CN102619755B - Compressor and refrigerating cycle apparatus - Google Patents
Compressor and refrigerating cycle apparatus Download PDFInfo
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- CN102619755B CN102619755B CN201210031199.5A CN201210031199A CN102619755B CN 102619755 B CN102619755 B CN 102619755B CN 201210031199 A CN201210031199 A CN 201210031199A CN 102619755 B CN102619755 B CN 102619755B
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Abstract
The invention discloses a compressor and a refrigerating cycle apparatus, capable of inhibiting the decrease of mechanical tightness resulting from the division of the cylinder chamber into an inhalation side and a discharging side and providing high volume efficiency. The compressor comprises an integrally formed cylinder, a drum, and blades, wherein the cylinder is formed by integrally forming the bearing portion and the cylinder portion; the cylinder chamber of the cylinder portion is enclosed by an enclosing member that is separately formed with the cylinder; the drum is configured to rotate in the cylinder chamber in a eccentric manner; and the blades are configured to be capable of conducting reciprocating sliding in a blade groove arranged at the cylinder portion. The radius of curvature of the first corner portion between the periphery of the drum and the side end face of the bearing portion is formed smaller than the that of the boundary corner portion between the internal circumference of the cylinder chamber and the internal surface of the bearing porition.
Description
Technical field
Embodiments of the present invention relate to a kind of compressor and comprise the refrigerating circulatory device of this compressor.
Background technique
As general compressor, there will be a known revolution type compressor as described below, in this revolution type compressor, by making cylinder eccentric rotary in the cylinder chamber of compression mechanical part, carrying out compressed fluid.The compression mechanical part of this compressor comprises: cylinder part, and this cylinder part has the cylinder chamber impaled by cylinder inner peripheral surface; Closure member, this closure member countershaft is supported, and countercylinder room is closed; And blade, this blade abuts with the outer circumferential face of cylinder, will be divided into two into suction side and discharge side in cylinder chamber.
In addition, above-mentioned compressor also comprises the compression mechanical part that cylinder part and bearing portion form as one.
When cylinder part and bearing portion form as one, in process of production, the place of portion, corner, border in the cylinder chamber on the internal surface being located at cylinder part forms the curved surface with certain curvature radius.In addition, in cylinder chamber, the corner portion place relative with corner, the border portion in cylinder chamber of the cylinder of eccentric rotary also arranges the curved surface with same curvature radius.
But, if make the radius of curvature in corner, the border portion in cylinder chamber identical with the radius of curvature in the corner portion of the relative with corner, border portion of cylinder, then can the outer circumferential face of cylinder and and the front-end face of blade that abuts against of outer circumferential face between form clearance space.If the clearance space formed between the outer circumferential face and the front-end face of blade of cylinder is comparatively large, then can be reduced by the mechanical seal being divided into two into the blade of suction side and discharge side in cylinder chamber, the volumetric efficiency of compressor reduces.
Patent documentation 1: Japanese Patent Laid-Open 10-131879 publication
Summary of the invention
According to the embodiment of the present invention, a kind of compressor that mechanical seal reduces, volumetric efficiency is high that can suppress because of the blade by being divided into two into suction side and discharge side in cylinder chamber is provided.
The compressor of embodiment of the present invention comprises: rotating shaft; And one-piece type cylinder, the bearing portion that countershaft is supported by this one-piece type cylinder and the cylinder part with the cylinder chamber impaled by cylinder inner peripheral surface form as one and form.
The cylinder chamber of one-piece type cylinder is closed by the closure member formed with one-piece type cylinder split, and is provided with cylinder that being configured to can slide in cylinder chamber rotates and is configured to the blade that can reciprocatingly slide in the blade groove being located at cylinder part.
In addition, the radius of curvature in the first corner portion between the outer circumferential face of cylinder and bearing portion side is formed as less than the radius of curvature in corner, the border portion between the cylinder inner peripheral surface of one-piece type cylinder and bearing portion internal surface.
By this, a kind of mechanical seal and lubricity is high, volumetric efficiency is high compressor can be provided.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the compressor of the first mode of execution.
Fig. 2 is the cross-sectional schematic of the major component in the cylinder chamber of the first mode of execution.
Fig. 3 is the cross-sectional schematic of the major component in the cylinder chamber of the second mode of execution.
Fig. 4 is the cross-sectional schematic of the major component in the cylinder chamber of the 3rd mode of execution.
Fig. 5 is the schematic diagram of the refrigerating circulatory device of the 4th mode of execution.
(symbol description)
1 closed shell
2 compression mechanical parts
3 motor part
4 cylinder chamber
5 cylinder part
6 main shaft bearing portion
7 supplementary bearings
8 eccentric shaft portions
9 rotating shafts
10 cylinders
10a outer circumferential face
11 blade grooves
12 blades
12a front-end face
14 discharging valve devices
16 corner, borders portion
18 first corners portion
19 second corners portion
20 one-piece type cylinders
30 springs
31 lubricant oil
40 gas-liquid separators
100 compressors
101 four-way valves
102 first heat exchangers
103 expansion gears
104 second heat exchangers
A refrigerating circulatory device
Embodiment
Below, based on accompanying drawing, embodiments of the present invention are described.
(the first mode of execution)
Fig. 1 is the longitudinal section of the compressor 100 representing present embodiment, and Fig. 2 is the schematic diagram representing its major component.
The compressor 100 of the first mode of execution is the closed rotary compressor compressed refrigeration agent, the motor part 3 above the inside of longitudinally longer cylindric closed shell 1 comprises the compression mechanical part 2 below being configured in and is configured in.
Compression mechanical part 2 is connected by rotating shaft 9 with motor part 3, and the rotating power produced in motor part 3 is passed to compression mechanical part 2 via rotating shaft 9.
Compression mechanical part 2 has one-piece type cylinder 20.The cylinder part 5 being positioned at below is used for rotating shaft 9 to be supported to revolvable main shaft bearing portion 6 and forms as one with the top being configured in cylinder part 5 and form by one-piece type cylinder 20.
One-piece type cylinder 20 is provided with cylinder chamber 4, and this cylinder chamber 4 is the blank parts worn from the below end face of cylinder part 5 by cutting such as facing cutter processing.Can eccentric rotary and from being rotatably configured with eccentric shaft portion 8 and the cylinder 10 chimeric with eccentric shaft portion 8, wherein, above-mentioned eccentric shaft portion 8 is arranged on the long side direction intermediate portion of rotating shaft 9 in this cylinder chamber 4.The lower opening portion of cylinder chamber 4 is closed by supplementary bearing 7, and this supplementary bearing 7 is not only closure member, itself or the support member of rotating shaft 9.
That is, as shown in Figure 2, cylinder chamber 4 closes by the bottom interior surface 6a of the inner peripheral surface 4a of cylinder part 5, main shaft bearing portion 6 with as the supplementary bearing 7 of closure member.
In addition, cylinder 10 is formed as the substantially cylindrical shape with outer circumferential face 10a, one end side 10b and the other end side 10c, wherein, above-mentioned outer circumferential face 10a relative with the inner peripheral surface 4a of cylinder chamber 4 and do not have concavo-convex, formed glossily, above-mentioned one end side 10b is the plane relative with bearing portion, and above-mentioned the other end side 10c is the plane relative with above-mentioned closure member.
Cylinder part 5 is equipped with the blade groove 11 to cylinder chamber 4 opening, and substantially rectangular blade 12 is configured to freely to move back and forth.Under the state that blade 12 is pressed by spring 30 at cardinal extremity, front-end face 12a abuts with the outer circumferential face 10a of cylinder 10, move back and forth in blade groove 11 along with the eccentric rotary of cylinder 10.By this, the suction side of low pressure and the discharge side of high pressure will be divided into two in cylinder chamber 4.
Be provided with the not shown suction port for being sucked from closed shell 1 outside by refrigeration agent in the suction side of cylinder chamber 4, this suction port is communicated with the gas-liquid separator 40 of closed shell 1 outside.
In addition, in main shaft bearing portion 6, be provided with not shown drain passageway, this drain passageway is closed by the expulsion valve 14 only opening closedown in discharge direction.In addition, be provided with exhaust silencer 15 on the top of main shaft bearing portion 6, this exhaust silencer 15 covers drain passageway.
Below in closed shell 1 has lubricant oil 31, and it is supplied to the slip surface of cylinder chamber 4 in compression mechanical part 2 and main shaft bearing portion 6 and supplementary bearing 7.
At this, as shown in Figure 2, corner, border portion 16 is formed by the inner peripheral surface 4a of cylinder chamber 4 and the bottom interior surface 6a of main shaft bearing portion 6.Because when machine shaping cylinder chamber 4, the front end geometry of Grinding tools is copied in corner, border portion 16, therefore it forms the curved surface with curvature on the roughly complete cycle of inner peripheral surface 4a.The radius of curvature of the above-mentioned curved surface be replicated is set to Rc.
The cylinder 10 be arranged in cylinder chamber 4 has: the first corner portion 18, and this first corner portion 18 is formed on the complete cycle in the one end side 10b relative with the main shaft bearing portion 6 corner portion crossing with outer circumferential face 10a; And the second corner portion 19, this second corner portion 19 is formed on the complete cycle by the other end side 10c of the supplementary bearing 7 side corner portion crossing with outer circumferential face 10a.At this, it is Rr1 that the first corner portion 18 is formed as radius of curvature, and it is Rr2 that the second corner portion 19 is formed as radius of curvature.
Clearance C t between clearance C s between the outer circumferential face 10a of the cylinder 10 and inner peripheral surface 4a of cylinder chamber 4, the one end side 10b of the cylinder 10 and bottom interior surface 6a of main shaft bearing portion 6 is filled up by the oil film formed by lubricant oil 31, by this, the slip of cylinder 10 rotates good, and can guarantee the tightness in cylinder chamber 4.
In general, in order to make the clearance C t between cylinder 10 and cylinder chamber 4, Cs minimum, cylinder 10 compressor rotated that slides in cylinder chamber 4 is formed as the radius of curvature R r1 equal with the radius of curvature R c in corner, border portion 16 (Rr1=Rc) in the first corner portion 18, wherein, cylinder chamber 4 has corner, border portion 16, and the front end geometry of the Grinding tools cuttves such as facing cutter is copied in this corner, border portion 16.
But now, the space U surrounded by the front-end face 12a of the outer circumferential face 10a of cylinder 10, the bottom interior surface 6a of main shaft bearing portion 6 and blade 12 becomes large, thus cannot maintain tightness higher between the suction side of cylinder chamber 4 and discharge side.
Particularly, when cylinder chamber 4 is formed less, the size of Grinding tools becomes large relatively, the size of the space U that the front-end face 12a of the outer circumferential face 10a of reason cylinder 10, the bottom interior surface 6a of main shaft bearing portion 6 and blade 12 surrounds becomes remarkable to bubble-tight impact.
Therefore, the radius of curvature R r1 in the first corner portion 18 of the cylinder 10 of present embodiment is formed as less than the radius of curvature R c in corner, border portion 16 (Rr1 < Rc).By this, as compared to the situation of the radius of curvature R c equal with the radius of curvature R r1 in the first corner portion 18 (Rc=Rr1) in corner, the border portion 16 represented with dotted line X in Fig. 2, the space U surrounded by main shaft bearing portion 6, cylinder 10 and blade 12 diminishes, thus can guarantee higher tightness.
At this, it is preferable that, the radius of curvature R r1 in the first corner portion 18 is less than the radius of curvature R c in corner, border portion 16 (Rr1 < Rc), and bubble-tight clearance C t, Cs can be guaranteed by maintenance oil film, reach the degree that corner, border portion 16 contacts with the first corner portion 18, neither interfere and also do not rub.
In addition, the radius of curvature R r2 in the second corner portion 19 of cylinder 10 is formed as less than the radius of curvature R r1 in the first corner portion 18 (Rr2 < Rr1), with the radius of curvature R r1 in the first corner portion 18 represented with dot and dash line Y in Fig. 2 and the second corner portion 19, the situation that Rr2 is equal is compared, can by the inner peripheral surface 4a by cylinder chamber 4, the SPACE V that the cylinder chamber sealing surface 7a of the supplementary bearing 7 and outer circumferential face 10a of cylinder 10 surrounds, by the cylinder chamber sealing surface 7a of supplementary bearing 7, the space W that the front-end face 12a of the blade 12 and outer circumferential face 10a of cylinder 10 surrounds is formed less.
As mentioned above, if formed less by U, V, W, then can form the higher cylinder chamber of tightness 4, and the compression mechanical part 2 by being divided into two into the suction side of low pressure and the discharge side of high pressure in cylinder chamber 4 can be formed.
And, the outer circumferential face 10a of cylinder 10 does not have arrange the groove portion that abuts with blade 12 all the time, if rotating shaft 9 rotates, eccentric shaft portion 8 and cylinder 10 eccentric rotary, then cylinder 10 rotation swimmingly around eccentric shaft portion 8.By this, the outer circumferential face 10a of cylinder 10 can not abut with the front-end face 12a of blade 12 local, and a part of outer circumferential face 10a can not be worn and torn, and abrasion powder also can not disperse in compression mechanical part 2.
In addition, along with cylinder 10 rotation, the lubricant oil of the clearance C s between the inner peripheral surface 4a being supplied to outer circumferential face 10a and cylinder chamber 4 increases, thus can obtain good lubricity and tightness.
Below, the running of the compressor 100 formed as mentioned above is described.
Once from compressor 100 outside supply driving current, motor part 3 is driven, rotating shaft 9 rotates, eccentric shaft portion 8 and cylinder 10 eccentric rotary in the cylinder chamber 4 of the cylinder part 5 of compression mechanical part 2.
Then, the refrigeration agent of the low-temp low-pressure be inhaled into from the suction port of compressor 100 can be inhaled into the suction side of the cylinder chamber 4 of compression mechanical part 2.Be inhaled into the eccentric rotary of the refrigeration agent in cylinder chamber 4 because of cylinder 10 is become High Temperature High Pressure refrigeration agent by compressing, and be expelled in closed shell 1 from the discharge side of cylinder chamber via drain passageway and exhaust silencer 15, then discharge from the discharge tube 32 being located at closed shell 1 top towards closed shell 1 outside.
Even if having the compressor of the one-piece type cylinder 20 cylinder part 5 and main shaft bearing portion 6 formed as one as in the present embodiment, Rr1 < Rc is set to by the radius of curvature R c in corner, border portion 16 of cylinder chamber 4 of the radius of curvature R r1 in the first corner portion 18 by cylinder 10 and the front end geometry that copies Grinding tools cutter, and the radius of curvature R r2 in radius of curvature R r1 and the second corner portion 19 is set to Rr2 < Rr1, just can provide mechanical seal and lubricity is high, volumetric efficiency is high compressor 100.
In addition, the outer circumferential face 10a noting be used in cylinder 10 arranges groove portion just can rotation glossily, thus the compressor 100 that the reliability that cylinder 10 can be provided not wear and tear is high.
In addition, in the one-piece type cylinder of the first mode of execution, main shaft bearing portion 6 is configured in motor part 3 side, but when main shaft bearing portion 6 and supplementary bearing about 7 are exchanged, using when being configured in motor part 3 side as the supplementary bearing 7 of closure member, also same effect can be obtained.
(the second mode of execution)
At this, Fig. 3 is the cross-sectional schematic of the major component represented in the cylinder chamber 4 of the second mode of execution.The compressor 100 of present embodiment is the same with the compressor 100 of the first mode of execution, comprises compression mechanical part 2, motor part 3 and rotating shaft 9 in closed shell 1, for its explanation of same incomplete structure.
As shown in Figure 3, corner, the border portion 16 of one-piece type cylinder 20 is formed as the radius of curvature towards main shaft bearing portion 6 side depression (recessed) is the curved surface of Rc.
When the Grinding tools such as using end milling cutter forms cylinder chamber 4 in the fabrication process, the amount of feed only deepening Grinding tools at place of portion 16, corner, border carries out grinding, thus forms corner, the border portion 16 of above-mentioned depression.
The dotted line Z of Fig. 3 represents the radius of curvature R r1 in the first corner portion 18 in the first mode of execution.Cave in by making corner, border portion 16, compared with dotted line Z, radius of curvature R r1 can be made less, under the state maintaining clearance C t, Cs, the space U surrounded by the front-end face 12a of the bottom interior surface 6a of main shaft bearing portion 6, the outer circumferential face 10a of cylinder 10 and blade 12 can be reduced further.
By this, can provide compared with the compressor of the first mode of execution, the compressor 100 that mechanical seal is higher, volumetric efficiency is higher at blade 12 place.
In addition, by making corner, border portion 16 cave in, lubricant oil 31 is accumulated, thus improves the lubricity of cylinder 10, and can reduce mechanical loss.
(the 3rd mode of execution)
Fig. 4 is the cross-sectional schematic of the major component represented in the cylinder chamber 4 of the 3rd mode of execution.For the compressor 100 of present embodiment, omit the explanation about the identical structure of the compressor 100 with the second mode of execution.As the structure different from the second mode of execution, as shown in Figure 4, corner, the border portion 16 of one-piece type cylinder 20 be configured to towards cylinder chamber 4 inner peripheral surface 4a side depression and radius of curvature is Rc.
In this case, the same with the second mode of execution, can provide a kind of compared with the compressor of the first mode of execution, the compressor 100 that mechanical seal is higher, volumetric efficiency is higher at blade 12 place.In addition, by making corner, border portion 16 cave in, lubricant oil 31 is accumulated, thus improves the lubricity of cylinder 10.
(the 4th mode of execution)
The compressor 100 of the above-mentioned first to the 3rd mode of execution can be arranged in the refrigerating circulatory device of such as air conditioner or heat pump heat supply hydrophone etc.Fig. 5 is the figure of refrigerating circulatory device A of the compressor 100 about using the 4th mode of execution, is described with reference to the roughly situation of Fig. 5 to refrigerating circulatory device A.
Refrigerating circulatory device A comprises four-way valve 101, first heat exchanger 102, expansion gear 103, second heat exchanger 104 that are connected with compressor 100, and these components connect with refrigerant piping successively.Working fluid and refrigeration agent is sealed with in this refrigerating circulatory device A.
To be compressed by compressor 100 and the refrigeration agent of discharging is supplied to the first heat exchanger 102 via four-way valve 101 as shown in solid arrow.Now, the first heat exchanger 102 plays the effect of condenser, captures heat of condensation and make refrigeration agent condensing from refrigeration agent.
The duty cryogen be condensed in the first heat exchanger 102 reduces pressure via refrigerant piping and is supplied to the second heat exchanger 104 in expansion gear 103.Second heat exchanger 104 plays the effect of vaporizer, captures vaporization heat and refrigeration agent is evaporated from refrigeration agent.Vaporized duty cryogen is sucked into compressor 100 via refrigerant piping and four-way valve 101, and refrigeration agent can circulate in above-mentioned path, and the running of refrigerating circulatory device A is continued.
In addition, by utilizing four-way valve 101 to switch stream, refrigeration agent can circulate with in the path shown in dotted arrow in Figure 5.That is, the refrigeration agent of discharging from compressor 100 flows the second heat exchanger 104, expansion gear 103, first heat exchanger 102 successively from four-way valve 101, circulates in the path being inhaled into compressor 100 via four-way valve 101.Now, the first heat exchanger 102 plays the effect of vaporizer, and the second heat exchanger 104 plays the effect of condenser.
As mentioned above, by using the compressor 100 that volumetric efficiency is high, reliability is high in refrigerating circulatory device A, a kind of performance can be provided high and the refrigerating circulatory device that reliability is high.
In addition, the above-mentioned first to the 3rd mode of execution is illustrated the situation that compression mechanical part is stage compressor, but also can use multiple compression mechanical part.Such as, the compression mechanical part of two-stage also can be set, and use the dividing plate separated the compression mechanical part of two-stage as the closure member closed the cylinder chamber of one-piece type cylinder.
In addition, the hermetic type compressor being provided with compression mechanical part and motor part in closed shell is illustrated, but also compression mechanical part can be set in the housing of style of opening, and configure the driving element such as motor part, motor outward to use at housing.
In addition, the present invention is not limited to above-mentioned mode of execution itself, implementation phase in the scope of the inventive concept, distortion can be carried out to constituting component and specializes not departing from.In addition, can by carrying out disclosed multiple constituting component in the above-described embodiment appropriately combinedly forming various invention.Also some constituting components can be removed from whole constituting component.
Claims (4)
1. a compressor, comprising:
Rotating shaft;
One-piece type cylinder, the bearing portion supported described rotating shaft and the described cylinder part with the cylinder chamber impaled by cylinder part inner peripheral surface form as one and form by this one-piece type cylinder;
Closure member, this closure member has the end face closed described cylinder chamber, and is formed with described one-piece type cylinder split;
Cylinder, this cylinder has the outer circumferential face relative with the inner peripheral surface of described cylinder chamber, the one end side relative with bearing portion and the other end side relative with described closure member, and be configured to can in described cylinder chamber eccentric rotary; And
Blade, this blade has the front-end face abutted with the outer circumferential face of described cylinder, and be configured in be located at described cylinder part blade groove in,
It is characterized in that,
The radius of curvature in the first corner portion formed by outer circumferential face and the one end side by described cylinder is formed as less than the radius of curvature in corner, the border portion between the inner peripheral surface of described cylinder chamber and bearing portion internal surface.
2. compressor as claimed in claim 1, it is characterized in that, the radius of curvature in the second corner portion formed with the other end side by the outer circumferential face by described cylinder is formed as less than the radius of curvature in the first corner portion of described cylinder.
3. compressor as claimed in claim 1 or 2, is characterized in that, corner, the border portion of described one-piece type cylinder is to be formed from the mode of described cylinder inner peripheral surface or described bearing portion internal surface depression.
4. a refrigerating circulatory device, is characterized in that, comprises compressor as claimed any one in claims 1 to 3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011014666A JP2012154263A (en) | 2011-01-27 | 2011-01-27 | Compressor and refrigerating cycle system |
| JP2011-014666 | 2011-01-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102619755A CN102619755A (en) | 2012-08-01 |
| CN102619755B true CN102619755B (en) | 2014-12-31 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210031199.5A Active CN102619755B (en) | 2011-01-27 | 2012-01-20 | Compressor and refrigerating cycle apparatus |
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| Country | Link |
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| JP (1) | JP2012154263A (en) |
| CN (1) | CN102619755B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112576502B (en) * | 2020-12-03 | 2022-05-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly, compressor and air conditioner with same |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85104676A (en) * | 1984-11-27 | 1986-05-10 | 三菱重工业株式会社 | The processing method of scroll-type fluid pressure-increasing machine and wherein used scroll-type member |
| US5878488A (en) * | 1996-09-04 | 1999-03-09 | General Motors Corporation | Washerless bolt head seal for compressor housing |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5067884A (en) * | 1989-07-28 | 1991-11-26 | Goldstar Co., Ltd. | Unitized structure of main bearing and cylinder of rotary compressor |
| JPH05187371A (en) * | 1992-01-13 | 1993-07-27 | Hitachi Ltd | Scroll compressor and end mill for machining scroll lap |
| JPH07109980A (en) * | 1993-10-13 | 1995-04-25 | Nippondenso Co Ltd | Pressure resistant structure in scroll compressor |
| JPH10131879A (en) * | 1996-10-29 | 1998-05-19 | Matsushita Refrig Co Ltd | Rotary refrigerant compressor |
| JP2006112276A (en) * | 2004-10-13 | 2006-04-27 | Calsonic Compressor Inc | Electric gas compressor |
| JP4813135B2 (en) * | 2005-09-21 | 2011-11-09 | 三菱電機株式会社 | Rotary compressor |
| JP4305550B2 (en) * | 2007-09-28 | 2009-07-29 | ダイキン工業株式会社 | Rotary fluid machine |
-
2011
- 2011-01-27 JP JP2011014666A patent/JP2012154263A/en active Pending
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2012
- 2012-01-20 CN CN201210031199.5A patent/CN102619755B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85104676A (en) * | 1984-11-27 | 1986-05-10 | 三菱重工业株式会社 | The processing method of scroll-type fluid pressure-increasing machine and wherein used scroll-type member |
| US5878488A (en) * | 1996-09-04 | 1999-03-09 | General Motors Corporation | Washerless bolt head seal for compressor housing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012154263A (en) | 2012-08-16 |
| CN102619755A (en) | 2012-08-01 |
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