CN104081055B - Rotary compressor and freezing cycle device - Google Patents
Rotary compressor and freezing cycle device Download PDFInfo
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- CN104081055B CN104081055B CN201380006906.8A CN201380006906A CN104081055B CN 104081055 B CN104081055 B CN 104081055B CN 201380006906 A CN201380006906 A CN 201380006906A CN 104081055 B CN104081055 B CN 104081055B
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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
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
- F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
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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
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/102—Geometry of the inlet or outlet of the outlet
Abstract
By (the 20a of cylinder chamber, internal diameter area 20b) is made as A, the internal diameter size of the ejiction opening of base bearing (16a) (22a) is made as to dm, when the internal diameter size of the ejiction opening of supplementary bearing (16b) (22b) is made as to ds, at least one party in formula (1) and formula (2) sets up, by (the 20a of cylinder chamber, volume 20b) is made as V, the spring constant of the ejection valve (23a) of base bearing (16a) is made as to Km, when the spring constant of the ejection valve (23b) of supplementary bearing (16b) is made as to Ks, formula (3), at least one party in formula (4) sets up. wherein, 4.6 × 10－3≦dm/A≦6.5×10－3……(1)；4.6×10－3≦ds/A≦6.5×10－3……(2)；1.2×10－4≦Km/V≦3.5×10－4……(3)；1.2×10－4≦Ks/V≦3.5×10－4……(4)。
Description
Technical field
Embodiments of the present invention relate to rotary compressor and have used the cold of this rotary compressorFreeze EGR.
Background technology
As the rotary compressor using in the freezing cycle devices such as air-conditioning equipment, known have haveSuch structure shown in the invention of recording in JP 2007-92534 communique. Have: cylinder;Run through the rotating shaft of cylinder; Be arranged at rotating shaft and in cylinder, carry out bias mobile (eccentric rotary)Roller; And rotating shaft axle is supported to and can be rotated and by the end face sealing of cylinder and at cylinderInterior two bearings (base bearing, supplementary bearing) that form cylinder chamber. In such rotary compressor,The flange part of bearing be provided with ejiction opening for being ejected in compressed gas refrigerant in cylinder chamber andFor the ejection valve that this ejiction opening is opened and closed.
Ejection valve is beaten the in the situation that in cylinder chamber, compressed gas refrigerant having reached authorized pressureOpen. Then, gas refrigerant is closed after ejiction opening ejection.
Such rotary compressor is except when starting, in most cases in middling speed rotation territory (fortuneTurning frequency is 30～60Hz) or low speed rotation territory (operating frequency be 30Hz following) turn round.Therefore, each several part size is to pay attention to improving the compression efficiency in middling speed rotation territory or low speed rotation territory and quiltSet.
Therefore, the internal diameter size of ejiction opening in order to reduce dead volume, reduce again expansion-loss and as far as possibleNinor feature becomes. With respect to the internal diameter area A (mm of cylinder chamber2) the internal diameter size d of ejiction opening(mm) ratio " d/A " is set to " 3 × 10－3＜d/A＜4×10－3(mm/mm2)”。
In addition when, ejection valve is for pressure rise in cylinder chamber, drive valve smoothly and use spring normalThe little ejection valve of number, the ejection spring constant K (N/mm) of valve and the volume V (mm of cylinder chamber3)Ratio " K/V " be set to " 0.6 × 10－4＜K/V＜0.7×10－4(N/mm4)”。
Look-ahead technique document
Patent documentation
Patent documentation 1: JP 2007-92534 communique
Summary of the invention
But, make such rotary compressor at the more than 1.2 times of source power supply frequency, i.e. 70HzIn the situation turning round in above High Rotation Speed territory, it is large that the passage resistance of ejiction opening becomes. This be because,Very little relative with the internal diameter size of ejiction opening, compression speed is very fast. And, due to the path of ejiction openingIt is large that resistance becomes, and causes gas refrigerant in cylinder chamber by excess compression, therefore produces based on overcompressionLoss increase and produce compression efficiency reduce problem. And, be accompanied by the excessive of gas refrigerantCompression, increases to the load of the axial gas refrigerant of rotation, and sliding part is easily deteriorated, produces slidingThe problem that the reliability of moving portion reduces.
In addition, in the case of ejection valve spring constant less, if rotary compressor is at high-speed rotaryTurn territory and turn round, can produce the state of affairs of the ejection valve constant time lag of closing. Then, due to ejectionValve timeing closing postpones, and cause compressed after from the gas refrigerant adverse current of ejiction opening ejection to cylinderIndoor. The gas refrigerant of this adverse current and then expand again in cylinder chamber, thereby based on the generation of expanding againLoss, the compression efficiency of rotary compressor reduces.
The object of embodiments of the present invention is to provide a kind of situation about turning round in High Rotation Speed territoryCan improve down the rotary compressor of compression efficiency and possess the freeze cycle of this rotary compressorDevice.
For solving the means of problem
In the rotary compressor of embodiment, in closed shell, contain motor part and via toolHave the rotating shaft of eccentric part and the compression mechanical part that this motor part links, compression mechanical part has: gasCylinder, rotating shaft runs through this cylinder; Roller, chimeric with eccentric part, one side makes a part and the gas of outer peripheral faceIt is mobile that bias is carried out in the inner peripheral surface contact of cylinder on one side; And base bearing and supplementary bearing, supporting rotating shaft,And the end face sealing of cylinder is formed to cylinder chamber in cylinder; In base bearing and supplementary bearing settingHave: ejiction opening, make by roller carry out bias mobile and in cylinder chamber compressed working fluid to closeEjection in closed shell body; And ejection valve, this ejiction opening is opened and closed. And, in cylinder chamberFootpath area is made as A (mm2), by the internal diameter size of ejiction opening that is arranged at base bearing be made as dm (mm),When the internal diameter size of ejiction opening that is arranged at supplementary bearing is made as to ds (mm), set the following formula that makes for(1) at least one party and in formula (2) sets up, and the volume of cylinder chamber is made as to V (mm3), will establishThe spring constant that is placed in the ejection valve of base bearing is made as Km (N/mm), will be arranged at the spray of supplementary bearingWhen the spring constant that goes out valve is made as Ks (N/mm), set following formula (3) and the formula (4) of making forIn at least one party set up.
Formula (1), (2), (3), (4) are:
4.6×10－3≦dm/A≦6.5×10－3(mm/mm2)…………(1)
4.6×10－3≦ds/A≦6.5×10－3(mm/mm2)…………(2)
1.2×10－4≦Km/V≦3.5×10－4(N/mm4)………………(3)
1.2×10－4≦Ks/V≦3.5×10－4(N/mm4)………………(4)
Wherein, at cylinder, be multiple in the situation that, V is the volume of 1 cylinder chamber.
Brief description of the drawings
Fig. 1 is that the freezing of the rotary compressor representing with section including in the first embodiment followsThe structure chart of loop device.
Fig. 2 is the top view that represents base bearing.
Fig. 3 is the top view that represents to spray valve.
Fig. 4 is the internal diameter area A (mm that represents the first cylinder chamber2) with the internal diameter chi of the first ejiction openingThe experiment of the relation between ratio " dm/A " and the compression efficiency of rotary compressor of very little dm (mm)The chart of result.
Fig. 5 is the volume V (mm that represents cylinder chamber3) with ejection valve spring constant K (N/mm)Ratio " K/V (N/mm4) " and the compression efficiency of rotary compressor between the experimental result of relationChart.
Fig. 6 is rotary compressor, formula (1)～(4) that represent to make to meet formula (1)～(4)All the rotary compressor of ungratified past case, meet formula (1), (2) but do not meet formula (3),(4) in the situation that having carried out running in High Rotation Speed territory, the rotary compressor of comparative example measuredPV line chart.
Fig. 7 is illustrated in the rotary compressor, formula (1)～(4) that meet formula (1)～(4)All the rotary compressor of ungratified past case, meet formula (1)～(2) but do not meet formula(3), the rotating speed in the rotary compressor of the comparative example of (4) and the overall efficiency of rotary compressorBetween the chart of experimental result of relation.
Fig. 8 is the vertical profile front view that represents the shape of the ejiction opening in the second embodiment.
Fig. 9 is illustrated in the path size dm1 of the tapered portion that the ejection side of ejiction opening arranges with maximumThe experiment of the relation between ratio " dm2/dm1 " and the overall efficiency of rotary compression of footpath size dm2The chart of result.
Figure 10 is the top view that represents the cylinder in the 3rd embodiment.
Figure 11 is the Y-Y line profile representing in Figure 10.
Figure 12 is the stereogram that a part for the cylinder of Figure 10 is represented with section.
Detailed description of the invention
Below, based on accompanying drawing, embodiments of the present invention are described.
(the first embodiment)
Based on Fig. 1 to Fig. 7, the first embodiment is described. Freezing cycle device 1 tool shown in Fig. 1There is compressor main body 2 and reservoir (accumulator) 3, and possess the low pressure as working fluidGas refrigerant compression and make the rotary compressor 4 of the gas refrigerant of high pressure. And, freezingEGR 1 has: condenser 5, is connected with the ejection side of compressor main body 2, for making high pressureGas refrigerant condensation and make liquid refrigerant; Expansion gear 6, is connected with condenser 5, for inciting somebody to actionLiquid refrigerant decompression; And evaporimeter, be connected between expansion gear 6 and reservoir 3, forMake liquid refrigerant evaporates.
Compressor main body 2 has and is formed as closed shell 8 cylindraceous. Bottom in closed shell 8Accumulate and have lubricating oil 9. And, in closed shell 8, contain the motor part that is positioned at upper side10 and be positioned at the compression mechanical part 11 of lower side. This motor part 10 and compression mechanical part 11 are via revolvingRotating shaft 12 and linking. Rotating shaft 12 is taking the center of the long side direction of compressor main body 2 as rotating shaft entersRow rotation.
Motor part 10 is so-called motor, for rotating shaft 12 is rotated. Motor part 10 hasRotor 13 and stator 14. Rotor 13 is fixed in rotating shaft 12, is provided with permanent magnet (not shown).Stator 14 is fixed in closed shell 8, is configured in the position that rotor 13 is surrounded, and is wound withCoil (not shown).
Compression mechanical part 11 is by the gas refrigerant compression of low pressure. Compression mechanical part 11 has and is positioned atThe first cylinder 15a of portion's side and the second cylinder 15b that is positioned at lower side. This first cylinder 15a and secondBetween cylinder 15b, be provided with demarcation strip 17. In addition, in the upper surface of the first cylinder 15a, be fixed with,Rotating shaft 12 is supported to the base bearing 16a that can rotate, in the lower surface of the second cylinder 15b, GuSurely have rotating shaft 12 is supported to the supplementary bearing 16b that can rotate.
Rotating shaft 12 runs through the first cylinder 15a, the second cylinder 15b and configures. At this rotating shaft 12,Be provided with the first eccentric part 18a and the second eccentric part 18b of same diameter with 180 ° of phase differences. ?One eccentric part 18a is chimeric the first roller 19a, has a second roller 19b the second eccentric part 18b is chimeric.
In the inside of the first cylinder 15a, be formed with the two ends of the first cylinder 15a by base bearing 16aThe first 20a of cylinder chamber sealing with demarcation strip 17. In the inside of the second cylinder 15b, be formed with byThe second 20b of cylinder chamber that the two ends of the second cylinder 15b are sealed by demarcation strip 17 and supplementary bearing 16b.In the first 20a of cylinder chamber, contain the first roller 19a chimeric with the first eccentric part 18a, secondIn the 20b of cylinder chamber, contain the second roller 19b chimeric with the second eccentric part 18b. This first roller 19a,Second roller 19b is configured in the time that rotating shaft 12 rotates to make its outer peripheral face and the first cylinder 15a, the on one sideBias mobile (eccentric rotary) is carried out in the inner peripheral surface line contact of two cylinder 15b on one side.
In addition,, in the first 20a of cylinder chamber, the second 20b of cylinder chamber, contain and be accompanied by the first rollerThe rotation of 19a, second roller 19b and these 2 cylinder chamber's interior separations are become to volume and pressure changes twoThe blade (blade) (not shown) in individual space. The leading section of this blade and the first roller 19a, second rollerThe outer peripheral face butt of 19b. Be provided with the first ejection valve system 21a at base bearing 16a. This first ejectionValve system 21a has the first ejiction opening 22a, the first leaf valve (reed that are formed at base bearing 16aValve) 23a and the first valve guard 24a. The first leaf valve 23a is fixed on bearing by screw thread16a, for the first ejiction opening 22a is opened and closed first ejection valve. The first valve guard 24a withThe first leaf valve 23a together screw thread is fixed on base bearing 16a, for limiting the first leaf valve 23aLarge aperture. This first ejection valve system 21a is installed in the first silencer (muffler) of base bearing 16a25a covers. The first silencer 25a is formed with the ejiction opening of the inside and outside connection that makes the first silencer 25a26。
Be provided with the second ejection valve system 21b at supplementary bearing 16b. This second ejection valve system 21b hasThe structure identical with the first above-mentioned ejection valve system 21b, has and is formed at second of supplementary bearing 16bEjiction opening 22b, the second leaf valve 23b and second valve stop 24b. The second leaf valve 23b byScrew thread be fixed on supplementary bearing 16b, for the second ejiction opening 22b is opened and closed second ejection valve. TheTwo valve guard 24b screw thread together with the second leaf valve 23b is fixed on supplementary bearing 16b, for limitingThe maximum opening of two leaf valve 23b. This second ejection valve system 21b is installed in supplementary bearing 16b'sThe second silencer 25b covers. In the second silencer 25b with the first silencer 25a in by run throughThe mode of supplementary bearing 16b, the second cylinder 15b, demarcation strip 17, the first cylinder 15a and base bearing 16aThe gas refrigerant path of navigation (not shown) forming and be joined into gas refrigerant can be moved.
Reservoir 3 has closed shell 27 cylindraceous. Reservoir 3 is connected to and makes with evaporimeter 7The gas refrigerant that must be gasified by evaporimeter 7 or the liquid refrigerant streams not gasified by evaporimeter 7Enter in closed shell 27. In this closed shell 27, be provided with one end in closed shell 27Upper side opening, two suctions that only mode that flows into for the gas refrigerant in closed shell 27 configuresPipe 28. The other end of these suction lines 28 is from the lower end side of closed shell 27 to closed shell 27 extensionsStretch, link with the first 20a of cylinder chamber, second 20b of cylinder chamber of compression mechanical part 11. In these suctionsEnter the part of the lower side that is positioned at closed shell 27 in pipe 28, be formed with in closed shell 27The oily return aperture 29 that flows into of the lubricating oil that accumulates of bottom.
Fig. 2 is the top view that represents above-mentioned base bearing 16a. As described above, at this base bearing 16aBe formed with the first ejiction opening 22a. In addition, be formed with screw 30 at base bearing 16a, this screw 30 suppliesScrew (not shown) acts on upper fixing the first above-mentioned leaf valve 23a of this base bearing 16a by screwWith the first valve guard 24a. The internal diameter size of the first ejiction opening 22a is set to dm (mm).
Although omit the diagram of top view,, above-mentioned supplementary bearing 16b is and base bearing 16aIdentical structure. Therefore, be formed with the second above-mentioned ejiction opening 22b at supplementary bearing 16b, the second ejectionThe internal diameter size of mouth 22b is set to ds (mm).
Fig. 3 is the bowing of the first leaf valve 23a that is illustrated in the configuration of installed position on base bearing 16aView. The first leaf valve 23a is formed by tabular member. The first leaf valve 23a have arm 32,Valve body portion 33. Arm 32 has flexible, is at one end formed with the installing hole of inserting for fixing screw31. It is distolateral that valve body portion 33 is arranged on another of arm 32, and, can with discoid being formed asThe size that the first ejiction opening 22a is closed. The appearance and size of valve body portion 33 is set to R (mm),The width dimensions of arm 32 is set to W (mm), and it is set to " R/W >=2 " than " R/W ",Valve body portion 33 becomes necking down shape from valve body portion 33 towards arm 32 with the coupling part of arm 32Shape.
Although omitted the diagram of top view, be installed on the second leaf valve 23b of supplementary bearing 16bAlso be formed as the shape identical with the first leaf valve 23a.
At this, in this rotary compressor 4, by the first 20a of cylinder chamber, the second 20b of cylinder chamberInternal diameter area is separately made as A (mm2), the internal diameter size of the first ejiction opening 22a is made as to dm(mm), the internal diameter size of the second ejiction opening 22b is made as to ds (mm). Now, the first cylinder chamberInternal diameter area A (the mm of 20a2) with the ratio " dm/A of the internal diameter size dm (mm) of the first ejiction opening 22a(mm/mm2) ", the internal diameter area A (mm of the second 20b of cylinder chamber2) and the second ejiction opening 22bRatio " the ds/A " (mm/mm of internal diameter size ds (mm)2) be set so that respectively following formula becomesVertical:
4.6×10－3≦dm/A≦6.5×10－3(mm/mm2)…………(1)
4.6×10－3≦ds/A≦6.5×10－3(mm/mm2)…………(2)。
In addition, in this rotary compressor 4, by the first 20a of cylinder chamber, the second 20b of cylinder chamberVolume is separately made as V (mm3), and the spring constant of the first leaf valve 23a is made as to Km (N/mm),The spring constant of the second leaf valve 23b is made as to Ks (N/mm). Now, first 20a of cylinder chamberVolume V (mm3) with the ratio " Km/V of the spring constant Km (N/mm) of the first leaf valve 23a(N/mm4) ", the volume V (mm of the second 20b of cylinder chamber3) with the spring of the second leaf valve 23bRatio " Ks/V (the N/mm of constant K s (N/mm)4) " be set so that respectively following formula set up:
1.2×10－4≦Km/V≦3.5×10－4(N/mm4)………………(3)
1.2×10－4≦Ks/V≦3.5×10－4(N/mm4)………………(4)。
In addition, in cylinder chamber be multiple in the situation that, the first cylinder chamber shown in formula (3), formula (4)The volume " V " of 20a, the second 20b of cylinder chamber refers to the volume of 1 cylinder chamber.
In addition, as shown in Figure 3, in the first leaf valve 23a, the second leaf valve 23b, by valve bodyThe appearance and size of portion 33 is made as R (mm), when the width dimensions of arm 32 is made as to W (mm),The ratio of the appearance and size R (mm) of valve body portion 33 and the width dimensions W (mm) of arm 32" R/W " is set so that following formula establishment:
R/W≥2………………(5)。
The size example of each structural portion of rotary compressor 4 is set as described below.
The internal diameter size of the first 20a of cylinder chamber, the second 20b of cylinder chamber is respectively 43mm,
The height dimension of the first 20a of cylinder chamber, the second 20b of cylinder chamber is respectively 18mm,
The appearance and size of the first roller 19a, second roller 19b is respectively 35mm,
The offset of the first eccentric part 18a, the second eccentric part 18b of rotating shaft 12 is (from rotating shaft 12Pivot to the 18a, the distance at the second eccentric part 18b center) be respectively 4mm,
The internal diameter size (dm) of the first ejiction opening 22a is 8mm,
The internal diameter size (ds) of the second ejiction opening 22b is 8mm.
At this, about above-mentioned " dm/A (mm/mm2)”、“ds/A(mm/mm2) " modelThe setting of enclosing, describes with the chart of the experimental result of presentation graphs 4. Fig. 4 represents firstInternal diameter area A (the mm of cylinder chamber2) with the ratio of the internal diameter size dm (mm) of the first ejiction openingThe chart of the experimental result of the relation between " dm/A " and the compression efficiency of rotary compressor.
In addition, this experiment be by middling speed rotate rotating speed in territory be made as 40Hz, by High Rotation Speed territoryRotating speed is made as that 90Hz carries out. In addition the leaf valve using in this experiment, is rotary pressure in the pastThe leaf valve that contracting machine uses, the leaf valve that so-called spring constant is little and soft.
In chart shown in Fig. 4, using transverse axis as " dm/A (mm/mm2) ", using the longitudinal axis asThe compression efficiency of rotary compressor.
Known according to the chart shown in this Fig. 4, rotary compressor is transported in middling speed rotation territoryIn situation about turning, along with " dm/A (mm/mm2) " value become large, that is, and in ejiction openingIt is large that the ratio of footpath size " dm " becomes, and compression efficiency reduces.
On the other hand, the in the situation that rotary compressor having carried out running in High Rotation Speed territory, " dm/A(mm/mm2) " value " 4.6 × 10－3≦dm/A≦6.5×10－3" scope in time compression effectRate improves, at " dm/A (mm/mm2) " value be 5.5 × 10－3Situation under, obtained maximumCompression efficiency. Therefore, by by " dm/A (mm/mm2) " be set as " 4.6 × 10－3≦dm/A≦6.5×10－3" scope, can improve the compression efficiency of the rotary compressor in High Rotation Speed territory.
In addition, at this with " dm/A (mm/mm2) " situation be that example is illustrated, but exist“ds/A(mm/mm2) " situation under too.
Then, about above-mentioned " Km/V (N/mm4)”、“Ks/V(N/mm4) " scopeSetting, illustrate with the chart of the experimental result of presentation graphs 5. Fig. 5 is the appearance that represents cylinder chamberLong-pending V (mm3) with the ratio " K/V (N/mm of spring constant K (N/mm) of ejection valve4) " withThe chart of the experimental result of the relation between the compression efficiency of rotary compressor.
In chart shown in Fig. 5, using transverse axis as " Km/V (N/mm4) ", using the longitudinal axis as revolvingThe compression efficiency of rotatable compressor. In addition, in this experiment, make " dm/A (mm/mm2) "Value is fixed as 5.5 × 10－3, make the spring constant " Km " of leaf valve variable. In addition, experiment is pinRunning in High Rotation Speed territory is carried out.
Known according to the chart shown in this Fig. 5, by so that " Km/V (N/mm4) " value become“1.2×10－4≦Km/V≦3.5×10－4(N/mm4) " the mode of scope set the bullet of leaf valveSpring constant " Km ", can improve the compression efficiency of rotary compressor. Before with " Km/V (N/mm4) " situation be that example is illustrated, but at " Ks/V (N/mm4) " situationUnder too.
In such structure, in this rotary compressor 4, by motor part 10 is switched on,Make the first roller 19a and second roller 19b carry out eccentric rotary, compressor around the center line of rotating shaft 12Structure portion 11 is driven.
In the situation that compression mechanical part 11 has been driven, be accompanied by the first roller 19a, second roller 19bEccentric rotary, volume and the pressure in two spaces in the first 20a of cylinder chamber, the second 20b of cylinder chamberChange. Because this volume and pressure change, thereby the gas refrigerant of low pressure is from reservoir 3Interior process suction line 28 is inhaled in the first 20a of cylinder chamber, the second 20b of cylinder chamber. Then, inhaleThe gas refrigerant of the low pressure entering is compressed in the first 20a of cylinder chamber, the second 20b of cylinder chamber, becomesThe gas refrigerant of high pressure.
In the first cylinder 15a, the pressure rise of the gas refrigerant in the first 20a of cylinder chamber arrivesThe timing of setting, the first leaf valve 23a opens. The gas system of the high pressure in the first 20a of cylinder chamberCryogen is ejected in the first silencer 25a through the first ejiction opening 22a. Be ejected into the first noise eliminationGas refrigerant in device 25a is ejected into closed shell through the ejiction opening 26 of the first silencer 25aIn 8.
In addition, in the second cylinder 15b, the pressure of the gas refrigerant in the second 20b of cylinder chamberRise to the timing of setting, the second leaf valve 23b opens. High pressure in the second 20b of cylinder chamberGas refrigerant is ejected in the second silencer 25b through the second ejiction opening 22b. Be ejected intoGas refrigerant in two silencer 25b flows into first through above-mentioned gas refrigerant path of navigation and disappearsAfter in sound device 25a, and then be ejected into closed shell through ejiction opening 26 in the first silencer 25aIn 8.
After compressed in the first 20a of cylinder chamber, the second 20b of cylinder chamber, be ejected into closed shell 8In the gas refrigerant of high pressure flow in condenser 5, heat radiation in condenser 5 and become liquid systemCryogen. This liquid refrigerant flows into expansion gear 6 and is depressurized, and is depressurized in rear inflow evaporimeter 7Evaporate by absorbing heat, become gas refrigerant. Gas refrigerant in evaporimeter 7 interior evaporations flows intoIn reservoir 3 and carried out gas-liquid separation (separation of the liquid component that gas refrigerant comprised). ItsIn, only gas refrigerant is from the interior process of suction line 28 of reservoir 3 and be supplied to compression mechanical part 11The first 20a of cylinder chamber, the second 20b of cylinder chamber in, again compressed.
At this, Fig. 6 all meets above-mentioned formula (1), formula (2), formula (3), formula (4)The rotary compressor 4 of present embodiment, formula (1), formula (2), formula (3), formula (4) are all notThe rotary compressor of satisfied past case, meet formula (1) and formula (2) but do not meet formula (3) andThe in the situation that having carried out running in High Rotation Speed territory, the rotary compressor of the comparative example of formula (4) measuresPV line chart.
Specifically, in the rotary compressor of past case, dm/A is made as to 3.5 × 10-3(mm/mm2), ds/A is made as to 3.5 × 10-3(mm/mm2), Km/V is made as to 0.8 × 10-4(N/mm4), Ks/V is made as to 0.8 × 10-4(N/mm4)。
In the rotary compressor of comparative example, dm/A is made as to 5.5 × 10-3(mm/mm2), willDs/A is made as 5.5 × 10-3(mm/mm2), Km/V is made as to 0.8 × 10-4(N/mm4), by Ks/VBe made as 0.8 × 10-4(N/mm4)。
In the rotary compressor 4 of present embodiment, dm/A is made as to 5.5 × 10-3(mm/mm2)，Ds/A is made as to 5.5 × 10-3(mm/mm2), Km/V is made as to 1.7 × 10-4(N/mm4), willKs/V is made as 1.7 × 10-4(N/mm4)。
According to the PV line chart shown in Fig. 6, in the rotary compressor of past case, due to ejiction openingInternal diameter size little, cause becoming large from the passage resistance of the gas refrigerant of this ejiction opening process. Therefore,After valve left by leaf valve, also make gas refrigerant compressed, thereby cause loss by overcompression. In addition,In the rotary compressor of past case, use the little and soft leaf valve of spring constant, therefore,After the gas refrigerant ejection of high pressure, the constant time lag that leaf valve cuts out. Then, due to this reedThe constant time lag that valve cuts out, causes the gas refrigerant of the high pressure temporarily spraying from ejiction opening from ejiction openingAdverse current is in cylinder chamber. Then, the gas refrigerant of this adverse current expands in cylinder chamber again, thereby byExpand and cause loss again.
On the other hand, in the rotary compressor of comparative example, it is large that the internal diameter size of ejiction opening becomes, because ofThis, diminish from the passage resistance of the gas refrigerant of this ejiction opening process, the loss being produced by overcompressionDiminish. And, be accompanied by the loss being produced by overcompression and diminish, to the direction that stops leaf valve to be closedThe power of effect diminishes, and therefore, the delay of leaf valve timeing closing is suppressed, by the damage that expands and cause againMistake diminishes.
In the rotary compressor 4 of present embodiment, ejiction opening (the first ejiction opening 22a, the second sprayOutlet 22b) internal diameter size so that become large. Therefore, from these ejiction openings (the first ejiction opening 22a,The second ejiction opening 22b) passage resistance of gas refrigerant of process diminishes, the loss being caused by overcompressionDiminish. And, use large and hard leaf valve (the first leaf valve 23a, the second leaf valve of spring constant23b), therefore, leaf valve (the first leaf valve 23a, the second spring after the gas refrigerant ejection of high pressurePlate valve 23b) timing of closing becomes early. Therefore, from ejiction opening (the first ejiction opening 22a, the second ejectionMouthful 22b) to the gas refrigerant in cylinder chamber (the first 20a of cylinder chamber, the second 20b of cylinder chamber)Adverse current is suppressed, is diminished by the loss causing of expanding again.
The in the situation that of having sucked gas refrigerant in cylinder chamber, can produce the loss being caused by overexpansion,But, the rotary compressor that is lost in past case that caused by this overexpansion, comparative example rotaryIn the rotary compressor 4 of compressor and present embodiment, similarly produce.
Fig. 7 is the rotary of the rotary compressor that is illustrated in the illustrated past case of Fig. 6, comparative exampleRotating speed in the rotary compressor 4 of compressor, present embodiment and overall efficiency (rotary compressionThe overall efficiency of machine) between the chart of relation. Known according to the chart of Fig. 7, revolving of past caseIn rotatable compressor, in middling speed rotation territory, overall efficiency is high, and in High Rotation Speed territory, overall efficiency is low.On the other hand, in the rotary compressor of comparative example, in middling speed rotation territory, overall efficiency is low,High Rotation Speed territory, overall efficiency is high, and the maximum of overall efficiency is little. And, in present embodimentRotary compressor 4 in, in middling speed rotation territory, overall efficiency is low, in High Rotation Speed territory, comprehensiveCompared with the rotary compressor of efficiency and comparative example, be enhanced.
Therefore the rotary compressor 4 that, meets formula (1)～formula (4) is comprehensive High Rotation Speed territoryEfficiency improves, and can realize the minimizing of power consumption.
In addition, any one party Chinese style (1) in the first ejiction opening 22a, the second ejiction opening 22b orIn the situation that person's formula (2) is set up, the first ejiction opening 22a of setting up in formula (1) or formula (2),The second ejiction opening 22b side can reduce the loss being caused by overcompression. In addition, the first leaf valve 23a,In the situation that any one party Chinese style (3) in the second leaf valve 23b or formula (4) are set up, in formula(3) or formula (4) the first leaf valve 23a, the second leaf valve 23b side set up can reduce by againThe loss that expansion causes. Therefore, there are these two sprays of the first ejiction opening 22a, the second ejiction opening 22bOutlet rotary compressor 4 in, in the first ejiction opening 22a, the second ejiction opening 22b any oneIn side, meet formula (1) or formula (2) and in the first leaf valve 23a, the second leaf valve 23bAny one party in meet in the situation of formula (3) or formula (4), can improve High Rotation Speed territoryOverall efficiency.
Then, as shown in Figure 3, in the first leaf valve 23a, the appearance and size R (mm) of valve body portion 33Be set to " R/W >=2 ", valve body portion 33 with the ratio of the width dimensions W (mm) of arm 32Become necking down shape with the coupling part of arm 32. Therefore, in the time that the first leaf valve 23a opens, fromThe gas refrigerant of the first ejiction opening 22a ejection from Fig. 3 with week of the valve body portion 33 of shadow representationThe periphery process of limit portion and arm 32. Therefore the gas refrigerant, spraying from the first ejiction opening 22aThe area of passage become large, the flow velocity of the gas refrigerant of ejection reduces. Thus, can reduce from firstThe gas refrigerant of ejiction opening 22a ejection with respect to the first leaf valve 23a that wants to close to stoping itThe power of the directive effect of closing. Therefore, can prevent leaf valve timeing closing produce postpone and reduce byThe loss of expanding and causing again. About this point, be formed as and of the first leaf valve 23a same shapeIn two leaf valve 23b too.
In addition the width dimensions W (mm) of the appearance and size R of valve body portion 33 (mm) and arm 32,Ratio " R/W " be set to " R/W >=2 ", therefore, the first leaf valve 23a is in arm 32 partsEasily distortion. Therefore, can prevent the single-ended butt of valve body portion 33, and improve valve body portion 33To the close property of valve seat part. Then, by improving valve body portion 33 being close to respect to valve seat partProperty, can improve the compression performance in the first 20a of cylinder chamber. And, can prevent by single-ended buttThe damage of the first ejiction opening 22a causing, can obtain the valve system that reliability is high. About this point,Be formed as with the second leaf valve 23b of the first leaf valve 23a same shape in too.
In addition, in the present embodiment, to the first roller 19a, second roller 19b and blade split formRotary compressor be illustrated, but the present invention also can be applied in roller and blade one landformIn the rotary compressor (rotation type compressor) becoming.
In addition in present embodiment, be illustrated as an example of following situation example: there is the first cylinder chamber,20a, the second 20b Zhe Liangge cylinder chamber of cylinder chamber, at the base bearing 16a that forms the first 20a of cylinder chamberOn be formed with the first ejiction opening 22a, on the supplementary bearing 16b of the second 20b of cylinder chamber, be formed with the formingTwo ejiction opening 22b. But, as applying rotary compressor of the present invention, can be also gasCylinder chamber is one, is formed with respectively ejiction opening at the base bearing and the supplementary bearing that form this cylinder chamber.
(the second embodiment)
Based on Fig. 8 and Fig. 9, the second embodiment is described. In addition, the second embodiment with andIn his embodiment, the inscape that the inscape illustrated with the first embodiment is identical is givenIdentical Reference numeral, the repetitive description thereof will be omitted.
The essential structure of the second embodiment is identical with the first embodiment, the second embodiment and firstEmbodiment difference is, is valve seat side at the outlet side of the first ejiction opening 22a, is formed with towards gasThe tapered portion 34 that the emission direction of cryogen extends out successively. In addition, going out at the second ejiction opening 22bMouth side, is also formed with same tapered portion.
In the first ejiction opening 22a, the path size of tapered portion 34 is made as dm1 (mm),And when the maximum diameter size of tapered portion 34 is made as to dm2 (mm), it is than " dm2/dm1 " quiltBe set as making following formula to set up:
1.1≦dm2/dm1≦1.35……………………(6)。
In addition, although omitted diagram, the cone that the outlet side at the second ejiction opening 22b is formedThe path size of shape portion is made as ds1 (mm), when maximum diameter size is made as to ds2 (mm), itsThan " ds2/ds1 is set so that following formula establishment:
1.1≦ds2/ds1≦1.35……………………(7)。
At this, about the setting of the scope of above-mentioned " dm2/dm1 ", use the experiment of presentation graphs 9The chart of result describes. In chart shown in Fig. 9, the minimum using transverse axis as tapered portion 34Footpath size is that dm1 (mm) is the ratio of dm2 (mm) with the maximum diameter size of tapered portion 34" dm2/dm1 ", the compression efficiency using the longitudinal axis as rotary compressor.
Known according to the chart shown in this Fig. 9, in " 1.1≤dm2/dm1≤1.35 " shown in formula (6)Scope in, the overall efficiency of rotary compressor improves 3%～5%.
In the tapered portion of ejiction opening 22b forming at the second ejiction opening 22b too, in formula (7) instituteIn the scope of " 1.1≤ds2/ds1≤1.35 " that show, the overall efficiency raising 3% of rotary compressor～5％。
In such structure, the tapered portion 34 forming at the outlet side of the first ejiction opening 22a meets formula(6), thereby while running in High Rotation Speed territory, the gas refrigeration spraying from the first ejiction opening 22aAgent is flowed along tapered portion 34 as shown in the arrow of Fig. 8. Thus, the gas refrigerant of ejectionPassage resistance further diminishes, and can further reduce the loss that caused by overcompression, and result, canImprove the overall efficiency of rotary compressor 4. Meet the situation of formula (7) in the second ejiction opening 22b sideUnder too.
In addition, any one party Chinese style (6) in the first ejiction opening 22a, the second ejiction opening 22b orIn the situation that person's formula (7) is set up, the first ejiction opening 22a of setting up in formula (6) or formula (7),The second ejiction opening 22b side, can reduce the loss being caused by overcompression. Therefore, there is the first sprayIn the rotary compressor 4 of outlet 22a, second these two ejiction openings of ejiction opening 22b, in the first ejectionAny one party in mouthful 22a, the second ejiction opening 22b meets in the situation of formula (6) or formula (7) alsoCan improve the overall efficiency in High Rotation Speed territory.
In addition, in Fig. 8 the situation taking the valve seat of the outlet side of the first ejiction opening 22a as even shape asExample illustrates, but the shape of this valve seat can be also circular-arc. In this situation, tapered portion 34Size between the apex that large footpath size " dm2 " is arc shape.
(the 3rd embodiment)
Based on Figure 10 to Figure 12, the 3rd embodiment is described.
The essential structure of the 3rd embodiment is identical with the first embodiment, the 3rd embodiment and firstThe difference of embodiment is, is formed with the portion of keeping out of the way 35 at the inner peripheral surface of the first cylinder 15a. Keep out of the wayPortion 35 is formed as the shape with respect to the inner peripheral surface depression of the first cylinder 15a. In addition, although omittedDiagram, but be also formed with the same portion of keeping out of the way at the inner peripheral surface of the second cylinder 15b.
As shown in figure 10, will link on the central point " O " and the first cylinder 15a of the first cylinder 15aThe datum line that the blade reception room 36 forming forms is made as " X ". To play from this datum line " X "Be fixed on upper the first ejiction opening 22a forming of the base bearing 16a of the first cylinder 15a (Fig. 1 reference)Center till angle be made as " θ 1 ". And, will play the first ejiction opening from this datum line " X "The point that 22a and the inner peripheral surface of the first cylinder 15a intersect and at the angle top-cross fork larger than angle " θ 1 "Point till angle be made as " θ 2 ", now, keep out of the way portion 35 and be formed from datum line " X "The scope of angle " θ 3 (θ 3 > θ 2) " in.
Figure 11 is the Y-Y line profile in Figure 10. As shown in figure 11, by the first cylinder 15a'sWhen height dimension is made as " H ", the height dimension of keeping out of the way portion 35 is formed from being fixed with base bearing 16aThe height dimension that rises of the side scope that is " h " in. The height dimension of these first cylinders 15a" H " and the height dimension " h " of keeping out of the way portion 35 are set to " H/2≤h < H ".
Figure 12 is with the stereogram shown in section by a part of the first cylinder 15a. At the first cylinder 15aInner peripheral surface, be formed with the portion of keeping out of the way 35, blade reception room 36, in the first cylinder 15a, suck gasThe inlet hole 37 of cold-producing medium.
In such structure, when compression travel, the first roller 19a (with reference to Fig. 1) and the first cylinder 15aInner peripheral surface carry out contiguously eccentric rotary. At the first roller 19a of eccentric rotary to the first ejiction opening 22aNear the finish time of approaching compression travel, gas refrigerant compressed space stenosis is little, this skyInterior pressure rise. In addition, the inner peripheral surface by the first roller 19a and the first cylinder 15a contiguouslyCarry out eccentric rotary, the lubricating oil in the first cylinder 15a is brought to and becomes in narrow space.
The lubricating oil being brought by the first roller 19a enters into the portion of keeping out of the way near the finish time of compression travel35. Therefore, can prevent from becoming in the compressed narrow space of gas refrigerant in the first cylinder 15aFor causing excessive pressure, hydraulic compression state rises.
At this, in this embodiment, keeping out of the way the angle that portion 35 is formed is " θ 3 ", should " θ 3 "Scope is " θ 3 > θ 2 ", and therefore, the timing that lubricating oil enters into the portion of keeping out of the way 35 becomes early. Therefore, logicalCross rotary compressor 4 made under the situation that starts to accelerate of hydraulic compression in the running of High Rotation Speed territory,The timing that also can enter the portion of keeping out of the way 35 by lubricating oil becomes the generation that early prevents hydraulic compression, Neng GoufangThe breakage of the rotary compressor 4 only being caused by hydraulic compression.
Several embodiment of the present invention has more than been described, but these embodiments just as an exampleAnd point out, and be not intended to limit scope of invention. These new embodiments can be with other various sidesFormula is implemented, and can carry out without departing from the spirit and scope of the invention various omissions, displacement and change.These embodiments and distortion thereof are included in scope of invention and aim, and are included in claimIn the invention that book is recorded and the scope being equal to thereof.
The utilizability of industry
The present invention is used to rotary compressor.
Claims (8)
1. a rotary compressor,
In closed shell, contain motor part and via rotating shaft and this motor with eccentric partThe compression mechanical part that portion links,
Described compression mechanical part has:
Cylinder, described rotating shaft runs through this cylinder;
Roller, chimeric with described eccentric part, make a part for outer peripheral face and the inner peripheral surface of described cylinder on one sideIt is mobile that bias is carried out in contact on one side; And
Base bearing and supplementary bearing, support described rotating shaft, and the end face sealing of described cylinder is comeIn described cylinder, form cylinder chamber;
Be provided with at described base bearing and described supplementary bearing:
Ejiction opening, makes to carry out bias by described roller and moves and compressed work in described cylinder chamberFluid sprays in described closed shell; And
Ejection valve, opens and closes this ejiction opening;
It is characterized in that,
The internal diameter area of described cylinder chamber is made as to A, will be arranged at the described ejiction opening of described base bearingInternal diameter size be made as dm, the internal diameter size of the described ejiction opening that is arranged at described supplementary bearing is made asDs, wherein, the unit of A is mm2, the unit of dm and ds is mm, now, set for make followingFormula (1) and formula (2) at least one party set up,
The volume of described cylinder chamber is made as to V, will be arranged at the bullet of described ejection valve of described base bearingSpring constant is made as Km, and the spring constant of the described ejection valve that is arranged at described supplementary bearing is made as to Ks,Wherein, the unit of V is mm3, the unit of Km and Ks is N/mm, now, set for make followingFormula (3) and formula (4) at least one party set up,
Formula (1), (2), (3), (4) are:
4.6×10－3≦dm/A≦6.5×10－3mm/mm2…………(1)
4.6×10－3≦ds/A≦6.5×10－3mm/mm2…………(2)
1.2×10－4≦Km/V≦3.5×10－4N/mm4………………(3)
1.2×10－4≦Ks/V≦3.5×10－4N/mm4………………(4)
Wherein, at cylinder, be multiple in the situation that, V is the volume of 1 cylinder chamber.
2. rotary compressor as claimed in claim 1, is characterized in that,
Described ejection valve is made up of leaf valve, and this leaf valve has:
Arm, described base bearing or described supplementary bearing are fixed in one end, have flexible; And
Discoid valve body portion, be arranged at described arm another is distolateral, for by described ejiction openingClose;
The appearance and size of described valve body portion is made as to R, the width dimensions of described arm is made as to W,Wherein, the unit of R and W is mm, now, set for following formula (5) is set up,
R/W≥2………………(5)。
3. rotary compressor as claimed in claim 1, is characterized in that,
Be provided with the tapered portion extending out gradually towards emission direction at the outlet side of described ejiction opening,
The path size that is arranged at the described tapered portion in the described ejiction opening of described base bearing is made asDm1, is made as dm2 by the maximum diameter size of this tapered portion, will be arranged at the described spray of described supplementary bearingThe path size of the described tapered portion in outlet is made as ds1, and the maximum diameter size of this tapered portion is made asDs2, wherein, the unit of dm1, dm2, ds1 and ds2 is mm, now, set for make followingAt least one party in formula (6) and formula (7) sets up,
1.1≦dm2/dm1≦1.35……………………(6)
1.1≦ds2/ds1≦1.35……………………(7)。
4. rotary compressor as claimed in claim 2, is characterized in that,
Be provided with the tapered portion extending out gradually towards emission direction at the outlet side of described ejiction opening,
The path size that is arranged at the described tapered portion in the described ejiction opening of described base bearing is made asDm1, is made as dm2 by the maximum diameter size of this tapered portion, will be arranged at the described spray of described supplementary bearingThe path size of the described tapered portion in outlet is made as ds1, and the maximum diameter size of this tapered portion is made asDs2, wherein, the unit of dm1, dm2, ds1 and ds2 is mm, now, set for make followingAt least one party in formula (6) and formula (7) sets up,
1.1≦dm2/dm1≦1.35……………………(6)
1.1≦ds2/ds1≦1.35……………………(7)。
5. a freezing cycle device, is characterized in that, possesses:
Rotary compressor claimed in claim 1;
Condenser, is connected with described rotary compressor;
Expansion gear, is connected with described condenser; And
Evaporimeter, is connected between described expansion gear and described rotary compressor.
6. a freezing cycle device, is characterized in that, possesses:
Rotary compressor claimed in claim 2;
Condenser, is connected with described rotary compressor;
Expansion gear, is connected with described condenser; And
Evaporimeter, is connected between described expansion gear and described rotary compressor.
7. a freezing cycle device, is characterized in that, possesses:
Rotary compressor claimed in claim 3;
Condenser, is connected with described rotary compressor;
Expansion gear, is connected with described condenser; And
Evaporimeter, is connected between described expansion gear and described rotary compressor.
8. a freezing cycle device, is characterized in that, possesses:
Rotary compressor claimed in claim 4;
Condenser, is connected with described rotary compressor;
Expansion gear, is connected with described condenser; And
Evaporimeter, is connected between described expansion gear and described rotary compressor.
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| JP2012-067941 | 2012-03-23 | ||
| JP2012067941 | 2012-03-23 | ||
| PCT/JP2013/053893 WO2013140912A1 (en) | 2012-03-23 | 2013-02-18 | Rotating compressor and freeze-cycle apparatus |
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| CN104081055B true CN104081055B (en) | 2016-05-18 |
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| CN104165140A (en) * | 2014-08-01 | 2014-11-26 | 广东美芝制冷设备有限公司 | Rotary compressor |
| JP6177741B2 (en) * | 2014-08-22 | 2017-08-09 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| WO2016110982A1 (en) * | 2015-01-08 | 2016-07-14 | 三菱電機株式会社 | Multi-cylinder hermetic compressor |
| WO2017006454A1 (en) * | 2015-07-08 | 2017-01-12 | 三菱電機株式会社 | Compressor and refrigeration cycle device |
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| JP2001050184A (en) * | 1999-08-05 | 2001-02-23 | Sanyo Electric Co Ltd | Multiple cylinder rotary compressor |
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| JP2005180317A (en) * | 2003-12-19 | 2005-07-07 | Daikin Ind Ltd | Rotary compressor |
| JP4483656B2 (en) * | 2005-03-31 | 2010-06-16 | ダイキン工業株式会社 | Fluid machinery |
| JP5338275B2 (en) * | 2008-11-25 | 2013-11-13 | ダイキン工業株式会社 | Discharge valve mechanism and rotary compressor |
| JP5328697B2 (en) * | 2010-03-02 | 2013-10-30 | 三菱電機株式会社 | Two-stage compressor and heat pump device |
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- 2013-02-18 JP JP2014506084A patent/JPWO2013140912A1/en active Pending
- 2013-02-18 CN CN201380006906.8A patent/CN104081055B/en active Active
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| US4580604A (en) * | 1983-06-23 | 1986-04-08 | Mitsubishi Denki Kabushiki Kaisha | Discharging valve device for a compressor |
| JPH11210626A (en) * | 1998-01-21 | 1999-08-03 | Toshiba Corp | Hermetic compressor |
| JP2002005057A (en) * | 2000-06-21 | 2002-01-09 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| JP2004308428A (en) * | 2003-04-02 | 2004-11-04 | Calsonic Compressor Seizo Kk | Shut-off valve of gas compressor and gas compressor |
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| WO2013140912A1 (en) | 2013-09-26 |
| JPWO2013140912A1 (en) | 2015-08-03 |
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