CN106133321A - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
CN106133321A
CN106133321A CN201580008662.6A CN201580008662A CN106133321A CN 106133321 A CN106133321 A CN 106133321A CN 201580008662 A CN201580008662 A CN 201580008662A CN 106133321 A CN106133321 A CN 106133321A
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CN
China
Prior art keywords
cylinder
blade
cold
producing medium
annular piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201580008662.6A
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Chinese (zh)
Inventor
森下卓
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Fujitsu General Ltd
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Fujitsu General Ltd
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Publication of CN106133321A publication Critical patent/CN106133321A/en
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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/268—R32
    • 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
    • F04C2240/40—Electric motor
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The present invention provides a kind of rotary compressor, in this rotary compressor, if width of blade be W, the offset of eccentric part be e, vane nose radius of curvature be Rv, annular piston radius be Rro, the non-slip peak width of vane nose both sides be Wt, so that the non-slip peak width W of the vane nose both sides defined by following formula (A)tFor meeting the mode of the value of formula (B), set width of blade W and vane nose radius of curvature Rv: Wt=(W/2)-e × Rv/(Rv+Rro)…(A)0.3mm≤Wt≤0.6mm…(B)。

Description

Rotary compressor
Technical field
The present invention relates to the rotary compressor for air conditioner or fridge etc..
Background technology
As it is shown on figure 3, it is R that the vane nose of rotary compressor is formed as vane nose radius of curvaturevArc surface.As The crestal line portion that really this arc surface intersects to form with blade side abuts with the outer peripheral face of roller (annular piston), then can cause the different of roller Often abrasion.As shown in Figure 4, if setting roller to be positioned at the position of top dead centre as 0 °, then from top dead centre, revolve round the sun 90 ° and 270 ° at roller and Non-slip (noncontact) the peak width W of the position blade arrivedtFor minimum.In the past, in order to do not make the crestal line portion of blade with The outer peripheral face of roller abuts and makes roller produce inordinate wear, can reduce vane nose radius of curvature Rv, increase width of blade W (such as W =4mm), and by the non-slip peak width W of bladetIt is set to 0.8mm～1.0mm.
But, the abutting part (roller blade sliding area) of vane nose and roller, relatively low and carry out at external air temperature Under conditions of during heating, the low-pressure side of such refrigerant gas is higher with on high-tension side pressure ratio, due on high-tension side gas temperature Spend higher and gas flow minimizing, so the temperature of vane nose uprises, and be difficult to form oil film.Particularly, use and R410A Cold-producing medium is compared the R32 cold-producing medium that gas density is little and discharge temperature is high and be there is following problems: the sliding surface between blade and roller Temperature raise further compared with R410A cold-producing medium, at blade and roller, then produce inordinate wear, and cannot guarantee reliable Property.
As the rotary compressor of solution the problems referred to above, disclosed following rotary compressor in the past, comprising: gas Cylinder, it has suction inlet and outlet；Rotary shaft, it has the crank portion being arranged on cylinder-bore axis；Roller, it is arranged in bent axle Eccentric rotary is carried out between portion and cylinder；And blade, its move back and forth in the groove being arranged at cylinder and with roller outside Circumferential contact, in above-mentioned rotary compressor, starts the base of the reciprocating position anglec of rotation as roller with blade towards roller On time, the song that when anglec of rotation of roller is positioned at either one or both near 90 degree and in 270 degree, the contact surface of blade and roller has Rate is the curvature value below (referring for example to patent documentation 1) of roller.
Patent documentation 1: Japanese Unexamined Patent Publication 7-229488 publication
Summary of the invention
But, the historically conventional art in above-mentioned patent documentation 1, owing to vane nose face is different many by curvature Individual face is constituted, so there is the problem that production management is complex.Additionally, due to the radius of curvature for vane nose face is R Face and the connecting portion in the face with roller curvature value below for, it is necessary to its radius of curvature is set smaller than vane nose face Radius of curvature R, so the hertz stress of connecting portion (Hertzian stress) rises, may cause roller peripheral part to produce abnormal Abrasion.
The present invention completes in view of the foregoing, it is therefore intended that provide a kind of rotary compressor, its vane nose Face is not to be made up of different multiple of curvature, but uses simple shape, and blade and roller (annular piston) is durable Property high.
In order to solve the problems referred to above, realize goal of the invention, the present invention provides a kind of rotary compressor, comprising: compression Casing body, it is airtight and longitudinal housing, is provided with the discharge portion of cold-producing medium on top, lower side is provided with cold-producing medium Sucting；Compression unit, it is configured at the bottom of above-mentioned compressor housing, including: cylinder, it is in the form of a ring；End plate, it has axle Bearing portion and dump valve portion, close the one end of above-mentioned cylinder；End plate or central dividing plate, it has bearing portion, by above-mentioned cylinder The other end close；Annular piston, it is chimeric with the eccentric part of the rotary shaft supported by above-mentioned bearing portion, along above-mentioned cylinder Cylinder inner wall revolve round the sun in this cylinder, and between above-mentioned cylinder inner wall formed operating room；And blade, it is from being arranged at Abut with above-mentioned annular piston in being projected into above-mentioned operating room in the blade groove of above-mentioned cylinder, above-mentioned operating room is divided into suction Room and discharge chambe；And motor, it is configured at the top of above-mentioned compressor housing, drives above-mentioned compression via above-mentioned rotary shaft Portion, wherein, makes cold-producing medium pass above-mentioned sucting and sucks wherein, and it is interior from above-mentioned to make cold-producing medium pass above-mentioned compressor housing Discharge portion discharge, in above-mentioned rotary compressor, if width of blade be W, the offset of eccentric part be e, vane nose curvature Radius is Rv, annular piston radius be Rro, the non-slip peak width of vane nose both sides be Wt, so that by following formula (A) The non-slip peak width W of the vane nose both sides of definitiontFor meeting the mode of the value of formula (B), set width of blade W and leaf Sheet front end radius of curvature Rv:
Wt=(W/2)-e × Rv/(Rv+Rro)…(A)
0.3mm≤Wt≤0.6mm…(B)。
According to the present invention, play following effect: need not increase the width of blade, it is not required that reduce the offset of roller, Just can obtain the rotary compressor that the durability of blade and roller (annular piston) is high.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the rotary compressor representing the application present invention.
Fig. 2 is the cross-sectional view observed from the top of the first and second compression units.
Fig. 3 is the magnified partial view of Fig. 2.
Fig. 4 is the magnified partial view of Fig. 3.
Detailed description of the invention
Below, the embodiment of the rotary compressor that the present invention relates to is described in detail based on accompanying drawing.It addition, the present invention is not It is confined to this embodiment.
Embodiment
Fig. 1 is the longitudinal section of the embodiment representing the rotary compressor that the present invention relates to, and Fig. 2 is from embodiment One and second cross-sectional view observed of the top of compression unit.
As it is shown in figure 1, the rotary compressor 1 of embodiment includes: compression unit 12, it is configured at airtight longitudinal cylindrical shape The bottom of compressor housing 10；And motor 11, it is configured at the top of compressor housing 10, via rotary shaft 15 driving pressure Contracting portion 12.
The stator 111 of motor 11 forms cylindrical shape, and hot charging is fixed on the inner peripheral surface of compressor housing 10.The rotor of motor 11 The inside of 112 stators 111 being configured at cylindrical shape, hot charging is fixed on and mechanically connects motor 11 and the rotation of compression unit 12 Rotating shaft 15.
Compression unit 12 includes: the first compression unit 12S；And the second compression unit 12T, it is joined side by side with the first compression unit 12S Put, be laminated in the upside of the first compression unit 12S.As in figure 2 it is shown, first and second compression unit 12S, 12T have ring-type first With second cylinder 121S, 121T, it is radially provided with first and at first and second side protuberance 122S, 122T Two inlet hole 135S, 135T, first and second blade groove 128S, 128T.
As in figure 2 it is shown, at first and second cylinder 121S, 121T, be concentrically formed with circle with the rotary shaft 15 of motor 11 First and second cylinder inner wall 123S, 123T of shape.It is each configured with external diameter in first and second cylinder inner wall 123S, 123T Less than first and second annular piston 125S, 125T of cylinder bore diameter, at first and second cylinder inner wall 123S, 123T and first And second be formed between annular piston 125S, 125T suck refrigerant gas and compress it after the first and second works of discharging Make room 130S, 130T.
At first and second cylinder 121S, 121T, it is radially formed horizontal stroke from first and second cylinder inner wall 123S, 123T Across first and second blade groove 128S, 128T of the whole altitude range of cylinder, divide in first and second blade groove 128S, 128T Not chimeric in the way of free sliding have flat first and second blade 127S, 127T.
As in figure 2 it is shown, in the deep of first and second blade groove 128S, 128T, from first and second cylinder 121S, 121T Peripheral part be formed in the way of connecting with first and second blade groove 128S, 128T the first and second spring eye 124S, 124T.It is inserted into for pressing first and second blade 127S, 127T back sides at first and second spring eye 124S, 124T First and second leaf springs (not shown).
When rotary compressor 1 starts, due to the bounce of this first and second leaf spring, the first and second blades 127S, 127T are projected in first and second operating room 130S, 130T in first and second blade groove 128S, 128T, before it End abuts with the outer peripheral face of first and second annular piston 125S, 125T, thus by first and second blade 127S, 127T by the One and second operating room 130S, 130T be divided into first and second suction chamber 131S, 131T and the first and second discharge chambes 133S、133T。
Additionally, be formed with first and second pressure lead-in path 129S, 129T at first and second cylinder 121S, 121T, The deep of first and second blade groove 128S, 128T is connected in compressor housing 10 by it by the peristome R shown in Fig. 1, And import the refrigerant gas compressed in compressor housing 10, and by the pressure of refrigerant gas to the first and second leaves Sheet 127S, 127T apply back pressure.
In order to cold-producing medium be sucked into from outside first and second suction chamber 131S, 131T, at the first and second cylinders 121S, 121T be provided with make first and second suction chamber 131S, 131T and ft connection the first and second inlet hole 135S, 135T。
Additionally, as it is shown in figure 1, be configured with central dividing plate 140 between the first cylinder 121S and the second cylinder 121T, divide Go out the second operating room 130T of the first operating room 130S (with reference to Fig. 2) and the second cylinder 121T of the first cylinder 121S (with reference to figure 2) and closed.The upper end of the first cylinder 121S and the bottom of the second cylinder 121T are closed by central dividing plate 140.? The bottom of one cylinder 121S is configured with bottom plate 160S, is closed by the first operating room 130S of the first cylinder 121S.Additionally, The upper end of the second cylinder 121T is configured with upper head plate 160T, is closed by the second operating room 130T of the second cylinder 121T.Lower end The bottom of the first cylinder 121S is closed by plate 160S, and the upper end of the second cylinder 121T is closed by upper head plate 160T.
Being formed with countershaft bearing portion 161S at bottom plate 160S, the countershaft portion 151 of rotary shaft 15 is to rotate mode quilt freely Countershaft bearing portion 161S supports.Be formed with main shaft bearing portion 161T at upper head plate 160T, the main shaft part 153 of rotary shaft 15 with rotate from by Mode supported by main shaft bearing portion 161T.
Rotary shaft 15 has the first eccentric part 152S and the second eccentric part 152T of the 180 ° of phase place ground bias that offset one from another, the One eccentric part 152S is embedded in the first annular piston 125S of the first compression unit 12S, the second eccentric part to rotate mode freely 152T is embedded in the second annular piston 125T of the second compression unit 12T to rotate mode freely.
When rotary shaft 15 rotates, first and second annular piston 125S, 125T are along the first and second cylinder inner walls 123S, 123T in first and second cylinder 121S, 121T at the revolution clockwise of Fig. 2, the first and second blades 127S, 127T follow it and move back and forth.By this first and second annular pistons 125S, 125T and the first and second blades The motion of 127S, 127T, makes first and second suction chamber 131S, 131T and the appearance of first and second discharge chambe 133S, 133T Amassing and change continuously, compression unit 12 is continuously drawn into refrigerant gas and it is compressed discharge.
As it is shown in figure 1, be configured with lower silencer cover 170S in the downside of bottom plate 160S, and it is formed between bottom plate 160S Lower anechoic chamber 180S.And, the first compression unit 12S downward anechoic chamber 180S opening.That is, at first blade of bottom plate 160S Near 127S, it is provided with the first row by the first discharge chambe 133S of the first cylinder 121S and lower anechoic chamber 180S connects and portals 190S (with reference to Fig. 2), is configured with, at the first row 190S that portals, the reed valve type first preventing the refrigerant gas compressed from flowing backwards Dump valve 200S.
Lower anechoic chamber 180S is created as a ring-type chamber, is that the discharge side making the first compression unit 12S is through refrigeration A part for agent path 136 (with reference to Fig. 2) communication paths that connect interior with upper anechoic chamber 180T, this refrigerant passage 136 runs through Bottom plate 160S, the first cylinder 121S, central dividing plate the 140, second cylinder 121T and upper head plate 160T.Lower anechoic chamber 180S is permissible Reduce the pressure oscillation of discharging refrigerant gas.Additionally, it is overlapping with the first dump valve 200S, for limiting the first dump valve First dump valve compressed part 201S of the flexure valve opening amount of 200S is fixed by rivet together with the first dump valve 200S.First discharges Hole 190S, the first dump valve 200S and the first dump valve compressed part 201S constitute the first dump valve portion of bottom plate 160S.
It is formed as it is shown in figure 1, be configured with between silencer cover 170T, and upper head plate 160T in the upside of upper head plate 160T Upper anechoic chamber 180T.Near the second blade 127T of upper head plate 160T, it is provided with second discharge chambe of the second cylinder 121T The second row that 133T and upper anechoic chamber 180T connects portals 190T (with reference to Fig. 2), second row portal 190T be configured with prevent by Reed valve type the second dump valve 200T that the refrigerant gas of compression flows backwards.Additionally, overlapping with the second dump valve 200T, be used for Limit second dump valve compressed part 201T of flexure valve opening amount of the second dump valve 200T together with the second dump valve 200T by riveting Nail is fixing.Upper anechoic chamber 180T can reduce the pressure oscillation of discharging refrigerant.Second row portals 190T, the second dump valve 200T With the second dump valve portion that the second dump valve compressed part 201T constitutes upper head plate 160T.It addition, figure is shown without, rotary In the case of compressor is single air-cylinder type compressor, the upper and lower end portion of cylinder is closed by end plate respectively, in closed cylinder bottom End plate can be not provided with dump valve portion.
First cylinder 121S, bottom plate 160S, lower silencer cover 170S, the second cylinder 121T, upper head plate 160T, upper silencer cover 170T and central dividing plate 140 are connected to one by multiple bolts 175 etc. that run through.All-in-one-piece pressure is linked by running through bolt 175 grade Peripheral part in contracting portion 12, upper head plate 160T is fixed in compressor housing 10 by means of spot welds, and compression unit 12 is fixed on pressure Contracting casing body 10.
At the periphery wall of cylindric compressor housing 10, it is provided with first and second the most separatedly from bottom Through hole 101,102, passes for the first and second suction tubes 104,105.Additionally, at the lateral part of compressor housing 10, by The reservoir 25 that independent cylindric hermetic container is constituted is kept by reservoir support 252 and reservoir fixing band 253.
In the top center of reservoir 25, connect the system connecting tube 255 having the vaporizer with refrigerant loop to be connected, It is arranged at bottom through hole 257 bottom reservoir 25 to connect and have first and second low-pressure connection tube 31S, 31T, first and second One end of low-pressure connection tube 31S, 31T extends to the inner upper of reservoir 25, the other end and the first and second suction tubes 104, The other end of 105 connects.
The low pressure refrigerant of refrigerant loop is imported via reservoir 25 the first of first and second compression unit 12S, 12T With second low-pressure connection tube 31S, 31T, via first and second suction tube the 104,105 and first and second gas as sucting First and second inlet hole 135S, 135T (with reference to Fig. 2) of cylinder 121S, 121T connect.I.e., first and second inlet hole 135S, 135T is connected side by side with the vaporizer of refrigerant loop.
Connect at the top of compressor housing 10 and have the discharge pipe 107 as discharge portion, discharge pipe 107 and refrigerant loop Connect, higher pressure refrigerant gas is expelled to the condenser side of refrigerant loop.That is, first and second tap 190S, 190T It is connected with the condenser of refrigerant loop.
The lubricating oil of the height approximately reaching the second cylinder 121T it is sealed with in compressor housing 10.Additionally, lubricating oil Drunk up from the fuel feed pump 16 being installed on rotary shaft 15 bottom by the not shown pump blade being inserted into rotary shaft 15 bottom, In compression unit 12, circulation, is lubricated slide unit, and is sealed by the minim gap of compression unit 12.
Then, with reference to Fig. 3 and Fig. 4, the characteristic structural of the rotary compressor 1 of embodiment is illustrated.Fig. 3 is figure The magnified partial view of 2, Fig. 4 is the magnified partial view of Fig. 3.As shown in Figure 3 and Figure 4, when first and second blade 127S, 127T by Blade thrust P that produces based on back pressure and when being pressed against first and second annular piston 125S, 125T, produce by following formula And the Max.contact stress σ shown in formula (2) (1)max。
Several 1
a = 2 P π ( 1 - v V 2 E V + 1 - v r o 2 E r o ) / ( 1 R V + 1 R r o ) ... ( 1 )
σmax=2P/ (π a) ... (2)
Here, σmax: Max.contact stress；A: contact width；P: blade thrust；Rv: vane nose radius of curvature；Rro: Annular piston radius；Ev: paddles elastomeric coefficient；Ero: annular piston coefficient of elasticity；νv: blade Poisson's ratio；νro: annular piston is moored Pine ratio.
Additionally, the non-slip peak width W of the both sides, front end of first and second blade 127S, 127TtBy following formula (A) Represent (size relationships of the similar triangles of reference Fig. 4).
Wt=(W/2)-e × Rv/(Rv+Rro)…(A)
Here, Wt: the non-slip peak width of vane nose both sides；W: width of blade；The offset of e: eccentric part.
Rotary compressor 1 under harsh operating condition (such as external air temperature relatively low and when carrying out heating so Low-pressure side and the on high-tension side pressure ratio of refrigerant gas big the most relatively, the most on high-tension side gas temperature is higher and gas flow subtracts Under few operating condition), when first and second blade 127S, 127T and the contact of first and second annular piston 125S, 125T When stress increases, first and second blade 127S, 127T and first and second annular piston 125S, 125T can produce exception Abrasion, it is therefore desirable to reduce as much as possible by the Max.contact stress σ shown in formula (2)max。
In order to reduce Max.contact stress σmax, and reduce the width of blade W of first and second blade 127S, 127T, for Blade thrust P reducing back pressure based on the refrigerant gas in compressor housing 10 generation is effective (with reference to formula (2)). If additionally, increasing vane nose radius of curvature Rv, then can increase by shown in formula (1), the first and second blade 127S, The contact width a of 127T and first and second annular piston 125S, 125T (contact width a be the first and second blade 127S, The contact width in circumference that the junction of 127T and first and second annular piston 125S, 125T produces because of elastic deformation. Can only see contact point in the diagram.), therefore, it is possible to reduce by the Max.contact stress σ shown in formula (2)max。
But, if too increasing vane nose radius of curvature Rv, then shown in formula (A), the first and second blade 127S, The non-slip peak width W of the both sides, front end of 127TtCan become 0, and the vane camberline portion shown in Fig. 3 and the first and second rings The outer peripheral face contact of shape piston 125S, 125T, Max.contact stress σmaxGreatly, the inordinate wear of outer peripheral face is caused.
Therefore, even if in view of the making tolerance of first and second blade 127S, 127T, the first and second blade grooves The making tolerance of 128S, 128T, the existence of the factor such as flexure of first and second blade 127S, 127T, also by width of blade W and Vane nose radius of curvature RvIt is set to both sides, front end non-of first and second blade 127S, the 127T defined by formula (A) Sliding area width WtFor meeting the value of following formula (B), to prevent because of non-slip peak width WtBecome 0 and vane camberline portion with The outer peripheral face contact of first and second annular piston 125S, 125T.
0.3mm≤Wt≤0.6mm…(B)
By by non-slip peak width WtIt is set as meeting value (the non-slip peak width W of formula (B)tRatio is in background technology The value in the past recorded is narrow by more than 10%), width of blade W becomes the thinnest, and can be compressed by the blade that produce based on back pressure Power P reduces 20%, thus reduces Max.contact stress σmax。
The non-slip region width of the both sides, front end of first and second blade 127S, 127T by being defined by formula (A) Degree WtIt is set as meeting formula (B), it is possible to obtain improving the Optimum Leaves width W of the reliability of rotary compressor 1 and leaf Sheet front end radius of curvature Rv.Thus, it also is able to use rotation under the harsh operating condition that the discharge temperature of refrigerant gas is the highest Rotary compressor 1.
The rotary compressor that the present invention relates to particularly is using gas density compared with R410A cold-producing medium little and is discharging It is to have in the case of the R32 cold-producing medium that temperature is high or the mix refrigerant including at least R32 cold-producing mediums more than 25 weight % Effect.
Symbol description
1 rotary compressor
10 compressor housings
11 motors
12 compression units
15 rotary shafts
25 reservoirs
31S the first low-pressure connection tube
31T the second low-pressure connection tube
101 first through holes
102 second through holes
104 first suction tubes
105 second suction tubes
107 discharge pipes (discharge portion)
111 stators
112 rotors
12S the first compression unit
12T the second compression unit
121S the first cylinder (cylinder)
121T the second cylinder (cylinder)
122S the first side protuberance
122T the second side protuberance
123S the first cylinder inner wall (cylinder inner wall)
123T the second cylinder inner wall (cylinder inner wall)
124S the first spring eye
124T the second spring eye
125S the first annular piston (annular piston)
125T the second annular piston (annular piston)
127S the first blade (blade)
127T the second blade (blade)
128S the first blade groove (blade groove)
128T the second blade groove (blade groove)
129S the first pressure lead-in path
129T the second pressure lead-in path
130S the first operating room (operating room)
130T the second operating room (operating room)
131S the first suction chamber (suction chamber)
131T the second suction chamber (suction chamber)
133S the first discharge chambe (discharge chambe)
133T the second discharge chambe (discharge chambe)
135S the first inlet hole (inlet hole)
135T the second inlet hole (inlet hole)
136 refrigerant passage
140 central dividing plates
151 countershaft portions
152S the first eccentric part (eccentric part)
152T the second eccentric part (eccentric part)
153 main shaft part
160S bottom plate (end plate)
160T upper head plate (end plate)
161S countershaft bearing portion (bearing portion)
161T main shaft bearing portion (bearing portion)
Silencer cover under 170S
The upper silencer cover of 170T
175 run through bolt
Anechoic chamber under 180S
The upper anechoic chamber of 180T
190S first row portals (dump valve portion)
190T second row portals (dump valve portion)
200S the first dump valve (dump valve portion)
200T the second dump valve (dump valve portion)
201S the first dump valve compressed part (dump valve portion)
201T the second dump valve compressed part (dump valve portion)
252 reservoir supports
253 reservoir fixing bands
255 system connecting tubes
Through hole bottom 257
R peristome

Claims (2)

1. a rotary compressor, comprising:
Compressor housing, it is airtight and longitudinal housing, is provided with the discharge portion of cold-producing medium on top, arranges in lower side There is the sucting of cold-producing medium；
Compression unit, it is configured at the bottom of described compressor housing, including: cylinder, it is in the form of a ring；End plate, it has bearing portion With dump valve portion, the one end of described cylinder is closed；End plate or central dividing plate, it has bearing portion, another by described cylinder One end is closed；Annular piston, it is chimeric with the eccentric part of the rotary shaft supported by described bearing portion, along the gas of described cylinder The inside wall of cylinder revolves round the sun in this cylinder, and forms operating room between described cylinder inner wall；And blade, it is described from being arranged at Abut with described annular piston in being projected into described operating room in the blade groove of cylinder, described operating room is divided into suction chamber and Discharge chambe；And
Motor, it is configured at the top of described compressor housing, drives described compression unit via described rotary shaft, wherein,
Make cold-producing medium pass described sucting to suck wherein, and it is interior from described discharge to make cold-producing medium pass described compression case body Portion discharges, and described rotary compressor is characterised by:
If width of blade is W, the offset of eccentric part is e, vane nose radius of curvature is Rv, annular piston radius be Rro, leaf The non-slip peak width of both sides, sheet front end is Wt, so that the non-slip of the vane nose both sides defined by following formula (A) Peak width WtFor meeting the mode of the value of formula (B), set width of blade W and vane nose radius of curvature Rv:
Wt=(W/2)-e × Rv/(Rv+Rro) …(A)
0.3mm≤Wt≤0.6mm …(B)。
Rotary compressor the most according to claim 1, it is characterised in that:
Described cold-producing medium is R32 cold-producing medium or the mix refrigerant including at least R32 cold-producing mediums more than 25 weight %.
CN201580008662.6A 2014-02-28 2015-02-03 Rotary compressor Pending CN106133321A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2014039064A JP2015161295A (en) 2014-02-28 2014-02-28 rotary compressor
JP2014-039064 2014-02-28
PCT/JP2015/052976 WO2015129406A1 (en) 2014-02-28 2015-02-03 Rotary compressor

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CN106133321A true CN106133321A (en) 2016-11-16

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EP (1) EP3112683A4 (en)
JP (1) JP2015161295A (en)
CN (1) CN106133321A (en)
AU (1) AU2015224264B2 (en)
WO (1) WO2015129406A1 (en)

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JP6926449B2 (en) * 2016-11-16 2021-08-25 株式会社富士通ゼネラル Rotary compressor
KR102302472B1 (en) * 2017-05-30 2021-09-16 엘지전자 주식회사 Rotary compressor

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AU2015224264A1 (en) 2016-08-18
US20170051739A1 (en) 2017-02-23
WO2015129406A1 (en) 2015-09-03
AU2015224264B2 (en) 2017-06-29
EP3112683A4 (en) 2017-11-15
EP3112683A1 (en) 2017-01-04

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