CN106168220B - Compressor and refrigeration cycle device - Google Patents

Compressor and refrigeration cycle device Download PDF

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Publication number
CN106168220B
CN106168220B CN201610692381.3A CN201610692381A CN106168220B CN 106168220 B CN106168220 B CN 106168220B CN 201610692381 A CN201610692381 A CN 201610692381A CN 106168220 B CN106168220 B CN 106168220B
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Prior art keywords
compressor
rotor
shell
compression mechanism
equal
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CN106168220A (en
Inventor
付清轩
张河茂
伏拥军
刘银虎
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Anhui Meizhi Precision Manufacturing Co Ltd
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Anhui Meizhi Precision Manufacturing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/13—Vibrations

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

The invention discloses a compressor and a refrigeration cycle device, wherein the compressor comprises: a housing; the crankshaft is arranged in the shell; the motor is arranged in the shell and comprises a stator and a rotor, the rotor is rotatably arranged in the stator, and the rotor is sleeved at the upper end of the crankshaft; and compressing mechanism, compressing mechanism establishes in the casing and be connected with the internal perisporium of casing, and compressing mechanism overlaps the lower extreme at the bent axle, and the distance between the lower terminal surface of the position that compressing mechanism and casing are connected and the iron core of rotor is H, and compressing mechanism includes upper bearing, cylinder assembly and the lower bearing of arranging in proper order along upper and lower direction, and the height of upper bearing is H1, and satisfies: H/H1 is more than or equal to 0.5 and less than or equal to 0.8. According to the compressor, the ratio of the distance H between the position where the compression mechanism is connected with the shell and the lower end face of the iron core of the rotor to the height H1 of the upper bearing is more than or equal to 0.5 and less than or equal to H/H1 and less than or equal to 0.8, so that the electromagnetic noise peak value in the operating frequency range of the compressor can be reduced, and the lower rotor vibration amplitude value can be obtained.

Description

Compressor and refrigeration cycle device
Technical Field
The invention relates to the technical field of refrigeration equipment, in particular to a compressor and a refrigeration cycle device.
Background
In the related art, in order to reduce the vibration noise generated by the motor of the compressor, the main bearing is inserted into the hole part of the iron core of the rotor as much as possible, and the compressor with the structure cannot solve the problem of the motor noise very well, and particularly cannot guide how to determine the fixed position of the compression mechanism, so that the natural frequency of a system consisting of the rotor and the compression mechanism avoids the integral multiple of the operating frequency of the compressor, thereby reducing the vibration amplitude of the rotor and reducing the electromagnetic noise of the frequency band.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the technical problems in the related art. Therefore, the invention provides a compressor which has the advantages of low electromagnetic noise peak value and low rotor vibration amplitude.
The invention also provides a refrigeration cycle device which comprises the compressor.
The compressor according to the embodiment of the present invention includes: a housing; a crankshaft disposed within the housing; the motor is arranged in the shell and comprises a stator and a rotor, the rotor is rotatably arranged in the stator, and the rotor is sleeved at the upper end of the crankshaft; and the compression mechanism is arranged in the shell and connected with the inner peripheral wall of the shell, the compression mechanism is sleeved at the lower end of the crankshaft, the distance between the position of the compression mechanism connected with the shell and the lower end face of the iron core of the rotor is H, the compression mechanism comprises an upper bearing, an air cylinder assembly and a lower bearing which are sequentially arranged along the vertical direction, the height of the upper bearing is H1, and the requirements are met: H/H1 is more than or equal to 0.5 and less than or equal to 0.8.
According to the compressor provided by the embodiment of the invention, the ratio of the distance H between the position where the compression mechanism is connected with the shell and the lower end surface of the iron core of the rotor to the height H1 of the upper bearing is more than or equal to 0.5 and less than or equal to H/H1 and less than or equal to 0.8, so that the electromagnetic noise peak value in the operating frequency range of the compressor can be reduced, and the lower rotor vibration amplitude value can be obtained.
According to some embodiments of the invention, the core volume thickness of the rotor is H2, the diameter of the crankshaft is d, and: h2/d < 4.0.
According to some embodiments of the invention, the compression mechanism is welded to the housing.
According to some embodiments of the invention, the compressor further comprises a support ring, an inner ring of the support ring is connected with the compression mechanism, and an outer ring of the support ring is connected with the inner circumferential wall of the shell.
In some embodiments of the present invention, the inner ring of the support ring is welded to the compression mechanism, and the outer ring of the support ring is welded to the inner circumferential wall of the housing.
In some embodiments of the invention, the inner ring of the support ring is welded to the cylinder assembly.
In some embodiments of the present invention, the support ring includes a main annular portion, the main annular portion is disposed on the upper bearing and attached to the upper surface of the cylinder assembly, an outer periphery of the main annular portion is folded upwards to extend out an annular flange portion, and an outer peripheral surface of the annular flange portion is welded to the inner peripheral wall of the housing.
The refrigeration cycle device according to the embodiment of the invention comprises the compressor.
According to the refrigeration cycle device provided by the embodiment of the invention, the ratio of the distance H between the position where the compression mechanism is connected with the shell and the lower end surface of the iron core of the rotor to the height H1 of the upper bearing is more than or equal to 0.5 and less than or equal to H/H1 and less than or equal to 0.8, so that the electromagnetic noise peak value in the operating frequency range of the compressor can be reduced, and the lower rotor vibration amplitude value can be obtained.
Additional aspects and advantages of the invention 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 invention.
Drawings
Fig. 1 is a schematic structural view of a compressor according to an embodiment of the present invention;
FIG. 2 is a graph in which the peak value of electromagnetic noise shifts to the high operating frequency side with the decrease in H/H1, in which the broken line is a graph of the peak value of electromagnetic noise and the operating frequency when H/H1 is 0.8 or less, and the solid line is a graph of the peak value of electromagnetic noise and the operating frequency when H/H1 is > 0.8;
FIG. 3 is a graph of rotor vibration amplitude versus H/H1;
FIG. 4 is a graph in which m is decreased and a peak value of electromagnetic noise is shifted to a high operating frequency side, in which a dotted line is a graph of the peak value of the electromagnetic noise with a rotor mass m and the operating frequency, and a solid line is a graph of the peak value of the electromagnetic noise with a rotor mass 2m and the operating frequency;
FIG. 5 is a graph of the rate of reduction of the maximum value of electromagnetic noise versus H2/d.
Reference numerals:
the compressor (100) is provided with a compressor,
a housing 1, an upper housing 11, a main housing 12, a lower housing 13,
the crankshaft 2 is provided with a crankshaft for rotating,
the motor 3, the stator 31, the rotor 32,
a compression mechanism 4, an upper bearing 41, an upper cylinder 42, a middle partition plate 43, a lower cylinder 44, a lower bearing 45,
a support ring member 5, a main body annular part 51 and an annular flanging part 52.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
A compressor 100 according to an embodiment of the present invention is described below with reference to fig. 1 to 5.
As shown in fig. 1, a compressor 100 according to an embodiment of the present invention includes a housing 1, a crankshaft 2, a motor 3, and a compression mechanism 4.
Specifically, the crankshaft 2 is disposed in the housing 1, the motor 3 is disposed in the housing 1 and includes a stator 31 and a rotor 32, the rotor 32 is rotatably disposed in the stator 31, the rotor 32 is disposed at an upper end (an upper end as shown in fig. 1) of the crankshaft 2, the compression mechanism 4 is disposed in the housing 1 and is connected to an inner peripheral wall of the housing 1, the compression mechanism 4 is disposed at a lower end (a lower end as shown in fig. 1) of the crankshaft 2, a distance between a position where the compression mechanism 4 is connected to the housing 1 and a lower end surface (a lower end surface as shown in fig. 1) of an iron core of the rotor 32 is H, the compression mechanism 4 includes an upper bearing 41, a cylinder assembly and a lower bearing 45 which are sequentially arranged in an up-down direction, a height of the upper bearing 41 is H35: H/H1 is more than or equal to 0.5 and less than or equal to 0.8.
As shown in fig. 2, when H/H1 is less than or equal to 0.8, in the operating frequency range of the compressor 100, the peak value of the electromagnetic noise of integral multiple of the operating frequency moves outside the operating frequency range of the compressor 100, and the peak value of the electromagnetic noise of the compressor 100 in the operating range is reduced obviously. Further, as shown in fig. 3, when H/H1 < 0.5, the vibration amplitude of the rotor 32 is rapidly deteriorated when the compressor 100 is operated. Therefore, by satisfying H/H1 at 0.5 ≦ H/H1 ≦ 0.8, it is possible to reduce the peak value of electromagnetic noise in the operating frequency range of the compressor 100 and to achieve a lower vibration amplitude of the rotor 32.
According to the compressor 100 of the embodiment of the invention, the ratio of the distance H between the position where the compression mechanism 4 is connected with the shell 1 and the lower end surface of the iron core of the rotor 32 to the height H1 of the upper bearing 41 is equal to or more than 0.5 and equal to or less than H/H1 and equal to or less than 0.8, so that the peak value of electromagnetic noise in the operating frequency range of the compressor 100 can be reduced, and the lower vibration amplitude of the rotor 32 can be obtained.
In some embodiments of the present invention, as shown in fig. 1, the core volume thickness of the rotor 32 is H2, the diameter of the crankshaft 2 is d, and: h2/d < 4.0. In addition, the natural frequency f is (k/m)1/2Where k is the stiffness coefficient of the rotor 32 and m is the mass of the rotor 32, when the thickness H2 of the core of the rotor 32 increases, the mass m of the rotor 32 increases and the natural frequency of the system of the rotor 32 and the compression mechanism 4 decreases. As shown in fig. 4, when the mass m of the rotor 32 increases, the peak value of the electromagnetic noise of the integral multiple of the operation frequency shifts to the operation frequency of the compressor 100, so that the peak value of the electromagnetic noise increases in the operation frequency of the compressor 100. As shown in fig. 5, when the ratio of the core thickness H2 of the rotor 32 to the diameter d of the crankshaft 2 satisfies H2/d < 4.0, the reduction rate of the maximum value of electromagnetic noise is high. Therefore, when the requirement of 0.5 ≦ H/H1 ≦ 0.8 is satisfied, the ratio of the core thickness H2 of the rotor 32 to the diameter d of the crankshaft 2 satisfies H2/d < 4.0, and the reduction rate of the electromagnetic noise peak value can be further optimized.
In some embodiments of the present invention, the compression mechanism 4 is welded to the housing 1 in a simple and reliable manner, which can simplify the processing of the compressor 100, improve the production efficiency, and improve the reliability of the compressor 100.
In other embodiments of the present invention, as shown in fig. 1, the compressor 100 further includes a support ring 5, an inner ring of the support ring 5 is connected to the compression mechanism 4, and an outer ring of the support ring 5 is connected to the inner circumferential wall of the housing 1. Therefore, the compression mechanism 4 can be indirectly connected with the inner peripheral wall of the shell 1 through the support ring piece 5, so that the compression mechanism 4 is fixed, when the distance between the compression mechanism 4 and the inner peripheral wall of the shell 1 is large, the support ring piece 5 can be used for connection, the compression mechanism 4 is prevented from being offset due to direct connection between the compression mechanism 4 and the inner peripheral wall of the shell 1, and the working reliability of the compressor 100 is improved.
Further, the inner ring of the support ring 5 is welded with the compression mechanism 4, and the outer ring of the support ring 5 is welded with the inner circumferential wall of the shell 1. The welding method is simple and reliable, the processing technology of the compressor 100 can be simplified, the production efficiency can be improved, and meanwhile, the reliability of the compressor 100 can be improved. Further, the inner ring of the support ring 5 is welded to the cylinder block. For example, the inner ring of the support ring member 5 may be welded to the cylinder, and when the cylinder assembly includes two cylinders, the support ring member 5 may be welded to one of the cylinders, or to the intermediate partition 43 between the two cylinders. Therefore, the structure and the processing technology can be simplified, and the production efficiency is improved.
In some embodiments of the present invention, as shown in fig. 1, the support ring member 5 includes a main annular portion 51, the main annular portion 51 is sleeved on the upper bearing 41 and attached to the upper surface of the cylinder assembly, an outer periphery of the main annular portion 51 is folded upwards to extend out an annular flange portion 52, and an outer peripheral surface of the annular flange portion 52 is welded to the inner peripheral wall of the housing 1. The lower end surface of the main body annular portion 51 may be welded to the upper end surface of the cylinder assembly or the inner peripheral wall of the main body annular portion 51 may be welded to the outer peripheral wall of the upper bearing 41, and the outer peripheral surface of the annular flange portion 52 is welded to the inner peripheral wall of the housing 1. The compressing mechanism 4 can be indirectly connected with the inner peripheral wall of the shell 1 through the supporting ring piece 5, so that the compressing mechanism 4 is fixed, when the distance between the compressing mechanism 4 and the inner peripheral wall of the shell 1 is large, the supporting ring piece 5 can be used for connection, the compressing mechanism 4 is prevented from being offset due to direct connection between the compressing mechanism 4 and the inner peripheral wall of the shell 1, and the working reliability of the compressor 100 is improved.
A compressor 100 according to an embodiment of the present invention will be described with reference to fig. 1 to 5, and the following description is exemplary only and is not intended to limit the present invention.
As shown in fig. 1, a compressor 100 according to an embodiment of the present invention includes a housing 1, a crankshaft 2, a motor 3, a compression mechanism 4, and a support ring 5.
As shown in fig. 1, the housing 1 may include an upper housing 11, a main housing 12, and a lower housing 13. Crankshaft 2, motor 3 and compressing mechanism 4 all establish in casing 1, and motor 3 includes stator 31 and rotor 32, and rotor 32 rotationally establishes in stator 31, and rotor 32 cover is established in the upper end of crankshaft 2, and rotor 32 includes the iron core in the upper end cooperation tape shaft hole with crankshaft 2. The compression mechanism 4 is sleeved on the lower end of the crankshaft 2, and the compression mechanism 4 comprises an upper bearing 41, an upper cylinder 42, a middle partition plate 43, a lower cylinder 44 and a lower bearing 45 which are sequentially arranged along the vertical direction.
The supporting ring member 5 comprises a main body annular portion 51, the main body annular portion 51 is sleeved on the upper bearing 41 and attached to the upper end face of the upper air cylinder 42, the lower end face of the supporting ring member 5 is welded to the upper surface of the upper air cylinder 42, the outer periphery of the main body annular portion 51 is upwards turned and extended to form an annular flanging portion 52, the outer periphery of the annular flanging portion 52 is welded to the inner peripheral wall of the shell 1, and the compression mechanism 4 is indirectly connected with the inner peripheral wall of the shell 1 through the supporting ring member 5.
The distance between the position of the welding point of the support ring member 5 and the lower end face of the iron core of the rotor 32 is H, the height of the upper bearing 41 is H1, as shown in FIG. 2, when H/H1 is less than or equal to 0.8, the peak value of the electromagnetic noise of integral multiple of the operating frequency moves outside the operating frequency range of the compressor 100 within the operating frequency range of the compressor 100, and the peak value of the electromagnetic noise of the compressor 100 within the operating range is obviously reduced. Further, as shown in fig. 3, when H/H1 < 0.5, the vibration amplitude of the rotor 32 is rapidly deteriorated when the compressor 100 is operated. Therefore, in the present embodiment, by satisfying H/H1 at 0.5. ltoreq. H/H1. ltoreq.0.8, it is possible to reduce the peak value of electromagnetic noise in the operating range and to obtain a low vibration amplitude of the rotor 32.
In addition, the natural frequency f is (k/m)1/2Where k is the stiffness coefficient of the rotor 32 and m is the mass of the rotor 32, when the thickness H2 of the core of the rotor 32 increases, the mass m of the rotor 32 increases and the natural frequency of the system formed by the rotor 32 and the compression mechanism 4 decreases, as shown in fig. 4, and when the mass m of the rotor 32 increases, the electromagnetic noise peaks of integral multiples of the operating frequency shift toward the operating frequency of the compressor 100, so that the electromagnetic noise peaks in the operating frequency of the compressor 100 increase. As shown in fig. 5, when the ratio of the core thickness H2 of the rotor 32 to the diameter d of the crankshaft 2 satisfies H2/d < 4.0, the electromagnetic noise maximum value reduction rate is high. Therefore, when the requirement of 0.5 ≦ H/H1 ≦ 0.8 is satisfied, the ratio of the core thickness H2 of the rotor 32 to the outer diameter d of the crankshaft 2 is satisfied as H2/d < 4.0, and the reduction rate of the electromagnetic noise peak value can be further optimized.
A refrigeration cycle apparatus according to an embodiment of the present invention includes the above-described compressor 100.
According to the refrigeration cycle device of the embodiment of the invention, the ratio of the distance H between the position where the compression mechanism 4 is connected with the shell 1 and the lower end surface of the iron core of the rotor 32 to the height H1 of the upper bearing 41 is equal to or more than 0.5 and equal to or less than H/H1 and equal to or less than 0.8, so that the peak value of electromagnetic noise in the operating frequency range of the compressor 100 can be reduced, and the lower vibration amplitude of the rotor 32 can be obtained.
In some embodiments of the present invention, the refrigeration cycle apparatus further includes a condenser, an expansion mechanism, and an evaporator. Wherein the condenser and the expansion mechanism are connected with the evaporator in sequence, the exhaust pipe of the compressor 100 is connected with the condenser and the suction pipe of the compressor 100 is connected with the evaporator. Therefore, the high-temperature and high-pressure refrigerant compressed by the compressor 100 is discharged from the exhaust pipe of the compressor 100 and enters the condenser for condensation heat exchange, then the gas enters the expansion mechanism for throttling and pressure reduction treatment, then flows into the evaporator for evaporation and heat absorption to become a low-temperature and low-pressure refrigerant, and finally the low-temperature and low-pressure refrigerant flows back to the compression cavity of the compressor 100 again for compression, so that a refrigeration cycle is completed.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims (8)

1. A compressor, comprising:
a housing;
a crankshaft disposed within the housing;
the motor is arranged in the shell and comprises a stator and a rotor, the rotor is rotatably arranged in the stator, and the rotor is sleeved at the upper end of the crankshaft; and
the compression mechanism is arranged in the shell and connected with the inner peripheral wall of the shell, the compression mechanism is sleeved at the lower end of the crankshaft, the distance between the position where the compression mechanism is connected with the shell and the lower end face of the iron core of the rotor is H, the compression mechanism comprises an upper bearing, an air cylinder assembly and a lower bearing which are sequentially arranged along the vertical direction, the height of the upper bearing is H1, and the requirements are met: H/H1 is more than or equal to 0.5 and less than or equal to 0.8.
2. The compressor of claim 1, wherein a core volume thickness of the rotor is H2, a diameter of the crankshaft is d, and: h2/d < 4.0.
3. The compressor of claim 1, wherein the compression mechanism is welded to the housing.
4. The compressor of claim 1, further comprising a support ring, an inner ring of the support ring being coupled to the compression mechanism and an outer ring of the support ring being coupled to the inner circumferential wall of the shell.
5. The compressor of claim 4, wherein an inner ring of the support ring is welded to the compression mechanism and an outer ring of the support ring is welded to an inner circumferential wall of the shell.
6. The compressor of claim 5, wherein the inner ring of the support ring is welded to the cylinder assembly.
7. The compressor of claim 4, wherein the support ring includes a main annular portion, the main annular portion is disposed on the upper bearing and attached to the upper surface of the cylinder assembly, an outer periphery of the main annular portion is folded upwards to extend out an annular flange portion, and an outer peripheral surface of the annular flange portion is welded to the inner peripheral wall of the housing.
8. A refrigeration cycle apparatus, characterized by comprising the compressor according to any one of claims 1 to 7.
CN201610692381.3A 2016-08-19 2016-08-19 Compressor and refrigeration cycle device Active CN106168220B (en)

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CN106168220B true CN106168220B (en) 2020-04-03

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CN201486868U (en) * 2009-09-03 2010-05-26 广东美芝制冷设备有限公司 Cylinder fixing mechanism of rotary compressor
CN201779023U (en) * 2010-09-10 2011-03-30 广东美芝制冷设备有限公司 Rotary compressor
CN201874827U (en) * 2010-11-17 2011-06-22 广东美芝制冷设备有限公司 Thrust structure of rotary compressor
CN201916200U (en) * 2010-12-28 2011-08-03 广东美芝制冷设备有限公司 Oil passage structure of thrust brake of rotary compressor
CN102062099B (en) * 2011-02-12 2015-03-25 沈阳华润三洋压缩机有限公司 Rotary type compressor
CN201953660U (en) * 2011-02-16 2011-08-31 广东美芝制冷设备有限公司 Oil effluence decreasing device for compressor
CN205977694U (en) * 2016-08-19 2017-02-22 安徽美芝精密制造有限公司 Compressor and refrigerating cycle apparatus

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