CN100458165C - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
CN100458165C
CN100458165C CNB2006101399372A CN200610139937A CN100458165C CN 100458165 C CN100458165 C CN 100458165C CN B2006101399372 A CNB2006101399372 A CN B2006101399372A CN 200610139937 A CN200610139937 A CN 200610139937A CN 100458165 C CN100458165 C CN 100458165C
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CN
China
Prior art keywords
space
refrigeration agent
end plate
plate portion
press part
Prior art date
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Expired - Fee Related
Application number
CNB2006101399372A
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Chinese (zh)
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CN1955475A (en
Inventor
久保田淳
关上和夫
大沼敦
田所哲也
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Appliances Inc
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Publication of CN1955475A publication Critical patent/CN1955475A/en
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Publication of CN100458165C publication Critical patent/CN100458165C/en
Expired - Fee Related legal-status Critical Current
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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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/008—Hermetic pumps
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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

Abstract

Disclosed is a rotary compressor capable of inhibiting the pressure fluctuation generated in the ejection space of the intermediate container to improve energy efficiency. The rotary compressor(1)comprises a rotary type low pressure side compressing part(10)compressing the refrigerant; a rotary type high pressure side compressing part(12)compressing the refrigerant at opposite phase with respect to the compressing procedure of the low pressure side compressing part; and an intermediate container(18)connected between the refrigerant ejection opening(14)of the low pressure side compressing part and the refrigerant suction opening(16)of the high pressure side compressing part. The interior ejection space(20)of the intermediate container is divided into two parts, that is a main stream side space(20a)and an opposite main stream side space(20b), by an isolating part(22). The refrigerant ejection opening of the low pressure side compressing part and the refrigerant suction opening of the high pressure side compressing part are communicated with each other at the main stream side space, and a refrigerant flow path(20c)connecting the main stream side space with the opposite main stream side space is formed at the isolating part.

Description

Rotary compressor
Technical field
The present invention relates to be applicable to indoor air is carried out rotary compressor in the freezing cycle device of air conditioner etc. of heating and cooling.
Background technique
With the air conditioner is the freezing cycle device of representative, utilize repeatedly the gasification of refrigeration agent and liquefaction change of state freeze cycle and air or water etc. is carried out heating and cooling.As the coolant compressor that is applicable to this refrigerating plant, the known turning two-grade compressor that two stage compressor structure with interim ground compressed refrigerant is arranged.For example, turning two-grade compressor has: the helicoid low voltage side press part of compressed refrigerant; With respect to the compression section of low voltage side press part helicoid high pressure side press part with the antiphase compressed refrigerant; And have the intermediate receptacle that attracts the inner space that mouth is communicated with (below be called spray the space) with the refrigeration agent of the refrigeration agent ejiction opening of low voltage side press part and high pressure side press part.
In the intermediate receptacle of such turning two-grade compressor, because the phase difference of the suction process of the ejection process of low voltage side press part and high pressure side press part (for example 180 degree), and produce pressure oscillation in the ejection space.That is, carry out repeatedly: the pressure that the pressure that the state that can't be inhaled into because of the refrigeration agent to the ejection of ejection space causes increases and causes because of the state that had begun to suck before spraying refrigeration agent to the ejection space reduces.
Therefore, to spray the pressure oscillation that the space produces in order reducing, and to enlarge the volume in ejection space as best one can.For example, following scheme has been proposed: by the inner circle wall concavo-convex petal-shaped that forms on the direction of footpath that makes intermediate receptacle, thereby avoid connected element, do one's utmost to guarantee to spray the volume in space, the overcompression loss (for example patent documentation 1) in the inhibition ejection space simultaneously in the perisporium installation of intermediate receptacle.
Patent documentation 1: TOHKEMY 2003-166472 communique (the 10th page, the 10th figure)
But, because the ejection space of intermediate receptacle is the space that equally enlarges that does not have veil, therefore if to ejection space ejection refrigeration agent, then since sometimes under specific revolution its ripple component can not decay and resonate, therefore have the situation of the pressure oscillation increase in ejection space.Especially when its specific running revolution of compressor was high, pressure oscillation might further increase.If pressure oscillation increases, then because the kinergety that pressure oscillation causes is dissipated as frictional heat at the refrigerant flow path wall, energy loss increases, and therefore becomes the reason that causes freeze cycle achievement coefficient (COP) to reduce.Technology in the past such as patent documentation 1 grade is not considered such pressure oscillation, answers room for improvement thereby the energy efficiency of rotary compressor exists.
Summary of the invention
Problem of the present invention is, realizes a kind of rotary compressor that is more suitable for improving in the pressure oscillation in the generation of the ejection space of intermediate receptacle is suppressed energy efficiency.
In order to solve above-mentioned problem, rotary compressor of the present invention is characterized in that,
Comprise:
Rotary type low voltage side press part, it compresses refrigeration agent;
Rotary type high pressure side press part, its compression section with respect to this low voltage side press part compresses refrigeration agent with antiphase; With
Intermediate receptacle, it is communicated in the refrigeration agent ejiction opening of described low voltage side press part and the refrigeration agent of described high pressure side press part attracts mouth,
The inner space of described intermediate receptacle is divided at least two spaces by isolating part, attract mouth at the refrigeration agent ejiction opening of the described low voltage side press part of a side spatial communication and the refrigeration agent of described high pressure side press part, form the refrigerant flow path that links described two spaces at described isolating part.
In this case, intermediate receptacle can form, and has: the end plate portion of circular plate type; Outside wall portions, it erects and divides the Zhou Fangxiang in ejection space at axle direction from the peripheral portion of end plate portion; The supplementary bearing of tubular, its central authorities in end plate portion erect on axle direction; With inaccessible plate, it is faced and the forward end opening of inaccessible outside wall portions mutually with end plate portion.Isolating part herein is to be erected at periphery wall from supplementary bearing and to erect the beam of setting at the plate face of end plate portion, and this beam can form, from the axle direction size of end plate portion less than outside wall portions, and inaccessible plate between form refrigerant flow path.
That is, the refrigeration agent ejiction opening of low voltage side press part and the refrigeration agent of high pressure side press part attract a mouthful side's who is communicated with a space, become the main flow side space of the main flow circulation of refrigeration agent.In addition, via another space of isolating part connection, become the anti-main flow side space of the ripple component inflow and outflow of refrigeration agent in main flow side space.
Thus, if spray refrigeration agent to intermediate receptacle from the low voltage side press part, then the main flow of refrigeration agent attracted to the high pressure side press part after flowing through main flow side space, but part or all of the ripple component of the refrigeration agent in this process, in anti-main flow side space inflow and outflow.That is, anti-main flow side space performance is the effect of buffer as the acoustic resonator of the so-called empty formula of the resonance of the ripple component that prevents refrigeration agent.Thus, owing to suppress the resonance of ripple component in the ejection space, therefore be suppressed at the pressure oscillation that the ejection space produces.Consequently, can reduce the energy loss that causes owing to pressure oscillation and improve energy efficiency.
In addition, preferably, supplementary bearing is that the external diameter by the end panel part side forms greater than the wide diameter portion of the external diameter of forward end, isolating part from the axle direction size of end plate portion less than wide diameter portion.
In addition, isolating part is formed with in forward end: the parallel portion parallel with the plate face of end plate portion; Along with from the inner circumference edge of parallel portion towards axle direction and to the oblique interior all sides tapering of supplementary bearing inclination; With along with from the inner circumference edge of parallel portion towards axle direction and to the oblique outer circumferential side tapering of outside wall portions inclination, refrigerant flow path can form the trapezoidal opening in cross section that is marked off by parallel portion, interior all sides tapering, outer circumferential side tapering and inaccessible plate.That is, refrigerant flow path, along with towards axle direction and A/F increase gradually etc., can make A/F with a certain change width.In other words, by the angle of inclination in all sides tapering in adjusting or outer circumferential side tapering, the size of flow path cross sectional area that can the inching refrigerant flow path.Therefore, be not limited to specific running revolution, and can reducing pressure oscillation in the running revolution on a large scale.
In addition, intermediate receptacle can will be erected at periphery wall from supplementary bearing and erects the enhancing beam of setting at the plate face of end plate portion, is arranged at the opposing party's who is marked off by described isolating part space.Enhancing herein forms with beam, from the axle direction size of end plate portion less than isolating part.Therefore thus, can improve the rigidity of intermediate receptacle, can suppress because the distortion that the load of concluding key element during based on pressure load or assembling causes.
According to the present invention, can realize being more suitable for improving the rotary compressor of energy efficiency in the pressure oscillation in the generation of the ejection space of intermediate receptacle is suppressed.
Description of drawings
Fig. 1 is the sectional arrangement drawing of the structure of the expression rotary compressor that is suitable for an embodiment of the invention;
Fig. 2 is the low voltage side press part of presentation graphs 1 and the figure of high pressure side press part;
Fig. 3 is a worm's eye view of observing the intermediate receptacle of Fig. 1 from downside;
Fig. 4 is the A-A sectional drawing of the intermediate receptacle of Fig. 3;
Fig. 5 is the figure of the flow direction of the refrigeration agent in the ejection space of intermediate receptacle of presentation graphs 1;
Fig. 6 compares the pressure amplitude of the intermediate receptacle of Fig. 1 and the figure that represents with conventional art;
Fig. 7 is the B-B sectional drawing of the intermediate receptacle of Fig. 3;
Fig. 8 is the C-C sectional drawing of the intermediate receptacle of Fig. 3;
Fig. 9 is the D-D sectional drawing of the intermediate receptacle of Fig. 3;
Figure 10 is the plan view of the lid of Fig. 1 or Fig. 4;
Figure 11 is the elastomeric sectional drawing of Fig. 1 or Fig. 4;
Figure 12 is the figure of measurement result of variance ratio of the freeze cycle achievement coefficient (COP) of the expression air conditioner that is suitable for an embodiment of the invention;
Figure 13 is other the sectional drawing of first example that expression is suitable for intermediate receptacle of the present invention;
Figure 14 is other the sectional drawing of second example that expression is suitable for intermediate receptacle of the present invention.
Among the figure:
The 1-rotary compressor; 10-low voltage side press part; 12-high pressure side press part; 14-refrigeration agent ejiction opening; The 16-refrigeration agent attracts mouth; The 18-intermediate receptacle; 20-sprays the space; 20a-main flow side space; The anti-main flow side of 20b-space; The 20c-refrigerant flow path; The 22-isolating part.
Embodiment
With reference to accompanying drawing a mode of execution that is suitable for rotary compressor of the present invention is described.Fig. 1 is the sectional arrangement drawing of structure of the rotary compressor of expression present embodiment.Fig. 2 is the low voltage side press part of presentation graphs 1 and the figure of high pressure side press part.Fig. 3 is a worm's eye view of observing the intermediate receptacle of Fig. 1 from downside.Fig. 4 is the A-A sectional drawing of the intermediate receptacle of Fig. 3.
As shown in Figure 1, be applicable to the rotary compressor 1 of freezing cycle device such as air conditioner, have the two stage compressor structure of interim ground compressed refrigerant.More particularly, rotary compressor 1 has: the helicoid low voltage side press part 10 of compressed refrigerant (for example R410A); With respect to the compression section of low voltage side press part 10 helicoid high pressure side press part 12 with the antiphase compressed refrigerant; And have the intermediate receptacle 18 that attracts mouthful 16 inner spaces that are communicated with 20 (hereinafter referred to as spraying space 20) with the refrigeration agent of the refrigeration agent ejiction opening 14 of low voltage side press part 10 and high pressure side press part 12.
At this, be applicable to the intermediate receptacle 18 of rotary compressor 1, as Fig. 2～shown in Figure 4, ejection space 20 is two space 20a, 20b by isolating part 22 zonings for example.And, be communicated with the refrigeration agent ejiction opening 14 of low voltage side press part 10 and the refrigeration agent attraction mouth 16 of high pressure side press part 12 at a side space 20a (hereinafter referred to as main flow side space 20a), isolating part 22 is formed with the refrigerant flow path 20c of the space 20b (hereinafter referred to as anti-main flow side space 20b) that links main flow side space 20a and the opposing party.
That is, intermediate receptacle 18 has: the refrigeration agent ejiction opening 14 of connection low voltage side press part 10 and the refrigeration agent of high pressure side press part 12 attract the main flow side space 20a of mouth 16; With via main flow side space 20a and isolating part 22 and the anti-main flow side space 20b that is distinguished, it is refrigerant flow path 20c that isolating part 22 herein is formed with the opening that is communicated with main flow side space 20a and anti-main flow side space 20b.Thus, because anti-main flow side space 20b performance is the effect of buffer as the acoustic resonator of the so-called empty formula of the resonance of the ripple component that prevents refrigeration agent, therefore can be suppressed at the pressure oscillation that ejection space 20 produces and improves energy efficiency.
Rotary compressor 1 to present embodiment describes in further detail.As shown in Figure 1, rotary compressor 1 has been taken in seal container 26: motor 24, end plate portion 38, high pressure side press part 12, intermediate isolating plate 13, low voltage side press part 10 and intermediate receptacle 18.Particularly, seal container 26 is divided into via end plate portion 38: dispose the confined space 39 of motor 24 and dispose low voltage side press part 10 and space that key element such as compression such as the rotation of high pressure side press part 12 etc. is used.Rotation compression key element side is from motor 24 sides stacked high pressure side press part 12, intermediate isolating plate 13, low voltage side press part 10, intermediate receptacle 18 and fix by concluding key element 15 (for example being bolt) one on axle direction successively.
Seal container 26 has: the body portion 28 of tubular; The roughly bowl-shape cap 29 that the opening of motor 24 sides of body portion 28 is carried out locking; The bottom 30 that the opening of low voltage side press part 10 sides of body portion 28 is carried out locking.Cap 29 disposes the spraying pipe 31 that ejection is compressed into the refrigeration agent of high pressure P d.In addition, for convenience of explanation, the axle direction of body portion 28 suitably is called longitudinal direction, will suitably be called transverse direction with the substantially horizontal of axle direction quadrature.In addition, will on axle direction, suitably be called upside from body portion 28 towards the direction of cap 29 sides, will the direction of 30 sides suitably be called downside towards the bottom on axle direction from body portion 28.
Motor 24 is configured in the confined space 39 that the upside in seal container 26 is distinguished by end plate portion 38.This motor 24 has: the stator of installing with ring-type along the inner peripheral surface of seal container 26 32 as stator; Leave the rotor 34 that is inserted into configuration with gap as gyrator in the inboard of stator 32; The upper end portion is installed on the running shaft 36 of rotor 34 by axle.Running shaft 36 is provided with two eccentric parts in the part of forward end, is eccentric part 42 and the low eccentric part 44 that compresses usefulness that high compression is used.Eccentric part 42 is herein more relying on axle direction upside staggered positions than eccentric part 44 and is being provided with, and its eccentric direction is opposite directions, is that phase difference for example is 180 degree with respect to eccentric part 44.
End plate portion 38 is the plate member that wait the ring-type that is fixed along the inner peripheral surface of seal container 26 by welding.This end plate portion 38, the main bearing cylindraceous 40 of axle supporting rotating shaft 36 erects upward and is formed at central authorities.End plate portion 38 is formed with the ejiction opening 46 that has connected on thickness direction in addition.Dispose ejection valve 48 at this ejiction opening 46.In addition, end plate portion 38 thereon the central configuration of end face have the ejection cover 50.It is the hollow and annular parts that surround running shaft 36 that ejection covers 50, and its inner space is communicated with ejiction opening 46.In addition, ejection is covered 50 parts in motor 24 sides and is formed with ejiction opening 51.
High pressure side press part 12 is by end plate portion 38 and 13 clampings of intermediate isolating plate and dispose.This high pressure side press part 12 as shown in Figures 1 and 2, has: the cylinder 52 of approximate circle tubular, and it has the part of the external diameter identical with the internal diameter of seal container 26; Roller 54 cylindraceous, it is embedded in the periphery of the eccentric part 42 that is positioned at cylinder 52; The wing 56, its front end are connected to the outer circumferential face of roller 54 and can be supported on cylinder 52 by elastic force applying mechanism (for example being helical spring) with advancing and retreat; Attract mouth 16 with refrigeration agent, it connects on the direction of footpath and is communicated in the cylinder 52.Cylinder 52 is herein stopped up inner space 58 by the upper-end surface clamping of the lower end surface of end plate portion 38 and intermediate isolating plate 13.And the wing 56, by under the state of the outer circumferential face that is contacted with the roller 54 that rotates of matching with the eccentric motion of eccentric part 42, the motion of advancing and retreat, thereby refrigeration agent pressing chamber and refrigeration agent suction chamber are divided in the inner space 58 of cylinder 52.In addition, the refrigeration agent suction chamber is communicated with the ejection space 20 of intermediate receptacle 18 via the intermediate flow passage 60 that is connected in refrigeration agent attraction mouth 16.In addition, the refrigeration agent pressing chamber is communicated with confined space 39 via the ejiction opening 46 that is formed at end plate portion 38.
Intermediate isolating plate 13 is the inaccessible plates that are clamped between high pressure side press part 12 and the low voltage side press part 10.This intermediate isolating plate 13 is formed with the through hole of inserting logical running shaft 36 in central authorities.The axle center of this through hole is roughly consistent with running shaft.
Low voltage side press part 10 is by intermediate isolating plate 13 and intermediate receptacle 18 clampings and dispose.This low voltage side press part 10 as shown in Figures 1 and 2, has: the cylinder 62 of approximate circle tubular, and it has the part of the external diameter identical with the internal diameter of seal container 26; Roller 64 cylindraceous, it is embedded in the periphery of the eccentric part 44 that is positioned at cylinder 62; The wing 66, its front end are connected to the outer circumferential face of roller 64 and can be supported on cylinder 62 by elastic force applying mechanism (for example being helical spring) with advancing and retreat; Attract mouth 70 with refrigeration agent, it connects on the direction of footpath and is communicated in the cylinder 62.Cylinder 62 is herein stopped up inner space 71 by the upper-end surface clamping of the lower end surface of intermediate isolating plate 13 and intermediate receptacle 18.And the wing 66, by under the state of the outer circumferential face that is contacted with the roller 64 that rotates of matching with the eccentric motion of eccentric part 44, the motion of advancing and retreat, thereby refrigeration agent pressing chamber and refrigeration agent suction chamber are divided in the inner space 71 of cylinder 62.The refrigeration agent suction chamber flows into the gas refrigerant of discharging from the instrument class (for example being refrigerant evaporator) of freezing cycle device via the refrigerant piping 72 that is connected with refrigerant suction port 70.The refrigeration agent pressing chamber is communicated in the intermediate receptacle 18.
Intermediate receptacle 18 is temporary transient storages from the drum ladle of the refrigeration agent of low voltage side press part 10 ejections.More particularly, as shown in Figure 1, intermediate receptacle 18 is containers of spill, and it has: the discoideus end plate portion 74 of joining with the lower end surface of low voltage side press part 10; Below the mediad of end plate portion 74, erect the supplementary bearing cylindraceous 43 of formation; Spray the outside wall portions 78 of the Zhou Fangxiang in space 20 downwards from the outstanding differentiation of the peripheral portion of end plate portion 74; Connect the refrigeration agent exhaust port 79 of outside wall portions 78 in the horizontal direction.That is, intermediate receptacle 18 is with respect to the low voltage side press part 10 sides container of the spill of opening in the opposite direction.In addition, end plate portion 74 connects on thickness direction and is formed with: the refrigeration agent ejiction opening 14 that is communicated with the refrigeration agent pressing chamber of low voltage side press part 10.Refrigeration agent ejiction opening 14 disposes ejection valve 80.In addition, refrigeration agent exhaust port 79 disposes: will spray the intermediate flow passage 60 that space 20 is communicated with the refrigeration agent suction chamber of high pressure side press part 12.Such intermediate receptacle 18 disposes: the inaccessible plate of the annular plate of the opening of obstruction lower end surface promptly covers 82.
Elemental motion for the rotary compressor 1 of such formation describes.The arrow of Fig. 1 is represented the flow direction as the gas refrigerant of working fluid.The gas refrigerant of the low pressure Ps that discharges from the instrument class (for example being refrigerant evaporator) of freezing cycle device attracted to via refrigerant piping 72 in the cylinder 62 of low voltage side press part 10.The gas refrigerant that has been attracted, the off-centre rotation by roller 64 and in the refrigeration agent pressing chamber of cylinder 62, being compressed.If the pressure of this refrigeration agent pressing chamber reaches predetermined intermediate pressure Pm, then the gas refrigerant of refrigeration agent pressing chamber is ejected into ejection space 20 by the opening of ejection valve 80 via refrigeration agent ejiction opening 14.Ejection space 20 herein, owing to be the i.e. space that isolates of confined spaces 39 in the seal container 26, space that is isolated from the intermediate receptacle 18, so its internal pressure is pressed Pm in the middle of becoming basically.
Be ejected into the gas refrigerant in ejection space 20,, attract mouth 16 to attracted in the cylinder 52 of high pressure side press part 12 from refrigeration agent via intermediate flow passage 60.The gas refrigerant that has been attracted, the off-centre rotation by roller 54 and in the refrigeration agent pressing chamber of cylinder 52, being compressed.If the pressure of this refrigeration agent pressing chamber reaches predetermined high pressure P d, then the gas refrigerant of refrigeration agent pressing chamber sprays from ejiction opening 46 by the opening of ejection valve 48.Gas refrigerant after being ejected covers 50 ejiction opening 51 to confined space 39 outflows via ejection.The gas refrigerant that has flowed out after the gap of flowing through motor 24, is ejected into the instrument class (for example being refrigerant condenser) of freezing cycle device from spraying pipe 31.
In the compression process of the stage of such refrigeration agent, present embodiment, by in intermediate receptacle 18, possessing the anti-main flow side space 20b of resonant function, thereby reduce the pressure oscillation in the ejection space 20 that the phase difference owing to the suction process of the ejection process of low voltage side press part 10 and high pressure side press part 12 causes with empty formula.In addition, pressure oscillation, with the velocity of sound of refrigeration agent and the refrigeration agent spray volume of low voltage side press part 10, especially relevant with the volume in the running revolution of rotary compressor 1 and ejection space 20, but present embodiment mainly suppresses the resonance with the closely-related refrigeration agent ripple component of the velocity of sound of refrigeration agent.
At this, further middle container 18 is described in detail with reference to Fig. 2～Fig. 4.As shown in Figure 2, the ejection space 20 of intermediate receptacle 18 is divided into main flow side space 20a and anti-main flow side space 20b by isolating part 22.It is refrigerant flow path 20c that isolating part 22 is formed with the opening that is communicated with main flow side space 20a and anti-main flow side space 20b.That is, ejection space 20 is split into: be the anti-main flow side space 20b of the main flow side space 20a that mainly flows through of border, refrigeration agent and the time fluctuation composition that mainly flows through refrigeration agent with refrigerant flow path 20c.And main flow side space 20a strides across isolating part 22 and is communicated with anti-main flow side space 20b.Anti-main flow side space 20b herein comes in and goes out via refrigerant flow path 20c because of refrigeration agent, plays the function of the acoustic resonator of empty formula.
More particularly, intermediate receptacle 18 is sintered components of cast component or iron system, and as shown in Figures 3 and 4, end plate portion 74, outside wall portions 78 and supplementary bearing 43 are by one-body molded.That is, intermediate receptacle 18 forms the roughly concavity of an end face at lid 82 side openings.
End plate portion 74 is the plectanes that are formed with pedestal 84, and described pedestal 84 is used to be provided with the refrigeration agent ejiction opening 14 and the ejection valve 80 of low voltage side press part 10.In addition, outside wall portions 78 forms the general cylindrical shape shape, divides the Zhou Fangxiang in ejection space 20.This outside wall portions 78, the surface of contact 81 that forms abreast with the plate face of end plate portion 74 joins with lid 82.In addition, surface of contact 81 forms by mould-forming or cutting, grinding.In addition, outside wall portions 78 connects on axle direction and is formed with the hole 86 of concluding key element 15 usefulness of a plurality of (for example being four).These a plurality of holes 86 are uniformly-spaced to be formed on the same circumference.In addition, outside wall portions 78 forms and makes inner circle wall concavo-convex petal-shaped on the direction of footpath.More particularly, the inner circle wall of outside wall portions 78, the inboard concavity of radius vector direction ground forms and disposes the part in hole 86, the part radius vector direction outside convex ground formation between hole 86 and another hole 86 adjacent with this hole.By so the inner circle wall of outside wall portions 78 being formed petal-shaped, thereby can avoid hole 86 as far as possible and guarantee to spray the volume in space 20.In addition, the volume in ejection space 20 herein is greater than the refrigeration agent spray volume of low voltage side press part 10.Therefore, during to ejection space 20 ejection refrigeration agents, can suppress to spray the overcompression loss in the space 20 from low voltage side press part 10.
Supplementary bearing 43 the central authorities of end plate portion 74 with the approximate circle tubular erect and form.This supplementary bearing 43 is to be formed with stepped part on the periphery wall at the face of outside diameter.That is, supplementary bearing 43 is to be formed by the external diameter of the end plate portion 74 sides wide diameter portion greater than the external diameter of lid 82 sides.This stepped part has the relative tabular surface 88 in plane with lid 82.Tabular surface 88 is height recesses less than the surface of contact 81 of outside wall portions 78.Sandwich flexible body 90 being formed at tabular surface 88 and covering in the gap between 82.In addition, alleged height is to be the axial size of benchmark with end plate portion 74 in the present embodiment.
In addition, supplementary bearing 43 is formed with stepped part by the internal diameter of end plate portion 74 sides less than the internal diameter that covers 82 sides.That is, supplementary bearing 43, the contacting part 92 at end plate portion 74 sides formation axle supporting rotating shaft 36 carries out the non-contact portion 94 that axle supports to running shaft 36 in the formation of lid 82 sides.At this, the tabular surface 88 that forms at the periphery wall of supplementary bearing 43 is positioned at the outer peripheral portion of non-contact portion 94.Thus, owing to absorbed by non-contact portion 94, therefore can reduce the frictional force between supplementary bearing 43 and the running shaft 36 from the pressure load or the clamping load of lid 82 or elastomer 90.In addition, tabular surface 88 is as the part of intermediate receptacle 18 and by one-body molded, but also can form by machinings such as cuttings.
And the intermediate receptacle 18 of present embodiment shown in Fig. 3 and Fig. 4 etc., is formed with isolating part 22, and this isolating part 22 will spray space 20 and be divided into main flow side space 20a and anti-main flow side space 20b.Isolating part 22 as shown in Figure 3, is to be erected on the periphery wall 78 in the footpath direction from supplementary bearing 43 and to erect beam on the lower end surface that is arranged at end plate portion 74.That is, isolating part 22 is the weir plates of essentially rectangular section that link the madial wall of the outer side wall of supplementary bearing 43 and outside wall portions 78.In addition, in the present embodiment, though at the center that links supplementary bearing 43 with link on the straight line at center in hole 86 of usefulness and form two beams, also can be and form plural beam radially from supplementary bearing 43.In a word, be divided into main flow side space 20a and anti-main flow side space 20b as long as will spray space 20 by plural beam.
Such isolating part 22, as shown in Figure 4, and lid 82 between to form open profile be roughly trapezoidal refrigerant flow path 20c.More particularly, isolating part 22 is formed with in forward end: parallel portion 22a, and its height M is less than the surface of contact 81 of outside wall portions 78 and parallel with the lower end surface of end plate portion 74; In all sides tapering 22b, its along with from the inner circumference edge of parallel portion 22a towards axle direction and oblique to supplementary bearing 43 inclinations; And outer circumferential side tapering 22c, its along with from the outer periphery of parallel portion 22a towards axle direction and oblique to outside wall portions 78 inclinations.Interior all sides tapering 22b herein is the plane of inclination that links the outer periphery of the inner circumference edge of parallel portion 22a and tabular surface 88.In addition, outer circumferential side tapering 22c is the plane of inclination that the outer periphery of parallel portion 22a is linked to the inner circumference edge of outside wall portions 78.That is, by parallel portion 22a, interior all sides tapering 22b, outer circumferential side tapering 22c with cover 82 spaces that mark off and become refrigerant flow path 20c.In addition, interior all sides tapering 22b herein and the angle of inclination of outer circumferential side tapering 22c for example are 45 degree with respect to running shaft 36, but can change as required.That is, when needing to adjust the flow path cross sectional area S of refrigerant flow path 20c, as long as change the height of parallel portion 22a or the angle of inclination of interior all sides tapering 22b and outer circumferential side tapering 22c.
Fig. 5 is the figure of the flow direction of the refrigeration agent in the ejection space 20 of intermediate receptacle 18 of presentation graphs 1.As shown in Figure 5, if spray gas refrigerants via refrigeration agent ejiction opening 14 to intermediate receptacle 18 from low voltage side press part 10, then the main flow of refrigeration agent is after having flow through main flow side space 20a, attracted to high pressure side press part 12 via refrigeration agent exhaust port 79, but the ripple component of refrigeration agent is the refrigeration agent variance components part or all, in the space 20b inflow and outflow of anti-main flow side.That is, anti-main flow side space 20b, performance is the effect of buffer as the acoustic resonator of the so-called empty formula of the resonance of the ripple component that prevents refrigeration agent.Thus, owing to be suppressed at the resonance of the ripple component in the ejection space 20, therefore be suppressed at the increase of the pressure oscillation of ejection space 20 generations.Consequently, reduce the energy loss that causes because of pressure oscillation, can improve energy efficiency.
In a word, ejection space 20 is the anti-main flow side space 20b of the effect of border and the acoustic resonator that plays empty formula owing to have with refrigerant flow path 20c, therefore is suppressed at the pressure oscillation of the intermediate pressure Pm of ejection space 20 generations.
Fig. 6 compares the pressure amplitude of the intermediate receptacle 18 of present embodiment and the figure that represents with conventional art.The transverse axis of Fig. 6 is represented the running revolution (min of rotary compressor 1 -1), the longitudinal axis is represented the pressure amplitude (MPa) of 18 pairs of running revolutions of intermediate receptacle.As shown in Figure 6, along with the running revolution from minimum revolution increases, pressure amplitude increase.And in the prior art, the running revolution is for example at 4000 (min -1)～6000 (min -1) scope internal pressure amplitude become very big.That is, because the scope of general running revolution for example is 1000 (min -1)～8000 (min -1), therefore in the prior art, pressure amplitude relatively increases in high rotary side as can be known.This point according to present embodiment, owing to can reduce the maximum of the pressure amplitude of high rotary side, therefore improves freeze cycle achievement coefficient (COP), is suppressed at the noise and the vibration that produce in the rotary compressor 1.
In addition, according to present embodiment, owing to the A/F that makes refrigerant flow path 20c along with it is increased etc. gradually, make its A/F with a certain change width, therefore be not limited to certain running revolution (frequency) and can reducing pressure oscillation in the running revolution on a large scale.More particularly, intermediate receptacle 18 about present embodiment, the height N of parallel portion 22a by changing isolating part 22, or the tilt angle of all sides tapering 22b and outer circumferential side tapering 22c in changing, thereby the size of flow path cross sectional area S that can inching refrigerant flow path 20c.For example, if flow path cross sectional area S is diminished, then in the scope of high rotary side, bring into play the resonant function of anti-main flow side space 20b.In addition, if flow path cross sectional area S is increased, then in the scope of low rotary side, bring into play the resonant function of anti-main flow side space 20b.But,,, therefore have the situation of not bringing into play resonant function and can't suppressing pressure oscillation fully then because ejection space 20 is practically identical with the space in the past of the same expansion if flow path cross sectional area S is excessively increased.Therefore, for the size of flow path cross sectional area S, be preferably formed to more than the regulation area.The appropriate value of flow path cross sectional area S for example can be obtained by actual measurement.
In addition, the intermediate receptacle 18 of present embodiment as shown in Figures 3 and 4, is provided with second beam 96 as reinforcing member at anti-main flow side space 20b.This beam 96, be set up in periphery wall 78 from supplementary bearing 43 in the footpath direction and be integrally formed on this point of lower end surface of end plate portion 74, similar with isolating part 22, but different on this point with height L parallel surface littler than the height N of the parallel surface 22a of isolating part 22.By such beam 96 is set, owing to can improve the rigidity of intermediate receptacle 18, therefore can suppress because based on pressure load or the distortion that causes of the load of concluding key element 15 when assembling.
Further, middle container 18 is described.Fig. 7 is the B-B sectional drawing of the intermediate receptacle of Fig. 3.This Fig. 7 is the figure of the form of the isolating part 22 in the expression B-B section.As shown in Figure 7, isolating part 22 forms along with enlarging to the bottom towards end plate portion 74, base portion.That is, isolating part 22 is formed with the shank 98 as reinforcing member in the connecting part with end plate portion 74.Thus, even reduce under the situation of frictional loss, also can guarantee the rigidity of isolating part 22 in the flow path length that by the thickness that reduces isolating part 22 is refrigerant flow path 20c.
Fig. 8 is the C-C sectional drawing of the intermediate receptacle of Fig. 3.This Fig. 8 is the figure of the form of the beam 96 in the expression C-C section.As shown in Figure 8, beam 96 forms along with enlarging to the bottom towards end plate portion 74, base portion.That is, beam 96 is formed with the shank 100 as reinforcing member in the connecting part with end plate portion 74.Thus, even under the situation of the refrigeration agent aeration resistance that reduces anti-main flow side space 20b by the thickness that reduces beam 96,, therefore can reduce the distortion of intermediate receptacle 18 owing to also can guarantee the rigidity of beam 96.
Fig. 9 is the D-D sectional drawing of the intermediate receptacle of Fig. 3.That is, Fig. 9 shows the relation of the height L of the height N of parallel portion 22a of height M, isolating part 22 of the surface of contact 81 of outside wall portions 78 and beam 96.As shown in Figure 9, the height N by making parallel portion 22a guarantees the flow path cross sectional area S of refrigerant flow path 20c less than the height M of surface of contact 81.In addition, the height L by making beam 96 is less than the height N of parallel portion 22a, and can improve the rigidity of intermediate receptacle 18 and can guarantee the volume V of anti-main flow side space 20b.
Figure 10 is the plan view of the lid 82 of Fig. 1 or Fig. 4.As shown in figure 10, lid 82 be by punch process be punched moulding the parts of circular plate type.The hole 102 of concluding key element 15 usefulness that this lid 82 is formed with a plurality of (for example being four) connects on the thickness of slab direction.These a plurality of holes 102 to be uniformly-spaced being formed on the same circumference, and are corresponding with the position and the number in the hole 86 of intermediate receptacle 18.In addition, lid 82 is formed with the hole 104 that connects in the thickness of slab direction in plate face central authorities.This hole 104 is used for the fore-end by the non-contact portion 94 of supplementary bearing 40.More particularly, as Fig. 1 and shown in Figure 4, it is identical with the external diameter of the non-contact portion 94 of supplementary bearing 40 that hole 104 forms its diameter.That is,, then cover 82 and contact with non-contact portion 94 if the fore-end of non-contact portion 94 is embedded into hole 104.And, by in the gap between lid 82 and the tabular surface 88, sandwiching elastomer 90, thereby form sealing surface.
Figure 11 is the sectional drawing of the elastomer 90 of Fig. 1 or Fig. 4.As shown in figure 11, elastomer 90 is that copper part is carried out punch process and the belleville spring of the roughly annular taper platform shape that forms.This elastomer 90 as shown in Figure 4, is configured on the tabular surface 88 along the front end periphery of supplementary bearing 40.That is, elastomer 90 is sandwiched in the gap of tabular surface 88 and lid 82.When configuration elastomer 90, the bottom surface of elastomer 90 and the plane contact of covering 82.As elastomer 90 herein, can be suitable for the packing ring (gasket) of circular plate type or O shape ring etc.But when using packing ring, preferably be suitable for more the rubber material or the resinous wood of easy deformation.
Figure 12 is the figure of measurement result of the variance ratio of the freeze cycle achievement coefficient (COP) of expression when having controlled the flow path cross sectional area S of refrigerant flow path 20c.The transverse axis of Figure 12 is represented the volume V (mm of anti-main flow side space 20b 3) to the flow path cross sectional area S (mm of refrigerant flow path 20c 2) ratio (S/V).The longitudinal axis represents that the COP of air conditioner is with respect to the variance ratio (%) than (S/V).In addition, COP herein is meant the regulating power that removes air conditioner with input.In addition, the COP when than (S/V) serving as zero has carried out relative evaluation as benchmark.
As shown in figure 12, the variance ratio of the COP of air conditioner is along with increasing and sharply increase from zero than (S/V), with a certain be border and reducing gradually than (S/V).That is, make than (S/V) from zero increase initial, owing to along with pass through flow path cross sectional area S (mm than the increase of (S/V) 2) volume of the cooling medium increase, so bring into play the resonant function of anti-main flow side space 20b, the result who therefore suppresses the pressure oscillation in ejection space 20 is the COP that has improved air conditioner.But, excessively be increased to when surpassing a certain value making than (S/V), because the zoning of anti-main flow side space 20b and main flow side space 20a thickens, so ejection space 20 becomes identical in fact with the space in the past of the same expansion, therefore can not suppress to spray the pressure oscillation in space 20 fully, the COP of air conditioner reduces.In addition, along with increasing, because the effect that improves based on the rigidity of the end plate portion 74 of isolating part 22 descends, therefore because the mechanical loss that the distortion of end plate portion 74 causes increase than (S/V).In view of such situation, hope be that the ratio (S/V) of present embodiment is for example with 0.1 * 10 -2(mm -1) be lower limit, for example with 2.0 * 10 -2(mm -1) be in the scope of CLV ceiling limit value.If in this scope, can access for example COP 1% or more raising effect in the evaluated error scope of the performance measurement device of general air conditioner.
More than, illustrated to be suitable for a mode of execution of rotary compressor 1 of the present invention, but be not limited thereto.
Figure 13 is other the sectional drawing of first example of the intermediate receptacle 18 of expression present embodiment.As shown in figure 13, this routine intermediate receptacle 18, on this point that forms with identical diameter on the axle direction, the mode of Fig. 4 that has formed the stepped part with tabular surface 88 with periphery wall at supplementary bearing 43 is different at the periphery wall of supplementary bearing 106.That is, this routine intermediate receptacle 18 is the containers that make the height of tabular surface 88 of Fig. 4 and junction surface 81 involutory.Therefore, the outer periphery portion of the lower end surface 108 of supplementary bearing 106 and the plane contact of covering 82.Isolating part 22 herein forms, and has: height is less than the parallel portion 22a of the lower end surface 108 of supplementary bearing 106; The inner circumference edge of parallel portion 22a is linked to interior all sides tapering 22g of the outer periphery of lower end surface 108; Be linked to the outer circumferential side tapering 22c of the inner circumference edge of outside wall portions 78 with outer periphery with parallel portion 22a.Thus, can guarantee at isolating part 22 and cover the flow path cross sectional area S of the refrigerant flow path 20c that forms between 82 the plane.In addition, the angle of inclination of interior all sides tapering 22g still is not limited thereto greater than outer circumferential side tapering 22c, adjusts as required to get final product.
Figure 14 is other the sectional drawing of second example of the intermediate receptacle of expression present embodiment.As shown in figure 14, this routine intermediate receptacle 18 is formed at refrigerant flow path 20c on this point of a part of isolating part 22, and the mode of Figure 13 in whole zone that is formed at isolating part 22 with refrigerant flow path 20c is different.That is, this routine intermediate receptacle 18, on this point of width less than isolating part 22 of refrigerant flow path 20c, the mode of Figure 12 identical with the width of refrigerant flow path 20c and isolating part 22 is different.In other words, the outer periphery portion of the front-end face of isolating part 22 and the plane contact of covering 82.Isolating part 22 herein forms, and has: height is less than the parallel portion 22a of the lower end surface 108 of supplementary bearing 106; The inner circumference edge of parallel portion 22a is linked to interior all sides tapering 22g of the outer periphery of lower end surface 108; With the outer circumferential side tapering 22h that tilt to lid 82 from the outer periphery of parallel portion 22a.Thus, because the raising of the rigidity of isolating part 22, so consequently the rigidity of intermediate receptacle 18 improves.
More than, according to present embodiment, by the resonant function that has empty formula at intermediate receptacle 18, thus the pressure pulsation of the intermediate pressure Pm in the inhibition intermediate receptacle 18, therefore improve freeze cycle achievement coefficient (COP), can be suppressed at the noise and the vibration that produce in the rotary compressor 1.

Claims (4)

1, a kind of rotary compressor is characterized in that,
Comprise:
Rotary type low voltage side press part, it compresses refrigeration agent;
Rotary type high pressure side press part, its compression section with respect to this low voltage side press part compresses refrigeration agent with antiphase; With
Intermediate receptacle, it is communicated in the refrigeration agent ejiction opening of described low voltage side press part and the refrigeration agent of described high pressure side press part attracts mouth,
The inner space of described intermediate receptacle is divided at least two spaces by isolating part, attract mouth at the refrigeration agent ejiction opening of the described low voltage side press part of a side spatial communication and the refrigeration agent of described high pressure side press part, form the refrigerant flow path that links described two spaces at described isolating part
Described intermediate receptacle has:
The end plate portion of circular plate type;
Outside wall portions, it erects at axle direction from the peripheral portion of this end plate portion and divides the Zhou Fangxiang in described ejection space;
The supplementary bearing of tubular, its central authorities in described end plate portion erect on axle direction; With
Inaccessible plate, it is faced mutually with described end plate portion, the forward end opening of inaccessible described outside wall portions,
Described isolating part is to be erected at described periphery wall from described supplementary bearing and to erect the beam of setting at the plate face of described end plate portion,
This beam is formed axle direction size from described end plate portion less than described outside wall portions, and described inaccessible plate between form described refrigerant flow path.
2, rotary compressor according to claim 1 is characterized in that,
Described supplementary bearing is to be formed by the external diameter of the described end panel part side wide diameter portion greater than the external diameter of forward end, described isolating part from the axle direction size of described end plate portion less than described wide diameter portion.
3, according to the rotary compressor shown in claim 1 or 2, it is characterized in that,
Described isolating part is formed with in forward end:
The parallel parallel portion of plate face with described end plate portion;
Along with from the inner circumference edge of this parallel portion towards axle direction and to the oblique interior all sides tapering of described supplementary bearing inclination; With
Along with from the inner circumference edge of described parallel portion towards axle direction and to the oblique outer circumferential side tapering of described outside wall portions inclination,
Described refrigerant flow path is the trapezoidal opening in cross section that is marked off by described parallel portion, described interior all sides tapering, described outer circumferential side tapering and described inaccessible plate.
4, rotary compressor according to claim 1 and 2 is characterized in that,
Described intermediate receptacle is provided with in the opposing party's who is marked off by described isolating part space: is erected at described periphery wall from described supplementary bearing and erects the enhancing beam of setting at the plate face of described end plate portion,
Described enhancing with beam from the axle direction size of described end plate portion less than described isolating part.
CNB2006101399372A 2005-10-26 2006-09-27 Rotary compressor Expired - Fee Related CN100458165C (en)

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Effective date of registration: 20160901

Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor

Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd.

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Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc.

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Granted publication date: 20090204