CN104081055A - Rotating compressor and freeze-cycle apparatus - Google Patents
Rotating compressor and freeze-cycle apparatus Download PDFInfo
- Publication number
- CN104081055A CN104081055A CN201380006906.8A CN201380006906A CN104081055A CN 104081055 A CN104081055 A CN 104081055A CN 201380006906 A CN201380006906 A CN 201380006906A CN 104081055 A CN104081055 A CN 104081055A
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- China
- Prior art keywords
- rotary compressor
- ejiction opening
- cylinder
- formula
- cylinder chamber
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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
- F01C21/10—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
-
- 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
-
- 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
4.610-3<=dm/A<=6.510-3 (formula 1) and/or 4.610-3<=ds/A<=6.510-3 (formula 2) are true, where A is an inner diameter area of a cylinder chamber (20a, 20b), dm is the inner diameter of a discharge port (22a) on a main bearing (16a), and ds is the inner diameter of a discharge port (22b) of a counter bearing (16b)). 1.210-4<=Km/V<=3.510-4 (formula 3) and/or 1.210-4<=Ks/V<=3.510-4 (formula 4) are true, where V is the volume of a cylinder chamber (20a, 20b), Km is the spring constant of a discharge valve (23a) on the main bearing (16a), and Ks is the spring constant of the discharge valve (23b) on the counter bearing (16b).
Description
Technical field
The freezing cycle device that embodiments of the present invention relate to rotary compressor and used this rotary compressor.
Background technique
As the rotary compressor using in the freezing cycle devices such as air-conditioning equipment, known have there is such structure shown in the invention of recording in JP 2007-92534 communique.Have: cylinder; The running shaft that runs through cylinder; Be arranged at running shaft and in cylinder, carry out the eccentric roller that moves (eccentric rotary); And running shaft axle is supported to two bearings (main bearing, supplementary bearing) that can rotate and the end face sealing of cylinder be formed in cylinder to cylinder chamber.In such rotary compressor, at the lip part of bearing, be provided with for being ejected in ejiction opening and the ejection valve for this ejiction opening is opened and closed of compressed gas refrigerant in cylinder chamber.
In ejection Fa cylinder chamber, compressed gas refrigerant has reached in the situation of authorized pressure and has opened.Then, gas refrigerant is closed after ejiction opening ejection.
Such rotary compressor, except when starting, in most cases turns round in middling speed rotation territory (operating frequency is 30～60Hz) or low speed rotation territory (operating frequency is below 30Hz).Therefore, the compression efficiency in each several part size attention raising middling speed rotation territory or low speed rotation territory is set.
Therefore, the internal diameter size of ejiction opening is in order to reduce dead volume, to reduce expansion-loss and formation as small as possible again.Internal diameter area A (mm with respect to cylinder chamber
2) the ratio " d/A " of internal diameter size d (mm) of ejiction opening be set to " 3 * 10
-3< d/A < 4 * 10
-3(mm/mm
2) ".
In addition, ejection valve is driven valve smoothly during for pressure rise in cylinder chamber and is used the little ejection valve of spring constant, the ejection spring constant K (N/mm) of valve and the volume V (mm of cylinder chamber
3) ratio " K/V " be set to " 0.6 * 10
-4< K/V < 0.7 * 10
-4(N/mm
4) ".
Look-ahead technique document
Patent documentation
Patent documentation 1: JP 2007-92534 communique
Summary of the invention
Yet, making such rotary compressor in the situation that the more than 1.2 times of source power supply frequency, be to turn round in more than 70Hz High Rotation Speed territory, it is large that the passage resistance of ejiction opening becomes.This is because very little relative with the internal diameter size of ejiction opening, compression speed is very fast.And, because the passage resistance of ejiction opening becomes large, cause gas refrigerant in cylinder chamber by excess compression, the loss therefore producing based on overcompression increases and produces the problem that compression efficiency reduces.And, be accompanied by the excess compression of gas refrigerant, to the load of the axial gas refrigerant of rotation, increase, slide part is easily deteriorated, produces the problem that the reliability of slide part reduces.
In addition,, in the situation that the spring constant of ejection valve is less, if rotary compressor turns round in High Rotation Speed territory, can produce the state of affairs of the ejection valve constant time lag of closing.Then, because ejection valve timeing closing postpones, and cause compressed after from the gas refrigerant adverse current of ejiction opening ejection in cylinder chamber.The gas refrigerant of this adverse current and then expand again in cylinder chamber, thus based on expanding again, produce loss, and the compression efficiency of rotary compressor reduces.
The object of embodiments of the present invention is to provide a kind of freezing cycle device that can improve the rotary compressor of compression efficiency and possess this rotary compressor turn round in High Rotation Speed territory in the situation that.
For solving the means of problem
In the rotary compressor of mode of execution, in closed shell, contain motor part and via the compression mechanical part that has the running shaft of eccentric part and this motor part and link, compression mechanical part has: cylinder, running shaft runs through this cylinder; Roller, chimeric with eccentric part, while being contacted, a part for outer circumferential face and the inner peripheral surface of cylinder carry out bias movement; And main bearing and supplementary bearing, supporting rotating shaft, and the end face sealing of cylinder is formed to cylinder chamber in cylinder; At main bearing and supplementary bearing, be provided with: ejiction opening, makes to carry out compressed working fluid in eccentric mobile Er cylinder chamber by roller and spray in closed shell; And ejection valve, this ejiction opening is opened and closed.And, the internal diameter area of cylinder chamber is made as to A (mm
2), by the internal diameter size that is arranged at the ejiction opening of main bearing be made as dm (mm), when the internal diameter size that is arranged at the ejiction opening of supplementary bearing is made as to ds (mm), set at least one party who makes in following formula (1) and formula (2) for and set up, the volume of cylinder chamber is made as to V (mm
3), the spring constant that is arranged at the ejection valve of main bearing is made as to Km (N/mm), when the spring constant that is arranged at the ejection valve of supplementary bearing is made as to Ks (N/mm), sets at least one party who makes in following formula (3) and formula (4) for and set up.
Formula (1), (2), (3), (4) are:
4.6×10
－3≦dm/A≦6.5×10
－3(mm/mm
2)…………(1)
4.6×10
－3≦ds/A≦6.5×10
－3(mm/mm
2)…………(2)
1.2×10
－4≦Km/V≦3.5×10
－4(N/mm
4)………………(3)
1.2×10
－4≦Ks/V≦3.5×10
－4(N/mm
4)………………(4)
Wherein, at cylinder, be a plurality of in the situation that, V is the volume of 1 cylinder chamber.
Embodiment
Below, based on accompanying drawing, embodiments of the present invention are described.
(the first mode of execution)
Based on Fig. 1 to Fig. 7, the first mode of execution is described.Freezing cycle device 1 shown in Fig. 1 has compressor main body 2 and liquid-storage container (accumulator) 3, and possesses the rotary compressor 4 of the gas refrigerant compression of the low pressure as working fluid being made to the gas refrigerant of high pressure.And freezing cycle device 1 has: condenser 5, be connected with the ejection side of compressor main body 2, for making the gas refrigerant condensation of high pressure, make liquid refrigerant; Expansion gear 6, is connected with condenser 5, for liquid refrigerant is reduced pressure; And vaporizer, be connected between expansion gear 6 and liquid-storage container 3, for making liquid refrigerant evaporates.
Compressor main body 2 has and forms closed shell 8 cylindraceous.Accumulate bottom in closed shell 8 lubricant oil 9.And, in closed shell 8, contain the motor part 10 that is positioned at upper side and the compression mechanical part 11 that is positioned at lower side.This motor part 10 and compression mechanical part 11 link via running shaft 12.Running shaft 12 be take the center of long side direction of compressor main body 2 and is rotated as running shaft.
Motor part 10 is so-called motor, for making running shaft 12 rotations.Motor part 10 has rotor 13 and stator 14.Rotor 13 is fixed in running 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 with coil (not shown).
Compression mechanical part 11 is by the gas refrigerant compression of low pressure.Compression mechanical part 11 has the first cylinder 15a that is positioned at upper side and the second cylinder 15b that is positioned at lower side.Between this first cylinder 15a and the second cylinder 15b, be provided with demarcation strip 17.In addition, in the upper-end surface of the first cylinder 15a, be fixed with running shaft 12 is supported to the main bearing 16a that can rotate, in the lower end surface of the second cylinder 15b, be fixed with running shaft 12 is supported to the supplementary bearing 16b that can rotate.
Running shaft 12 runs through the first cylinder 15a, the second cylinder 15b and configures.At this running shaft 12, with 180 ° of phase differences, be provided with the first eccentric part 18a and the second eccentric part 18b of same diameter.There is the first roller 19a the first eccentric part 18a is chimeric, have a second roller 19b the second eccentric part 18b is chimeric.
In the inside of the first cylinder 15a, be formed with the first 20a of cylinder chamber that the two ends of the first cylinder 15a are sealed by main bearing 16a and demarcation strip 17.In the inside of the second cylinder 15b, be formed with the 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, in the second 20b of cylinder chamber, contain the second roller 19b chimeric with the second eccentric part 18b.This first roller 19a, second roller 19b are configured to while the inner peripheral surface line that makes its outer circumferential face with the first cylinder 15a, the second cylinder 15b, contact and carry out bias mobile (eccentric rotary) when running shaft 12 rotation.
In addition,, in the first 20a of cylinder chamber, the second 20b of cylinder chamber, contain the rotation that is accompanied by the first roller 19a, second roller 19b and the blade (blade) (not shown) that these 2 cylinder chamber's interior separations is become to two spaces of volume and pressure variation.The outer circumferential face butt of the front end of this blade and the first roller 19a, second roller 19b.At main bearing 16a, be provided with the first ejection valve system 21a.This first ejection valve system 21a has the first ejiction opening 22a, the first leaf valve (reed valve) 23a and the first valve guard 24a that is formed at main bearing 16a.The first leaf valve 23a by screw thread be fixed on bearing 16a, for the first ejiction opening 22a is opened and closed first ejection valve.The first valve guard 24a screw thread together with the first leaf valve 23a is fixed on main bearing 16a, for limiting the maximum opening of the first leaf valve 23a.The first silencing apparatus (muffler) 25a that this first ejection valve system 21a is installed in main bearing 16a covers.The first silencing apparatus 25a is formed with the ejiction opening 26 of the inside and outside connection that makes the first silencing apparatus 25a.
At supplementary bearing 16b, be provided with the second ejection valve system 21b.This second ejection valve system 21b has the structure identical with the first above-mentioned ejection valve system 21b, has the second ejiction opening 22b, the second leaf valve 23b and the second valve snubber 24b that are formed at supplementary bearing 16b.The second leaf valve 23b by screw thread be fixed on supplementary bearing 16b, for the second ejiction opening 22b is opened and closed second ejection valve.Second valve snubber 24b screw thread together with the second leaf valve 23b is fixed on supplementary bearing 16b, for limiting the maximum opening of the second leaf valve 23b.The second silencing apparatus 25b that this second ejection valve system 21b is installed in supplementary bearing 16b covers.In the second silencing apparatus 25b with the first silencing apparatus 25a in by being joined into gas refrigerant can be moved running through gas refrigerant path of navigation (not shown) that the mode of supplementary bearing 16b, the second cylinder 15b, demarcation strip 17, the first cylinder 15a and main bearing 16a forms.
Liquid-storage container 3 has closed shell 27 cylindraceous.Liquid-storage container 3 is connected so that with vaporizer 7 gas refrigerant being gasified by vaporizer 7 or the liquid refrigerant not gasified by vaporizer 7 flow in closed shell 27.In this closed shell 27, two suction pipes 28 that the mode that be provided with one end upper side opening in closed shell 27, only flows into for the gas refrigerant in closed shell 27 configures.The other end of these suction pipes 28, from the lower end side of closed shell 27 to closed shell 27 extensions, links with the first 20a of cylinder chamber, second 20b of cylinder chamber of compression mechanical part 11.The part of the lower side that is positioned at closed shell 27 in these suction pipes 28, is formed with the oily return aperture 29 that the lubricant oil that accumulates for the bottom in closed shell 27 flows into.
Fig. 2 means the plan view of above-mentioned main bearing 16a.As described above, at this main bearing 16a, be formed with the first ejiction opening 22a.In addition, at main bearing 16a, be formed with screw 30, this screw 30 acts on upper fixing above-mentioned the first leaf valve 23a and the first valve guard 24a of this main bearing 16a for screw (not shown) by screw.The internal diameter size of the first ejiction opening 22a is set to dm (mm).
Although omitted the diagram of plan view,, above-mentioned supplementary bearing 16b is the structure identical with main bearing 16a.Therefore, at supplementary bearing 16b, be formed with the second above-mentioned ejiction opening 22b, the internal diameter size of the second ejiction opening 22b is set to ds (mm).
Fig. 3 means the plan view of the first leaf valve 23a of the installed position configuration on main bearing 16a.The first leaf valve 23a is formed by tabular member.The first leaf valve 23a has arm 32, valve body portion 33.Arm 32 has flexible, is at one end formed with for fixing screw and inserts logical mounting hole 31.It is distolateral that valve body portion 33 is arranged on another of arm 32, and, with the discoid size that the first ejiction opening 22a can be closed that forms.The boundary dimension of valve body portion 33 is set to R (mm), the width dimensions of arm 32 is set to W (mm), it is set to " R/W >=2 " than " R/W ", and valve body portion 33 becomes necking down shape from valve body portion 33 towards arm 32 with the attachment portion of arm 32.
Although omitted the diagram of plan view, the second leaf valve 23b that is installed on supplementary bearing 16b also forms the shape identical with the first leaf valve 23a.
At this, in this rotary compressor 4, the first 20a of cylinder chamber, the second 20b of cylinder chamber internal diameter area are separately made as to A (mm
2), 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 internal diameter area A (mm of the first 20a of cylinder chamber
2) with the ratio " dm/A (mm/mm of the internal diameter size dm (mm) of the first ejiction opening 22a
2) ", the internal diameter area A (mm of the second 20b of cylinder chamber
2) with ratio " the ds/A " (mm/mm of the internal diameter size ds (mm) of the second ejiction opening 22b
2) be set so that respectively following formula sets up:
4.6×10
－3≦dm/A≦6.5×10
－3(mm/mm
2)…………(1)
4.6×10
－3≦ds/A≦6.5×10
－3(mm/mm
2)…………(2)。
In addition, in this rotary compressor 4, the first 20a of cylinder chamber, the second 20b of cylinder chamber volume are separately made as to V (mm3), 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, the volume V (mm of the first 20a of cylinder chamber
3) with the ratio " Km/V (N/mm of the spring constant Km (N/mm) of the first leaf valve 23a
4) ", the volume V (mm of the second 20b of cylinder chamber
3) with the ratio " Ks/V (N/mm of the spring constant Ks (N/mm) of the second leaf valve 23b
4) " be set so that respectively following formula sets up:
1.2×10
－4≦Km/V≦3.5×10
－4(N/mm
4)………………(3)
1.2×10－4≦Ks/V≦3.5×10－4(N/mm
4)………………(4)。
In addition, in cylinder chamber, be a plurality of in the situation that, the volume " V " of the first 20a of cylinder chamber, the second 20b of cylinder chamber shown in formula (3), formula (4) 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, the boundary dimension of valve body portion 33 is made as to R (mm), when the width dimensions of arm 32 is made as to W (mm), the boundary dimension R of valve body portion 33 (mm) is set so that following formula establishment with the ratio " R/W " of the width dimensions W (mm) of arm 32:
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 boundary dimension 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 running shaft 12 (from rotating center to the 18a of running shaft 12, the distance at the second eccentric part 18b center) is respectively 4mm,
The internal diameter size of the first ejiction opening 22a (dm) is 8mm,
The internal diameter size of the second ejiction opening 22b (ds) is 8mm.
At this, about above-mentioned " dm/A (mm/mm
2) ", " ds/A (mm/mm
2) " the setting of scope, with the chart of the experimental result of presentation graphs 4, describe.Fig. 4 means the internal diameter area A (mm of the first cylinder chamber
2) and the ratio " dm/A " of internal diameter size dm (mm) of the first ejiction opening and the chart of the experimental result of the relation between the compression efficiency of rotary compressor.
In addition, this experiment is middling speed to be rotated to rotating speed in territory be made as 40Hz, the rotating speed in High Rotation Speed territory is made as to 90Hz carries out.In addition, the leaf valve using in this experiment is the leaf valve that rotary compressor in the past 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/mm
2) ", the compression efficiency using the longitudinal axis as rotary compressor.
Known according to the chart shown in this Fig. 4, the in the situation that rotary compressor having carried out running in middling speed rotation territory, along with " dm/A (mm/mm
2) " value become large, that is, along with the ratio of the internal diameter size " dm " of ejiction opening becomes large, 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/mm
2) " value " 4.6 * 10
-3≤ dm/A≤6.5 * 10
-3" scope in time compression efficiency improve, at " dm/A (mm/mm
2) " value be 5.5 * 10
-3situation under, obtained maximum compression efficiency.Therefore, by by " dm/A (mm/mm
2) " 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/mm
2) " situation be that example is illustrated, but at " ds/A (mm/mm
2) " situation under too.
Then, about above-mentioned " Km/V (N/mm
4) ", " Ks/V (N/mm
4) " the setting of scope, with the chart of the experimental result of presentation graphs 5, illustrate.Fig. 5 means the volume V (mm of cylinder chamber
3) with the ratio " K/V (N/mm of spring constant K (N/mm) of ejection valve
4) " and the compression efficiency of rotary compressor between the chart of experimental result of relation.
In chart shown in Fig. 5, using transverse axis as " Km/V (N/mm
4) ", the compression efficiency using the longitudinal axis as rotary compressor.In addition, in this experiment, make " dm/A (mm/mm
2) " value be fixed as 5.5 * 10
-3, make the spring constant " Km " of leaf valve variable.In addition, experiment is carried out for the running in High Rotation Speed territory.
Known according to the chart shown in this Fig. 5, by so that " Km/V (N/mm
4) " value become " 1.2 * 10
-4≤ Km/V≤3.5 * 10
-4(N/mm
4) " the mode of scope set the spring constant " Km " of leaf valve, can improve the compression efficiency of rotary compressor.Before with " Km/V (N/mm
4) " situation be that example is illustrated, but at " Ks/V (N/mm
4) " situation under too.
In such structure, in this rotary compressor 4, by motor part 10 energisings, make the first roller 19a and second roller 19b carry out eccentric rotary around the center line of running shaft 12, compression mechanical part 11 is driven.
Compression mechanical part 11 driven in the situation that, be accompanied by the eccentric rotary of the first roller 19a, second roller 19b, volume and the pressure in two spaces in the first 20a of cylinder chamber, the second 20b of cylinder chamber change.Because this volume and pressure change, thereby the gas refrigerant of low pressure is inhaled in the first 20a of cylinder chamber, the second 20b of cylinder chamber through suction pipe 28 from liquid-storage container 3 is interior.Then, the gas refrigerant of the low pressure of suction is compressed in the first 20a of cylinder chamber, the second 20b of cylinder chamber, becomes the gas refrigerant of high pressure.
In the first cylinder 15a, the pressure rise of the gas refrigerant in the first 20a of cylinder chamber is to the timing of specified value, and the first leaf valve 23a opens.The gas refrigerant of the high pressure in the first 20a of cylinder chamber is ejected in the first silencing apparatus 25a through the first ejiction opening 22a.Being ejected into gas refrigerant in the first silencing apparatus 25a is ejected in closed shell 8 through the ejiction opening 26 of the first silencing apparatus 25a.
In addition, in the second cylinder 15b, the pressure rise of the gas refrigerant in the second 20b of cylinder chamber is to the timing of specified value, and the second leaf valve 23b opens.The gas refrigerant of the high pressure in the second 20b of cylinder chamber is ejected in the second silencing apparatus 25b through the second ejiction opening 22b.Be ejected into gas refrigerant in the second silencing apparatus 25b after in above-mentioned gas refrigerant path of navigation flows into the first silencing apparatus 25a, and then through ejiction opening 26, be ejected in closed shell 8 in the first silencing apparatus 25a.
The gas refrigerant that is ejected into the high pressure in closed shell 8 after compressed in the first 20a of cylinder chamber, the second 20b of cylinder chamber flows in condenser 5, heat radiation in condenser 5 and become liquid refrigerant.This liquid refrigerant flows into expansion gear 6 and is depressurized, and is depressurized in rear inflow vaporizer 7 and evaporates by absorbing heat, and becomes gas refrigerant.In the gas refrigerant of vaporizer 7 interior evaporations flows into liquid-storage container 3 and quilt is carried out gas-liquid separation (separation of the liquid constituent that gas refrigerant comprised).Wherein, only gas refrigerant is from the interior process of suction pipe 28 of liquid-storage container 3 and be supplied in the first 20a of cylinder chamber, second 20b of cylinder chamber of compression mechanical part 11, again compressed.
At this, Fig. 6 be make above-mentioned formula (1), formula (2), formula (3), formula (4) all satisfied present embodiment rotary compressor 4, formula (1), formula (2), formula (3), formula (4) all ungratified past case rotary compressor, meet formula (1) and formula (2) but the PV line chart that do not meet formula (3) and measure the rotary compressor of the comparative example of formula (4) has carried out running in High Rotation Speed territory in the situation that.
Specifically, in the rotary compressor of past case, dm/A is made as to 3.5 * 10
-3(mm/mm
2), ds/A is made as to 3.5 * 10
-3(mm/mm
2), Km/V is made as to 0.8 * 10
-4(N/mm
4), Ks/V is made as to 0.8 * 10
-4(N/mm
4).
In the rotary compressor of comparative example, dm/A is made as to 5.5 * 10
-3(mm/mm
2), ds/A is made as to 5.5 * 10
-3(mm/mm
2), Km/V is made as to 0.8 * 10
-4(N/mm
4), Ks/V is made as to 0.8 * 10
-4(N/mm
4).
In the rotary compressor 4 of present embodiment, dm/A is made as to 5.5 * 10
-3(mm/mm
2), ds/A is made as to 5.5 * 10
-3(mm/mm
2), Km/V is made as to 1.7 * 10
-4(N/mm
4), Ks/V is made as to 1.7 * 10
-4(N/mm
4).
According to the PV line chart shown in Fig. 6, in the rotary compressor of past case, because the internal diameter size of ejiction opening is 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 the constant time lag that this leaf valve cuts out, cause temporarily gas refrigerant from the high pressure of ejiction opening ejection from ejiction opening adverse current in cylinder chamber.Then, the gas refrigerant of this adverse current expands in cylinder chamber again, thereby by expanding 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, and therefore, from the passage resistance of the gas refrigerant of this ejiction opening process, diminishes, and the loss being produced by overcompression diminishes.And, being accompanied by the loss being produced by overcompression and diminishing, the power of the directive effect of closing to prevention leaf valve diminishes, and therefore, the delay of leaf valve timeing closing is suppressed, by the loss causing of expanding again, is diminished.
In the rotary compressor 4 of present embodiment, the internal diameter size of ejiction opening (the first ejiction opening 22a, the second ejiction opening 22b) and then change are large.Therefore, from the passage resistance of the gas refrigerant of these ejiction openings (the first ejiction opening 22a, the second ejiction opening 22b) process, diminish, the loss being caused by overcompression diminishes.And, use the large and hard leaf valve (the first leaf valve 23a, the second leaf valve 23b) of spring constant, therefore, the timing that the leaf valve (the first leaf valve 23a, the second leaf valve 23b) after the ejection of the gas refrigerant of high pressure cuts out becomes early.Therefore, from ejiction opening (the first ejiction opening 22a, the second ejiction opening 22b) to cylinder chamber (the first 20a of cylinder chamber, the second 20b of cylinder chamber), the adverse current of interior gas refrigerant is suppressed, by the loss causing of expanding again, is diminished.
The in the situation that of having sucked gas refrigerant in cylinder chamber, can produce the loss being caused by overexpansion, but, in the rotary compressor that is lost in past case being caused by this overexpansion, the rotary compressor of comparative example and the rotary compressor of present embodiment 4, similarly produce.
Fig. 7 means at the rotary compressor of the illustrated past case of Fig. 6, the chart of the relation between the rotating speed in the rotary compressor 4 of the rotary compressor of comparative example, present embodiment and overall efficiency (overall efficiency of rotary compressor).Known according to the chart of Fig. 7, in the rotary compressor of past case, 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, and in High Rotation Speed territory, overall efficiency is high, and the maximum value of overall efficiency is little.And in the rotary compressor 4 of present embodiment, in middling speed rotation territory, overall efficiency is low, in High Rotation Speed territory, overall efficiency is compared and is enhanced with the rotary compressor of comparative example.
Therefore, meet the rotary compressor 4 of formula (1)～formula (4) in the overall efficiency raising in High Rotation Speed territory, can realize the minimizing of power consumption.
In addition, in the situation that any one party Chinese style (1) in the first ejiction opening 22a, the second ejiction opening 22b or formula (2) set up, the first ejiction opening 22a, the second ejiction opening 22b side in formula (1) or formula (2), set up can reduce the loss being caused by overcompression.In addition, in the situation that any one party Chinese style (3) in the first leaf valve 23a, the second leaf valve 23b or formula (4) set up, the first leaf valve 23a, the second leaf valve 23b side in formula (3) or formula (4), set up can reduce the loss of expanding and causing by again.Therefore, in thering is the rotary compressor 4 of the first ejiction opening 22a, second these two ejiction openings of ejiction opening 22b, in any one party in the first ejiction opening 22a, the second ejiction opening 22b, meet formula (1) or formula (2) and in the situation that meet formula (3) or formula (4) in any one party in the first leaf valve 23a, the second leaf valve 23b, can improve the overall efficiency in High Rotation Speed territory.
Then, as shown in Figure 3, in the first leaf valve 23a, the boundary dimension R of valve body portion 33 (mm) is set to " R/W >=2 " with the ratio of the width dimensions W (mm) of arm 32, and valve body portion 33 becomes necking down shape with the attachment portion of arm 32.Therefore,, when the first leaf valve 23a opens, from the gas refrigerant periphery of valve body portion 33 and periphery of arm 32 with shadow representation from Fig. 3 of the first ejiction opening 22a ejection, pass through.Therefore, it is large that the area of passage of the gas refrigerant spraying from the first ejiction opening 22a becomes, and the flow velocity of the gas refrigerant of ejection reduces.Thus, can reduce gas refrigerant from the first ejiction opening 22a ejection with respect to the first leaf valve 23a that wants to close to the power that stops its directive effect of closing.Therefore, can prevent that leaf valve timeing closing from producing delay and reducing the loss by expansion causes again.About this point, in forming the second leaf valve 23b identical shaped with the first leaf valve 23a too.
In addition, the boundary dimension R of valve body portion 33 (mm) is set to " R/W >=2 " with the ratio " R/W " of the width dimensions W (mm) of arm 32, and therefore, the first leaf valve 23a is in the easy distortion of arm 32 part.Therefore, can prevent the single-ended butt of valve body portion 33, and improve valve body portion 33 to the close property of valve seat part.Then, by improving valve body portion 33 with respect to the close property of valve seat part, can improve the compression performance in the first 20a of cylinder chamber.And, can prevent the damage of the first ejiction opening 22a of being caused by single-ended butt, can obtain the valve system that reliability is high.About this point, in forming the second leaf valve 23b identical shaped with the first leaf valve 23a too.
In addition, in the present embodiment, to the first roller 19a, second roller 19b and blade split the rotary compressor that forms be illustrated, but the present invention also can be applied in the rotary compressor (rotation type compressor) that roller and blade form.
In addition, in present embodiment, the following situation of take is illustrated as example: have the first 20a of cylinder chamber, the second 20bZhe Liangge cylinder chamber of cylinder chamber, on the main bearing 16a that forms the first 20a of cylinder chamber, be formed with the first ejiction opening 22a, on the supplementary bearing 16b that forms the second 20b of cylinder chamber, be formed with the second ejiction opening 22b.But, as applying rotary compressor of the present invention, can be also that cylinder chamber is one, at the main bearing and the supplementary bearing that form this cylinder chamber, is formed with respectively ejiction opening.
(the second mode of execution)
Based on Fig. 8 and Fig. 9, the second mode of execution is described.In addition, in the second mode of execution and other mode of executions, to the constituting component that the constituting component illustrated with the first mode of execution is identical, give identical reference character, the repetitive description thereof will be omitted.
The essential structure of the second mode of execution is identical with the first mode of execution, and the second mode of execution and the first mode of execution difference be, at the outlet side of the first ejiction opening 22a, is valve seat side, is formed with the tapered portion 34 that the emission direction towards gas refrigerant extends out successively.In addition, at the outlet side of the second ejiction opening 22b, be also formed with same tapered portion.
In the first ejiction opening 22a, when the path size of tapered portion 34 is made as to dm1 (mm) and the maximum diameter size of tapered portion 34 is made as to dm2 (mm), it is set so that than " dm2/dm1 " following formula sets up:
1.1≦dm2/dm1≦1.35……………………(6)。
In addition, although omitted diagram, the path size of the tapered portion that outlet side at the second ejiction opening 22b is formed is made as ds1 (mm), when maximum diameter size is made as to ds2 (mm), its than " ds2/ds1 is set so that following formula sets up:
1.1≦ds2/ds1≦1.35……………………(7)。
At this, about the setting of the scope of above-mentioned " dm2/dm1 ", with the chart of the experimental result of presentation graphs 9, describe.In chart shown in Fig. 9, the path size using transverse axis as tapered portion 34 is that dm1 (mm) is the ratio " dm2/dm1 " of dm2 (mm) with the maximum diameter size of tapered portion 34, the compression efficiency using the longitudinal axis as rotary compressor.
Known according to the chart shown in this Fig. 9, in the scope of " 1.1≤dm2/dm1≤1.35 " shown in formula (6), the overall efficiency of rotary compressor improves 3%～5%.
In the tapered portion of the ejiction opening 22b forming at the second ejiction opening 22b, too, in the scope of " 1.1≤ds2/ds1≤1.35 " shown in formula (7), the overall efficiency of rotary compressor improves 3%～5%.
In such structure, the tapered portion 34 forming at the outlet side of the first ejiction opening 22a meets formula (6), thereby while turning round in High Rotation Speed territory, from the gas refrigerant of the first ejiction opening 22a ejection, as shown in the arrow of Fig. 8, along tapered portion 34, flow.Thus, the passage resistance of the gas refrigerant of ejection further diminishes, and can further reduce the loss that caused by overcompression, and result can improve the overall efficiency of rotary compressor 4.In the situation that the second ejiction opening 22b side meets formula (7) too.
In addition, in the situation that any one party Chinese style (6) in the first ejiction opening 22a, the second ejiction opening 22b or formula (7) are set up, the first ejiction opening 22a, the second ejiction opening 22b side in formula (6) or formula (7) establishment, can reduce the loss being caused by overcompression.Therefore, in having the rotary compressor 4 of the first ejiction opening 22a, second these two ejiction openings of ejiction opening 22b, in the situation that any one party in the first ejiction opening 22a, the second ejiction opening 22b meets formula (6) or formula (7) also can improve the overall efficiency in High Rotation Speed territory.
In addition, the situation that the valve seat of outlet side of the first ejiction opening 22a of take in Fig. 8 is even shape illustrates as example, but the shape of this valve seat can be also circular-arc.In this situation, the maximum diameter size " dm2 " of tapered portion 34 is the size between the apex of arc shape.
(the 3rd mode of execution)
Based on Figure 10 to Figure 12, the 3rd mode of execution is described.
The essential structure of the 3rd mode of execution is identical with the first mode of execution, and the difference of the 3rd mode of execution and the first mode of execution is, at the inner peripheral surface of the first cylinder 15a, is formed with the portion of keeping out of the way 35.Keep out of the way portion 35 and form the shape with respect to the inner peripheral surface depression of the first cylinder 15a.In addition, although omitted diagram, at the inner peripheral surface of the second cylinder 15b, be also formed with the same portion of keeping out of the way.
As shown in figure 10, the central point " O " and the first cylinder 15a reference line that above the blade containing room 36 of formation forms that link the first cylinder 15a are made as to " X ".The angle playing from this reference line " X " till the first ejiction opening 22a center of the main bearing 16a that is fixed on the first cylinder 15a (Fig. 1 reference) formation is made as to " θ 1 ".And, by play point and the angle till the point of the angle top-cross fork larger than angle " θ 1 " that the inner peripheral surface of the first ejiction opening 22a with the first cylinder 15a intersect from this reference line " X ", be made as " θ 2 ", now, keeping out of the way portion 35 is formed in the scope of the angle " θ 3 (θ 3 > θ 2) " from reference line " X ".
Figure 11 is the Y-Y line sectional drawing in Figure 10.As shown in figure 11, when the height dimension of the first cylinder 15a is made as to " H ", the height dimension of keeping out of the way portion 35 is formed in the scope that the height dimension from being fixed with a side of main bearing 16a is " h ".The height dimension " H " of these first cylinders 15a 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 inner peripheral surface of the first cylinder 15a, be formed with the portion of keeping out of the way 35, blade containing room 36, to the inlet hole 37 of inhaling air cryogen in the first cylinder 15a.
In such structure, during compression stroke, the first roller 19a (with reference to Fig. 1) carries out eccentric rotary contiguously with the inner peripheral surface of the first cylinder 15a.At the first roller 19a of eccentric rotary, near the finish time of the approaching compression stroke of the first ejiction opening 22a, gas refrigerant compressed space stenosis is little, the pressure rise in this space.In addition, the inner peripheral surface by the first roller 19a and the first cylinder 15a carries out eccentric rotary contiguously, and the lubricant oil in the first cylinder 15a is brought to and becomes in narrow space.
The lubricant oil being brought by the first roller 19a enters into the portion of keeping out of the way 35 near the finish time of compression stroke.Therefore, can prevent from becoming hydraulic compression state in the compressed narrow space of gas refrigerant in the first cylinder 15a and cause excessive pressure to rise.
At this, in this mode of execution, keeping out of the way the angle that portion 35 is formed is " θ 3 ", and scope that should " θ 3 " be " θ 3 > θ 2 ", and therefore, the timing that lubricant oil enters into the portion of keeping out of the way 35 becomes morning.Therefore, by making rotary compressor 4, in High Rotation Speed territory, running makes under the situation that starts to accelerate of hydraulic compression, the timing that also can enter the portion of keeping out of the way 35 by lubricant oil becomes the generation that early prevents hydraulic compression, can prevent the breakage of the rotary compressor 4 that caused by hydraulic compression.
Several mode of execution of the present invention has more than been described, but these mode of executions just point out as an example, and be not intended to limit scope of invention.These new mode of executions can be implemented with other variety of ways, can carry out various omissions, displacement and change without departing from the spirit and scope of the invention.These mode of executions and distortion thereof are included in scope of invention and aim, and are included in the invention that claims record and in the scope being equal to.
The utilizability of industry
The present invention is used to rotary compressor.
Accompanying drawing explanation
Fig. 1 is the structural drawing that includes the freezing cycle device of the rotary compressor representing with section in the first mode of execution.
Fig. 2 means the plan view of main bearing.
Fig. 3 means the plan view of ejection valve.
Fig. 4 means the internal diameter area A (mm of the first cylinder chamber
2) and the ratio " dm/A " of internal diameter size dm (mm) of the first ejiction opening and the chart of the experimental result of the relation between the compression efficiency of rotary compressor.
Fig. 5 means the volume V (mm of cylinder chamber
3) with the ratio " K/V (N/mm of spring constant K (N/mm) of ejection valve
4) " and the compression efficiency of rotary compressor between the chart of experimental result of relation.
Fig. 6 mean make to meet formula (1)～(4) rotary compressor, formula (1)～(4) all ungratified past case rotary compressor, meet formula (1), (2) but PV line chart that the rotary compressor that do not meet the comparative example of formula (3), (4) is measured carried out running in High Rotation Speed territory in the situation that.
Fig. 7 means in the rotary compressor that meets formula (1)～(4), formula (1)～(4) rotary compressors of ungratified past case all, meet formula (1)～(2) but do not meet rotating speed in the rotary compressor of comparative example of formula (3), (4) and the chart of the experimental result of the relation between the overall efficiency of rotary compressor.
Fig. 8 means the vertical profile plan view of the shape of the ejiction opening in the second mode of execution.
Fig. 9 means the path size dm1 of the tapered portion that arranges in the ejection side of ejiction opening and the chart of the ratio " dm2/dm1 " of maximum diameter size dm2 and the experimental result of the relation between the overall efficiency of rotary compression.
Figure 10 means the plan view of the cylinder in the 3rd mode of execution.
Figure 11 means the Y-Y line sectional drawing in Figure 10.
Figure 12 is the stereogram that a part for the cylinder of Figure 10 is represented with section.
Claims (8)
1. a rotary compressor,
In closed shell, contain motor part and via the compression mechanical part that there is the running shaft of eccentric part and this motor part and link,
Described compression mechanical part has:
Cylinder, described running shaft runs through this cylinder;
Roller, chimeric with described eccentric part, while being contacted, a part for outer circumferential face and the inner peripheral surface of described cylinder carry out bias movement; And
Main bearing and supplementary bearing, support described running shaft, and the end face sealing of described cylinder is formed to cylinder chamber in described cylinder;
At described main bearing and described supplementary bearing, be provided with:
Ejiction opening, make by described roller carry out bias mobile and in described cylinder chamber compressed working fluid in described closed shell, spray; 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 (mm
2), by the internal diameter size that is arranged at the described ejiction opening of described main bearing be made as dm (mm), when the internal diameter size that is arranged at the described ejiction opening of described supplementary bearing is made as to ds (mm), setting at least one party who makes in following formula (1) and formula (2) for sets up
The volume of described cylinder chamber is made as to V (mm
3), by the spring constant that is arranged at the described ejection valve of described main bearing be made as Km (N/mm), when the spring constant that is arranged at the described ejection valve of described supplementary bearing is made as to Ks (N/mm), setting at least one party who makes in following formula (3) and formula (4) for sets up
Formula (1), (2), (3), (4) are:
4.6×10
－3≦dm/A≦6.5×10
－3(mm/mm
2)…………(1)
4.6×10
－3≦ds/A≦6.5×10
－3(mm/mm
2)…………(2)
1.2×10
－4≦Km/V≦3.5×10
－4(N/mm
4)………………(3)
1.2×10
－4≦Ks/V≦3.5×10
－4(N/mm
4)………………(4)
Wherein, at cylinder, be a plurality of 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 consists of leaf valve, and this leaf valve has:
Arm, described main 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 described ejiction opening is closed;
The boundary dimension of described valve body portion is made as to R (mm), when the width dimensions of described arm is made as to W (mm), sets for following formula (5) is set up,
R/W≥2………………(5)。
3. rotary compressor as claimed in claim 1, is characterized in that,
Outlet side at described ejiction opening is provided with the tapered portion extending out gradually towards emission direction,
By the path size that is arranged at the described tapered portion in the described ejiction opening of described main bearing be made as dm1 (mm), by the maximum diameter size of this tapered portion be made as dm2 (mm), by the path size that is arranged at the described tapered portion in the described ejiction opening of described supplementary bearing be made as ds1 (mm), when the maximum diameter size of this tapered portion is made as to ds2 (mm), setting at least one party who makes in following formula (6) and formula (7) for 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,
Outlet side at described ejiction opening is provided with the tapered portion extending out gradually towards emission direction,
By the path size that is arranged at the described tapered portion in the described ejiction opening of described main bearing be made as dm1 (mm), by the maximum diameter size of this tapered portion be made as dm2 (mm), by the path size that is arranged at the described tapered portion in the described ejiction opening of described supplementary bearing be made as ds1 (mm), when the maximum diameter size of this tapered portion is made as to ds2 (mm), setting at least one party who makes in following formula (6) and formula (7) for 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
Vaporizer, 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
Vaporizer, 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
Vaporizer, 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
Vaporizer, is connected between described expansion gear and described rotary compressor.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| 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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| CN104081055A true CN104081055A (en) | 2014-10-01 |
| CN104081055B CN104081055B (en) | 2016-05-18 |
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| JP (1) | JPWO2013140912A1 (en) |
| CN (1) | CN104081055B (en) |
| WO (1) | WO2013140912A1 (en) |
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| CN106337814A (en) * | 2015-07-08 | 2017-01-18 | 三菱电机株式会社 | Compressor and refrigeration cycle device |
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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 |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN104081055B (en) | 2016-05-18 |
| WO2013140912A1 (en) | 2013-09-26 |
| WO2013140912A9 (en) | 2014-08-07 |
| JPWO2013140912A1 (en) | 2015-08-03 |
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