 on the rotor 220, so that the fixing plate 520 is firmly fixed on the upper end surface of the rotor 220.
Referring to fig. 1 and 4, it can be understood that the fixing plate 520 is further provided with a through hole 523, the rotor 220 is provided with a rotor passage 221, the rotor passage 221 penetrates through both ends of the rotor 220 in the direction of the central axis, the through hole 523 communicates with the rotor passage 221, the gaseous refrigerant compressed into high temperature and high pressure in the compression chamber of the cylinder rises along the rotor passage 221, is discharged between the fixing plate 520 and the support assembly 400 through the through hole 523, and forms an oil-gas mixture with liquid-state refrigerant oil, and the stirring plate 510 immediately stirs the oil-gas mixture to separate the refrigerant oil from the oil-gas mixture, thereby achieving the oil-gas separation.
Referring to fig. 1 and 4, it can be appreciated that the maximum outer diameter of the oil and gas separator 500 is less than or equal to the maximum outer diameter of the rotor 220, that is, the maximum outer diameter of the agitating plate 510 is less than or equal to the maximum outer diameter of the rotor 220. If the maximum outer diameter of the agitating plate 510 is larger than the maximum outer diameter of the rotor 220 but smaller than the inner diameter of the stator 210, the agitating plate 510 may interfere with the stator 210 in a structural manner when rotating, and there is a risk of collision. Therefore, making the maximum outer diameter of the oil-gas separator 500 smaller than or equal to the maximum outer diameter of the rotor 220 can avoid interference of the oil-gas separator 500 with the stator 210. Meanwhile, when the maximum outer diameter of the stirring plate 510 is as large as the maximum outer diameter of the rotor 220, the inner wall of the stirring plate 510 has a larger side area under the condition that the extending length of the stirring plate 510 is unchanged, so that the stirring plate 510 can stir more oil-gas mixture, because the oil-gas separation member 500 is fixedly connected with the rotor 220, the angular velocity of the oil-gas separation member 500 is equal to the angular velocity of the rotor 220, when the rotating speed of the rotor 220 is unchanged, the larger the outer diameter of the oil-gas separation member 500 is, the larger the linear velocity is, the centrifugal force to which the oil-gas mixture is subjected is, the more easily separated liquid-state frozen oil from the oil-gas mixture is, the oil-gas separation effect is enhanced, and the remaining gaseous refrigerant in the oil-gas mixture is continuously discharged upwards out of the compressor.
Further, the maximum outer diameter of the oil-gas separator 500 is made to be greater than twice the maximum distance between the inner wall of the rotor passage 221 and the central axis of the crankshaft 330 in the radial direction of the crankshaft 330, so that the mixture of the refrigerant and the refrigerant oil discharged from the upper end opening of the rotor passage 221 is located in the space surrounded by the agitating plate 510 to perform oil-gas separation.
Referring to fig. 1 and 4, it can be understood that the stator 210 includes a first core 211 and a coil 212, the coil 212 being wound around the first core 211 and protruding from the upper end of the first core 211, the coil 212 being a winding mounted on the stator 210, that is, a copper wire wound on the stator 210. The upper end surface of the first core 211 is a first wall surface 2111, the upper end surface of the coil 212 is a second wall surface 2121, and the upper end surface of the stirring plate 510 on the side close to the holder 410 is a fourth wall surface 511. Along the central axis direction of the crankshaft 330, the second wall 2121 is higher than the first wall 2111, the fourth wall 511 is lower than the second wall 2121, that is, the upper end of the coil 212 is higher than the upper end of the first iron core 211 and the upper end of the stirring plate 510, and the upper end surface of the stirring plate 510 is higher than the upper end surface of the first iron core 211, a gap is reserved between the bracket 410 and the coil 212, the stirring plate 510 rotating along with the rotor 220 separates the oil-gas mixture, and the separated frozen oil can be thrown towards the inner wall of the shell 100 along the gap between the bracket 410 and the coil 212 in a direction away from the crankshaft 330, so that the oil-gas separation is realized.
Referring to fig. 1 to 3, it is understood that the lower end surface of the bracket 410 near the stator 210 is a third wall 411, the minimum distance between the third wall 411 and the first wall 2111 is H 1, and the minimum distance from the lower end surface of the bracket 410 to the upper end surface of the first core 211 is H 1 along the central axis direction of the crankshaft 330. The minimum distance between the third wall 411 and the fourth wall 511 is defined as H 2, that is, H 2 is the minimum distance between the upper end surface of the stirring plate 510 and the lower end surface of the bracket 410, it is easy to understand that the lower end surface of the bracket 410 is parallel to the upper end surface of the first core 211, the lower end surface of the bracket 410 is parallel to the upper end surface of the stirring plate 510, that is, the distances between the lower end surface of the bracket 410 and the upper end surface of the stirring plate 510 are equal everywhere, and the distances between H 2,H1 and H 2 are 0.51-H 2/H1 -0.72.
It should be noted that, assuming that H 1 is unchanged, H 2 is made smaller so that H 2/H1 is smaller than 0.51, that is, the minimum distance between the lower end surface of the bracket 410 and the upper end surface of the first iron core 211 is unchanged, the upper end surface of the stirring plate 510 is made higher, so that the minimum distance between the upper end surface of the stirring plate 510 and the lower end surface of the bracket 410 is made smaller, the height of the stirring plate 510 is made higher, the axial stirring range of the stirring plate 510 for the oil-gas mixture is made larger, the stirring speed of the refrigerant is too fast, and the refrigerant with high rotation speed enters the refrigeration system through the exhaust pipe 130, so that the oil discharge amount is increased. Assuming that H 1 is unchanged, H 2 is increased so that H 2/H1 is greater than 0.72, that is, the minimum distance between the lower end surface of the bracket 410 and the upper end surface of the first iron core 211 is unchanged, the upper end surface of the stirring plate 510 is lowered so that the minimum distance between the upper end surface of the stirring plate 510 and the lower end surface of the bracket 410 is increased, the axial stirring range of the stirring plate 510 during rotation is small, the stirring speed of the oil-gas mixture rotating along with the stirring plate 510 is small, the centrifugal force is insufficient, liquid frozen oil is difficult to separate from the oil-gas mixture, and the oil-gas separation effect is poor.
Referring to fig. 3 and 5, the minimum distance between the upper end surface of the first iron core 211 and the lower end surface of the bracket 410 (i.e., H 1) and the minimum distance between the lower end surface of the bracket 410 and the upper end surface of the stirring plate 510 (i.e., H 2) satisfy 0.51.ltoreq.h 2/H1.ltoreq.0.72, so that the compressor can reduce the oil discharge amount and obtain a good oil-gas separation effect, referring to fig. 5, when H 2/H1 =0.51, the relative height of the oil surface is about 0.72 (the relative height of the oil surface is the ratio of the actual liquid surface to the theoretical maximum liquid surface), when H 2/H1 =0.6, the relative height of the oil surface is about 0.8, and when H 2/H1 =0.72, the relative height of the oil surface is about 0.73, as can be seen from fig. 5, the oil-gas separation effect of the oil-gas mixture is good when the ratio relationship between H 1 and H 2 is in the range of 0.51 to 0.72, so that the oil return to the oil pool can be enhanced, the oil surface can be reduced to the liquid surface of 120, and the oil discharge amount can be kept within the range of 0.72.72.7 to be kept stable.
Referring to fig. 1 to 3, it can be understood that the upper end surface of the coil 212 is higher than the upper end surface of the first core 211, and the maximum distance between the upper end surface of the coil 212 and the upper end surface of the first core 211 along the central axis direction of the crankshaft 330 is defined as H 3, that is, the maximum distance between the second wall 2121 and the first wall 2111 is defined as H 3,H3 and H 1, which satisfies 0.8.ltoreq.h 3/H1.ltoreq.0.95.
It should be noted that, assuming that H 1 is unchanged, H 3 is increased to make H 3/H1 greater than 0.95, that is, the minimum distance from the lower end surface of the bracket 410 to the first iron core 211 is unchanged, the height of the upper end surface of the coil 212 is increased, the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410 is reduced, the area speed is too high when the frozen oil passes through the narrow gap, the oil drops directly impact the wall surface of the shell 100 to become broken frozen oil beads, the frozen oil is not directly sagging on the wall surface of the shell 100, the refrigerant carries the frozen oil beads from the exhaust pipe 130 to enter the refrigeration system, and the oil discharge amount is increased. Assuming that H 3 is unchanged, H 1 is increased so that H 3/H1 is smaller than 0.8, that is, the minimum distance from the upper end surface of the coil 212 to the upper end surface of the first iron core 211 is unchanged, the lower end surface of the bracket 410 is increased, which means that the overall height of the bracket 410 is increased, the bracket 410 occupies more space above the housing 100, the separation effect of the upper cavity is affected, the oil-gas separation is insufficient, more refrigerating oil enters the refrigerating system from the exhaust pipe 130, the oil discharge amount is increased, and the refrigerating oil level of the compressor oil pool 120 is reduced.
Referring to fig. 3 and 6, when the minimum distance between the upper end surface of the first core 211 and the lower end surface of the bracket 410 (i.e., H 1) and the maximum distance between the upper end surface of the coil 212 and the upper end surface of the first core 211 (i.e., H 3) satisfy 0.8.ltoreq.h 3/H1.ltoreq.0.95, so that the compressor can reduce the oil discharge amount and obtain a better oil-gas separation effect, referring to fig. 6, when the relative height of the oil level of H 3/H1 =0.8 is 0.7, when the relative height of the oil level of H 3/H1 =0.9 is 0.8, when the relative height of the oil level of H 3/H1 =0.95 is 0.7, it can be seen from fig. 6 that the oil-gas separation effect of the oil-gas mixture is good, the oil-gas separation effect is enhanced, more refrigerant oil flows back to the oil sump 120, the oil discharge amount is reduced, the liquid level of the oil sump 120 is kept stable, and the relative height of the oil level is kept within the range of 0.7 to 0.9.
Referring to FIGS. 1 to 3, it can be understood that the minimum distance H 1 between the lower end surface of the bracket 410 and the upper end surface of the first core 211 and the maximum distance H 3 between the upper end surface of the coil 212 and the upper end surface of the first core 211 satisfy that H 1-H3 is equal to or more than 2mm, that is, the distance from the third wall surface 411 to the second wall surface 2121 is equal to or more than 2mm, and the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410 is further defined because the coil has a certain voltage when the compressor is operated, and the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410 is greater than 2mm, so that the electric shock between the coil 212 and the bracket 410 can be prevented, thereby enabling the compressor to operate normally.
A refrigeration appliance according to an embodiment of the second aspect of the present utility model includes a rotary compressor according to an embodiment of the first aspect of the present utility model.
The refrigeration equipment adopts all the technical schemes of the rotary compressor of the embodiment, so that the refrigeration equipment has at least all the beneficial effects brought by the technical schemes of the embodiment.
The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, but the present utility model is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present utility model.
Claims (10)
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| Application Number | Priority Date | Filing Date | Title |
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| CN202421218686.7U CN222315375U (en) | 2024-05-30 | 2024-05-30 | Rotary compressor and refrigeration equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202421218686.7U CN222315375U (en) | 2024-05-30 | 2024-05-30 | Rotary compressor and refrigeration equipment |
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| CN222315375U true CN222315375U (en) | 2025-01-07 |
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| CN202421218686.7U Active CN222315375U (en) | 2024-05-30 | 2024-05-30 | Rotary compressor and refrigeration equipment |
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