WO2015129406A1 - ロータリ圧縮機 - Google Patents
ロータリ圧縮機 Download PDFInfo
- Publication number
- WO2015129406A1 WO2015129406A1 PCT/JP2015/052976 JP2015052976W WO2015129406A1 WO 2015129406 A1 WO2015129406 A1 WO 2015129406A1 JP 2015052976 W JP2015052976 W JP 2015052976W WO 2015129406 A1 WO2015129406 A1 WO 2015129406A1
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- WIPO (PCT)
- Prior art keywords
- vane
- cylinder
- refrigerant
- width
- chamber
- Prior art date
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Classifications
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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
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- 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
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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
- 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
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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
- 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
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- 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
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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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/268—R32
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
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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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
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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
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
Definitions
- the present invention relates to a rotary compressor used in an air conditioner or a refrigerator.
- the vane tip of the rotary compressor is formed in an arcuate surface of the vane tip curvature radius R V.
- the ridge line portion formed by intersecting the arc surface and the vane side surface abuts on the outer peripheral surface of the roller (annular piston)
- abnormal wear of the roller is caused.
- the non-sliding (non-contact) region width W t of the vane is a position where the roller revolves 90 ° and 270 ° from the top dead center when the position where the roller is at the top dead center is 0 °. The minimum.
- the contact portion between the vane tip and the roller (the roller / vane sliding area) has a high gas pressure on the high pressure side under conditions where the pressure ratio between the low pressure side and the high pressure side of the refrigerant gas is high, such as during low outside air temperature heating. Since the gas flow rate is high and the gas flow rate is low, the temperature at the tip of the vane becomes high, and oil film formation becomes difficult. In particular, in the case of the R32 refrigerant having a gas density smaller than that of the R410A refrigerant and a high discharge temperature, the temperature of the sliding surface of the vane and the roller is higher than that of the R410A refrigerant, and thus the vane and the roller are abnormally worn. There is a problem that reliability cannot be secured.
- a cylinder having a suction port and a discharge port, a rotary shaft having a crank portion disposed on the cylinder axis, and an eccentricity disposed between the crank portion and the cylinder.
- a rotary compressor having a rotating roller and a vane that reciprocates in a groove provided in the cylinder and contacts the outer peripheral surface of the roller, the position at which the vane starts reciprocating toward the roller is a reference for the rotation angle of the roller.
- the rotary contact of the vane with respect to the roller when the rotation angle of the roller is in the vicinity of 90 degrees and / or 270 degrees, the curvature of which is less than the curvature of the roller is disclosed. (For example, refer to Patent Document 1).
- the present invention has been made in view of the above, and has a vane tip surface formed of a plurality of surfaces having different curvatures, and has a simple shape, and the rotary compression with high durability of the vane and the roller (annular piston). The aim is to get a chance.
- the present invention includes a vertically mounted compressor housing that is provided with a refrigerant discharge portion at an upper portion and a refrigerant suction portion at a lower side surface and sealed.
- a working chamber is formed between the end plate or intermediate partition plate and the eccentric portion of the rotating shaft supported by the bearing portion, revolving along the cylinder inner wall of the cylinder, and the cylinder inner wall.
- a compression portion comprising: an annular piston, and a vane that protrudes from the vane groove provided in the cylinder into the working chamber and contacts the annular piston and partitions the working chamber into a suction chamber and a compression chamber; It is placed at the top of the compressor housing and A rotary compressor that sucks refrigerant through the suction portion and discharges the refrigerant from the discharge portion through the compressor housing, and has a vane width of W and an eccentricity.
- the vane tip is defined by the following formula (a) nonsliding area width W t of the both side portions, (B) to a value that satisfies the formula, a rotary compressor and sets the vane width W and the vane tip curvature radius R v.
- W t (W / 2) ⁇ e ⁇ R v / (R v + R ro ) (A) 0.3 mm ⁇ W t ⁇ 0.6 mm (B)
- FIG. 1 is a longitudinal sectional view showing a rotary compressor to which the present invention is applied.
- FIG. 2 is a cross-sectional view seen from the top of the first and second compression portions.
- FIG. 3 is a partially enlarged view of FIG.
- FIG. 4 is a partially enlarged view of FIG.
- FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention
- FIG. 2 is a transverse sectional view seen from above the first and second compression portions of the embodiment.
- the rotary compressor 1 As shown in FIG. 1, the rotary compressor 1 according to the embodiment is disposed at a lower portion of a sealed vertical cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via the rotary shaft 15.
- the stator 111 of the motor 11 is formed in a cylindrical shape, and is fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 10.
- the rotor 112 of the motor 11 is disposed inside the cylindrical stator 111 and is fixed by being shrink-fitted to a rotating shaft 15 that mechanically connects the motor 11 and the compression unit 12.
- the compression unit 12 includes a first compression unit 12S and a second compression unit 12T that is arranged in parallel with the first compression unit 12S and stacked on the upper side of the first compression unit 12S. As shown in FIG. 2, the first and second compression parts 12S and 12T are arranged radially to the first and second side projecting parts 122S and 122T, and the first and second suction holes 135S and 135T, And annular first and second cylinders 121S and 121T provided with second vane grooves 128S and 128T.
- first and second cylinder inner walls 123S and 123T are formed concentrically with the rotating shaft 15 of the motor 11 in the first and second cylinders 121S and 121T.
- first and second annular pistons 125S, 125T having an outer diameter smaller than the cylinder inner diameter are respectively disposed, and the first and second cylinder inner walls 123S, 123T,
- first and second working chambers 130S and 130T there are formed first and second working chambers 130S and 130T for sucking, compressing and discharging the refrigerant gas.
- the first and second cylinders 121S and 121T are formed with first and second vane grooves 128S and 128T extending in the radial direction from the first and second cylinder inner walls 123S and 123T over the entire cylinder height.
- Flat first and second vanes 127S and 127T are slidably fitted in the second vane grooves 128S and 128T, respectively.
- first and second vane grooves 128S and 128T are communicated with the first and second vane grooves 128S and 128T from the outer periphery of the first and second cylinders 121S and 121T at the back of the first and second vane grooves 128S and 128T.
- First and second spring holes 124S and 124T are formed in the first and second spring holes 124S and 124T, respectively.
- First and second vane springs (not shown) that press the back surfaces of the first and second vanes 127S and 127T are inserted into the first and second spring holes 124S and 124T.
- first and second vane 127S and 127T are moved from the inside of the first and second vane grooves 128S and 128T by the repulsive force of the first and second vane springs.
- the first and second working chambers 130S, 130T are protruded into the working chambers 130S, 130T, their tips abutting against the outer peripheral surfaces of the first and second annular pistons 125S, 125T, and the first and second vanes 127S, 127T.
- 130T is partitioned into first and second suction chambers 131S and 131T and first and second compression chambers 133S and 133T.
- first and second cylinders 121S and 121T communicate with the inner portions of the first and second vane grooves 128S and 128T and the interior of the compressor housing 10 through the opening R shown in FIG.
- First and second pressure introduction paths 129S and 129T are formed in which the compressed refrigerant gas in the housing 10 is introduced and back pressure is applied to the first and second vanes 127S and 127T by the pressure of the refrigerant gas. .
- the first and second cylinders 121S and 121T have a first communication between the first and second suction chambers 131S and 131T and the outside in order to suck the refrigerant from the outside into the first and second suction chambers 131S and 131T. Also, second suction holes 135S and 135T are provided.
- an intermediate partition plate 140 is disposed between the first cylinder 121S and the second cylinder 121T, and the first working chamber 130S (see FIG. 2) of the first cylinder 121S and the second cylinder.
- the second working chamber 130T (see FIG. 2) of 121T is partitioned and closed.
- the intermediate partition plate 140 closes the upper end portion of the first cylinder 121S and the lower end portion of the second cylinder 121T.
- a lower end plate 160S is disposed at the lower end of the first cylinder 121S, and closes the first working chamber 130S of the first cylinder 121S.
- An upper end plate 160T is disposed at the upper end portion of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T.
- the lower end plate 160S closes the lower end portion of the first cylinder 121S, and the upper end plate 160T closes the upper end portion of the second cylinder 121T.
- a secondary bearing portion 161S is formed on the lower end plate 160S, and the secondary shaft portion 151 of the rotary shaft 15 is rotatably supported by the secondary bearing portion 161S.
- a main bearing portion 161T is formed on the upper end plate 160T, and the main shaft portion 153 of the rotary shaft 15 is rotatably supported by the main bearing portion 161T.
- the rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are eccentric with a phase difference of 180 ° from each other.
- the first eccentric portion 152S is connected to the first annular piston 125S of the first compression portion 12S.
- the second eccentric portion 152T is rotatably fitted to the second annular piston 125T of the second compression portion 12T.
- the first and second annular pistons 125S and 125T revolve in the first and second cylinders 121S and 121T in the clockwise direction in FIG. 2 along the first and second cylinder inner walls 123S and 123T. Then, following this, the first and second vanes 127S and 127T reciprocate. Due to the movement of the first and second annular pistons 125S, 125T and the first and second vanes 127S, 127T, the volumes of the first and second suction chambers 131S, 131T and the first and second compression chambers 133S, 133T are continuous.
- the compressor 12 continuously sucks, compresses and discharges the refrigerant gas.
- a lower muffler cover 170S is disposed below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S. And the 1st compression part 12S is opened to lower muffler room 180S. That is, a first discharge hole 190S (see FIG. 2) that connects the first compression chamber 133S of the first cylinder 121S and the lower muffler chamber 180S is provided in the vicinity of the first vane 127S of the lower end plate 160S. In the hole 190S, a reed valve type first discharge valve 200S for preventing the backflow of the compressed refrigerant gas is disposed.
- the lower muffler chamber 180S is one chamber formed in an annular shape, and the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T are arranged on the discharge side of the first compression unit 12S. This is a part of the communication path that communicates with the upper muffler chamber 180T through the refrigerant path 136 (see FIG. 2) that passes through.
- the lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant gas.
- a first discharge valve presser 201S for limiting the amount of deflection opening of the first discharge valve 200S is fixed to the first discharge valve 200S by a rivet together with the first discharge valve 200S.
- the first discharge hole 190S, the first discharge valve 200S, and the first discharge valve presser 201S constitute a first discharge valve portion of the lower end plate 160S.
- an upper muffler cover 170T is disposed above the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper muffler cover 170T.
- a second discharge hole 190T (see FIG. 2) that communicates the second compression chamber 133T of the second cylinder 121T and the upper muffler chamber 180T is provided, and the second discharge hole 190T. Is provided with a reed valve type second discharge valve 200T for preventing the backflow of the compressed refrigerant gas.
- a second discharge valve presser 201T for limiting the deflection opening amount of the second discharge valve 200T is fixed to the second discharge valve 200T by a rivet together with the second discharge valve 200T.
- the upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant.
- the second discharge hole 190T, the second discharge valve 200T, and the second discharge valve presser 201T constitute a second discharge valve portion of the upper end plate 160T.
- the first cylinder 121S, the lower end plate 160S, the lower muffler cover 170S, the second cylinder 121T, the upper end plate 160T, the upper muffler cover 170T, and the intermediate partition plate 140 are integrally fastened by a plurality of through bolts 175 and the like.
- the outer peripheral portion of the upper end plate 160T is fixed to the compressor housing 10 by spot welding, and the compression portion 12 is fixed to the compressor housing 10. .
- the first and second through holes 101 and 102 are passed through the outer peripheral wall of the cylindrical compressor housing 10 in order from the lower part in the axial direction so as to pass the first and second suction pipes 104 and 105. Is provided.
- an accumulator 25 formed of an independent cylindrical sealed container is held by an accumulator holder 252 and an accumulator band 253 on the outer side of the compressor housing 10.
- a system connection pipe 255 connected to the evaporator of the refrigerant circuit is connected to the center of the top of the accumulator 25, and one end of the bottom through hole 257 provided at the bottom of the accumulator 25 extends to the upper part inside the accumulator 25.
- the other ends of the first and second suction pipes 104 and 105 are connected to the first and second low-pressure communication pipes 31S and 31T.
- the first and second low-pressure connecting pipes 31S, 31T for guiding the low-pressure refrigerant of the refrigerant circuit to the first and second compression parts 12S, 12T through the accumulator 25 are the first and second suction pipes 104, 105 is connected to the first and second suction holes 135S and 135T (see FIG. 2) of the first and second cylinders 121S and 121T. That is, the first and second suction holes 135S and 135T are connected in parallel to the evaporator of the refrigerant circuit.
- a discharge pipe 107 Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigerant circuit and discharges high-pressure refrigerant gas to the condenser side of the refrigerant circuit. That is, the first and second discharge holes 190S and 190T are connected to the condenser of the refrigerant circuit.
- Lubricating oil is enclosed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil is sucked up from an oil supply pipe 16 attached to the lower end portion of the rotating shaft 15 by a pump blade (not shown) inserted in the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slide parts Lubrication is performed and a small gap in the compression portion 12 is sealed.
- FIG. 3 is a partially enlarged view of FIG. 2
- FIG. 4 is a partially enlarged view of FIG.
- the maximum contact stress ⁇ max expressed by the equations (2) is generated.
- ⁇ max 2P / ( ⁇ a) (2)
- ⁇ max is the maximum contact stress
- a is the contact width
- P is the vane pressing force
- R v is the vane tip curvature radius
- R ro is the annular piston radius
- E v is the vane elastic modulus
- E ro is the annular piston elastic modulus.
- ⁇ v vane poisson ratio
- ⁇ ro annular piston poisson ratio.
- non-sliding region width W t at the both ends of the first and second vanes 127S and 127T is expressed by the following equation (A) (see the dimensional relationship of the similar triangle in FIG. 4).
- W t (W / 2) ⁇ e ⁇ R v / (R v + R ro ) (A)
- W t width of the non-sliding region on both side portions of the vane tip
- W vane width
- e eccentric amount of the eccentric portion.
- the rotary compressor 1 has a large pressure ratio between the low pressure side and the high pressure side of the refrigerant gas, such as during heating at a low outside temperature, and the high pressure side gas temperature is high, resulting in a low gas flow rate. If the contact stress between the first and second vanes 127S, 127T and the first and second annular pistons 125S, 125T increases under operating conditions), the first and second vanes 127S, 127T and the first and second annulars Since abnormal wear occurs in the pistons 125S and 125T, it is necessary to reduce the maximum contact stress ⁇ max expressed by the equation (2) as much as possible.
- the vane width W of the first and second vanes 127S and 127T is reduced, and the vane pressing force P due to the back pressure of the refrigerant gas in the compressor housing 10 is reduced. Is effective ⁇ see equation (2) ⁇ .
- the contact width a (contact width a of the 125T is , The contact width in the circumferential direction due to elastic deformation at the contact point between the first and second vanes 127S, 127T and the first and second annular pistons 125S, 125T.
- the maximum contact stress ⁇ max expressed by the equation (2) can be reduced.
- the non-sliding region width W t is becomes 0, the vane ridge the first and second annular pistons 125S, so as not to impinge on the outer peripheral surface of 125T, the first and second vanes 127S defined in formula (a), nonsliding area width W t of the front end sides of the 127T is, to a value that satisfies the following formula (B), to set the vane width W and the vane tip curvature radius R v.
- the vane width W is The vane pressing force P due to the back pressure can be reduced by 20%, and the maximum contact stress ⁇ max can be reduced.
- the rotary compressor according to the present invention is particularly effective when using an R32 refrigerant whose gas density is smaller than that of the R410A refrigerant and whose discharge temperature is high, or a mixed refrigerant containing at least 25% by weight of the R32 refrigerant. is there.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Wt=(W/2)-e×Rv/(Rv+Rro)・・・(A)
0.3mm≦Wt≦0.6mm ・・・・・・・・・(B)
ここで、σmax:最大接触応力、a:接触幅、P:ベーン押付け力、Rv:ベーン先端曲率半径、Rro:環状ピストン半径、Ev:ベーン弾性係数、Ero:環状ピストン弾性係数、νv:ベーンポアソン比、νro:環状ピストンポアソン比。
Wt=(W/2)-e×Rv/(Rv+Rro)・・・・・(A)
ここで、Wt:ベーン先端両側部の非摺動領域幅、W:ベーン幅、e:偏心部の偏心量。
0.3mm≦Wt≦0.6mm・・・・・(B)
非摺動領域幅Wtを、(B)式を満足する値(非摺動領域幅Wtが、背景技術に記載した従来値よりも10%以上狭い)とすることにより、ベーン幅Wが、従来よりも薄くなり、背圧によるベーン押付け力Pを20%小さくして、最大接触応力σmaxを小さくすることができる。
10 圧縮機筐体
11 モータ
12 圧縮部
15 回転軸
25 アキュムレータ
31S 第1低圧連絡管
31T 第2低圧連絡管
101 第1貫通孔
102 第2貫通孔
104 第1吸入管
105 第2吸入管
107 吐出管(吐出部)
111 ステータ
112 ロータ
12S 第1の圧縮部
12T 第2の圧縮部
121S 第1シリンダ(シリンダ)
121T 第2シリンダ(シリンダ)
122S 第1側方張出し部
122T 第2側方張出し部
123S 第1シリンダ内壁(シリンダ内壁)
123T 第2シリンダ内壁(シリンダ内壁)
124S 第1スプリング穴
124T 第2スプリング穴
125S 第1環状ピストン(環状ピストン)
125T 第2環状ピストン(環状ピストン)
127S 第1ベーン(ベーン)
127T 第2ベーン(ベーン)
128S 第1ベーン溝(ベーン溝)
128T 第2ベーン溝(ベーン溝)
129S 第1圧力導入路
129T 第2圧力導入路
130S 第1作動室(作動室)
130T 第2作動室(作動室)
131S 第1吸入室(吸入室)
131T 第2吸入室(吸入室)
133S 第1圧縮室(圧縮室)
133T 第2圧縮室(圧縮室)
135S 第1吸入孔(吸入孔)
135T 第2吸入孔(吸入孔)
136 冷媒通路
140 中間仕切板
151 副軸部
152S 第1偏心部(偏心部)
152T 第2偏心部(偏心部)
153 主軸部
160S 下端板(端板)
160T 上端板(端板)
161S 副軸受部(軸受部)
161T 主軸受部(軸受部)
170S 下マフラーカバー
170T 上マフラーカバー
175 通しボルト
180S 下マフラー室
180T 上マフラー室
190S 第1吐出孔(吐出弁部)
190T 第2吐出孔(吐出弁部)
200S 第1吐出弁(吐出弁部)
200T 第2吐出弁(吐出弁部)
201S 第1吐出弁押さえ(吐出弁部)
201T 第2吐出弁押さえ(吐出弁部)
252 アキュムホルダー
253 アキュムバンド
255 システム接続管
257 底部貫通孔
R 開口部
Claims (2)
- 上部に冷媒の吐出部が設けられ下部側面に冷媒の吸入部が設けられ密閉された縦置きの圧縮機筐体と、
前記圧縮機筐体の下部に配置され、環状のシリンダと、軸受部及び吐出弁部を有し前記シリンダの一端部を閉塞する端板と、軸受部を有し前記シリンダの他端部を閉塞する端板又は中間仕切板と、前記軸受部に支持された回転軸の偏芯部に嵌合され前記シリンダのシリンダ内壁に沿って該シリンダ内を公転し前記シリンダ内壁との間に作動室を形成する環状ピストンと、前記シリンダに設けられたベーン溝内から前記作動室内に突出して前記環状ピストンに当接し前記作動室を吸入室と圧縮室とに区画するベーンと、を備える圧縮部と、
前記圧縮機筐体の上部に配置され、前記回転軸を介して前記圧縮部を駆動するモータと、
を備え、前記吸入部を通して冷媒を吸入し、前記圧縮機筐体内を通して前記吐出部から冷媒を吐出するロータリ圧縮機において、
ベーン幅をW、偏心部の偏心量をe、ベーン先端曲率半径をRv、環状ピストン半径をRro、ベーン先端両側部の非摺動領域幅をWtとすると、次の(A)式により定義されるベーン先端両側部の非摺動領域幅Wtが、(B)式を満足する値となるように、ベーン幅W及びベーン先端曲率半径Rvを設定することを特徴とするロータリ圧縮機。
Wt=(W/2)-e×Rv/(Rv+Rro)・・・(A)
0.3mm≦Wt≦0.6mm ・・・・・・・・・(B) - 前記冷媒は、R32冷媒、若しくは、R32冷媒を少なくとも25重量%以上含む混合冷媒であることを特徴とする請求項1に記載のロータリ圧縮機。
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CN201580008662.6A CN106133321A (zh) | 2014-02-28 | 2015-02-03 | 旋转式压缩机 |
US15/119,091 US20170051739A1 (en) | 2014-02-28 | 2015-02-03 | Rotary compressor |
AU2015224264A AU2015224264B2 (en) | 2014-02-28 | 2015-02-03 | Rotary compressor |
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CN108071587A (zh) * | 2016-11-16 | 2018-05-25 | 富士通将军股份有限公司 | 旋转式压缩机 |
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Citations (6)
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JPH07229488A (ja) * | 1994-02-18 | 1995-08-29 | Hitachi Ltd | ロータリ圧縮機 |
JPH07293463A (ja) * | 1994-04-20 | 1995-11-07 | Matsushita Refrig Co Ltd | 圧縮機 |
JPH0814175A (ja) * | 1994-04-27 | 1996-01-16 | Daikin Ind Ltd | ロータリー圧縮機 |
JP2001263280A (ja) * | 2000-03-15 | 2001-09-26 | Sanyo Electric Co Ltd | 回転圧縮機 |
JP2002242867A (ja) * | 2001-02-14 | 2002-08-28 | Sanyo Electric Co Ltd | 回転圧縮機 |
JP2007092575A (ja) * | 2005-09-28 | 2007-04-12 | Mitsubishi Electric Corp | 回転式圧縮機 |
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JPH06257579A (ja) * | 1993-03-04 | 1994-09-13 | Matsushita Electric Ind Co Ltd | 回転式圧縮機 |
SE517622C2 (sv) * | 1999-12-17 | 2002-06-25 | Ericsson Telefon Ab L M | Anordning för att minska en linjedrivares effektförlust |
-
2014
- 2014-02-28 JP JP2014039064A patent/JP2015161295A/ja active Pending
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2015
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- 2015-02-03 EP EP15755988.1A patent/EP3112683A4/en not_active Withdrawn
- 2015-02-03 CN CN201580008662.6A patent/CN106133321A/zh active Pending
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JPH07229488A (ja) * | 1994-02-18 | 1995-08-29 | Hitachi Ltd | ロータリ圧縮機 |
JPH07293463A (ja) * | 1994-04-20 | 1995-11-07 | Matsushita Refrig Co Ltd | 圧縮機 |
JPH0814175A (ja) * | 1994-04-27 | 1996-01-16 | Daikin Ind Ltd | ロータリー圧縮機 |
JP2001263280A (ja) * | 2000-03-15 | 2001-09-26 | Sanyo Electric Co Ltd | 回転圧縮機 |
JP2002242867A (ja) * | 2001-02-14 | 2002-08-28 | Sanyo Electric Co Ltd | 回転圧縮機 |
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CN108071587A (zh) * | 2016-11-16 | 2018-05-25 | 富士通将军股份有限公司 | 旋转式压缩机 |
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JP2015161295A (ja) | 2015-09-07 |
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EP3112683A4 (en) | 2017-11-15 |
EP3112683A1 (en) | 2017-01-04 |
US20170051739A1 (en) | 2017-02-23 |
AU2015224264B2 (en) | 2017-06-29 |
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