CN102619755A - Compressor and refrigerating cycle apparatus - Google Patents
Compressor and refrigerating cycle apparatus Download PDFInfo
- Publication number
- CN102619755A CN102619755A CN2012100311995A CN201210031199A CN102619755A CN 102619755 A CN102619755 A CN 102619755A CN 2012100311995 A CN2012100311995 A CN 2012100311995A CN 201210031199 A CN201210031199 A CN 201210031199A CN 102619755 A CN102619755 A CN 102619755A
- Authority
- CN
- China
- Prior art keywords
- cylinder
- compressor
- cylinder chamber
- corner
- curvature
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
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
Mode of execution of the present invention relates to a kind of compressor and comprises the refrigerating circulatory device of this compressor.
Background technique
As general compressor, known have a following described revolution type compressor, in this revolution type compressor, through making cylinder eccentric rotation in the cylinder chamber of compression mechanical part, comes compressed fluid.The compression mechanical part of this compressor comprises: cylinder part, and this cylinder part has the cylinder chamber that is impaled by the cylinder inner peripheral surface; Closure member, this closure member countershaft supports, and the countercylinder chamber is sealed; And blade, the outer circumferential face butt of this blade and cylinder is with being divided into two into the suction side in the cylinder chamber and discharging side.
In addition, above-mentioned compressor also comprises the compression mechanical part that cylinder part and bearing portion form as one.
Under the situation that cylinder part and bearing portion form as one, in process of production, corner, the border portion place in the cylinder chamber on being located at the internal surface of cylinder part forms the curved surface with certain curvature radius.In addition, the relative corner portion place of corner, the border portion with in the cylinder chamber of the cylinder of eccentric rotation also is provided with the curved surface with same curvature radius in cylinder chamber.
But, if make the radius of curvature of the corner portion relative of radius of curvature and cylinder of corner, the border portion in the cylinder chamber identical with corner, border portion, then can the outer circumferential face of cylinder and and the front-end face of the blade that connects of outer circumferential face between form clearance space.If the clearance space that between the front-end face of the outer circumferential face of cylinder and blade, forms is bigger, then can reduce the volumetric efficiency reduction of compressor with being divided into two into the mechanical seal property of suction side in the cylinder chamber with the blade of discharging side.
Patent documentation 1: japanese patent laid-open 10-131879 communique
Summary of the invention
According to the embodiment of the present invention, providing a kind of can suppress because of the high compressor of the reduction of mechanical seal property, volumetric efficiency with the blade that is divided into two into suction side and discharge side in the cylinder chamber.
The compressor of embodiment of the present invention comprises: rotating shaft; And one-piece type cylinder, the bearing portion that this one-piece type cylinder supports countershaft forms as one with the cylinder part with the cylinder chamber that is impaled by the cylinder inner peripheral surface and constitutes.
Cylinder chamber's quilt of one-piece type cylinder seals with the closure member that one-piece type cylinder split forms, and is provided be configured in cylinder chamber, to slide cylinder that rotates and the blade that is configured in being located at the blade groove of cylinder part, to reciprocatingly slide.
In addition, the radius of curvature of the outer circumferential face of cylinder and the first corner portion between the bearing portion side is formed littler than the radius of curvature of the cylinder inner peripheral surface of one-piece type cylinder and corner, the border portion between the bearing portion internal surface.
By this, the compressor that a kind of mechanical seal property and lubricity are high, volumetric efficiency is high can be provided.
Description of drawings
Fig. 1 is the longitudinal section of the compressor of first mode of execution.
Fig. 2 is the cross-sectional schematic of the major component in the cylinder chamber of first mode of execution.
Fig. 3 is the cross-sectional schematic of the major component in the cylinder chamber of 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 representation 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 bearing portions
7 supplementary bearings
8 eccentric shaft portions
9 rotating shafts
10 cylinders
The 10a outer circumferential face
11 blade grooves
12 blades
The 12a front-end face
14 discharging valve devices
16 border corner portion
18 first corner portions
19 second corner portions
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
The A refrigerating circulatory device
Embodiment
Below, based on accompanying drawing mode of execution of the present invention is described.
(first mode of execution)
Fig. 1 is the longitudinal section of the compressor 100 of this mode of execution of expression, and Fig. 2 is the schematic representation of its major component of expression.
The compressor 100 of first mode of execution is the closed rotary compressor that refrigeration agent is compressed, the motor part 3 above vertical inside of long 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 that in motor part 3, produces is passed to compression mechanical part 2 via rotating shaft 9.
Compression mechanical part 2 has one-piece type cylinder 20.One-piece type cylinder 20 forms as one the cylinder part 5 that is positioned at the below to constitute with being configured in the top of cylinder part 5 and being used for that rotating shaft 9 is supported to revolvable main bearing portion 6.
One-piece type cylinder 20 is provided with cylinder chamber 4, and this cylinder chamber 4 wears the blank part that forms through cutting such as facing cutter processing from the below end face of cylinder part 5.Can eccentric rotation in this cylinder chamber 4 and rotation dispose 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.The lower opening portion of cylinder chamber 4 is by supplementary bearing 7 sealings, and this supplementary bearing 7 is not only closure member, and it still is the support member of rotating shaft 9.
That is, as shown in Figure 2, cylinder chamber 4 is by the bottom interior surface 6a of the inner peripheral surface 4a of cylinder part 5, main bearing portion 6 with as 7 sealings of the supplementary bearing of closure member.
In addition; Cylinder 10 form have outer circumferential face 10a, the general cylindrical shape shape of an end side surface 10b and the other end side 10c; Wherein, The inner peripheral surface 4a of above-mentioned outer circumferential face 10a and cylinder chamber 4 is relative and do not have concavo-convex, formation glossily, and an above-mentioned end side surface 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.
On cylinder part 5, be equipped with the blade groove 11 to cylinder chamber's 4 openings, the blade 12 of essentially rectangular is configured to and can freely moves back and forth.Blade 12 is pushed by spring 30 at cardinal extremity, under the state of the outer circumferential face 10a butt of front-end face 12a and cylinder 10, along with the off-centre rotation of cylinder 10 and in blade groove 11, move back and forth.By this, with the discharge side of suction side that is divided into two into low pressure in the cylinder chamber 4 and high pressure.
Be provided with in the suction side of cylinder chamber 4 and be used for refrigeration agent from the closed shell 1 outside not shown suction port that sucks, this suction port is communicated with the gas-liquid separator 40 of closed shell 1 outside.
In addition, in main bearing portion 6, be provided with not shown drain passageway, this drain passageway only can be opened expulsion valve 14 sealings of closing on the discharge direction.In addition, be provided with exhaust silencer 15 on the top of main bearing portion 6, this exhaust silencer 15 covers drain passageway.
Storing below in closed shell 1 has lubricant oil 31, and it is supplied to cylinder chamber 4 and the slip surface of main bearing portion 6 and supplementary bearing 7 in the compression mechanical part 2.
At this, as shown in Figure 2, form corner, border portion 16 by the inner peripheral surface 4a of cylinder chamber 4 and the bottom interior surface 6a of main bearing portion 6.Because the front end shape that Grinding tools duplicates in corner, border portion 16 when machine shaping cylinder chamber 4, so 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 that is replicated is made as Rc.
The cylinders 10 that are arranged in the cylinder chamber 4 have: the first corner portion 18, this first corner portion 18 are formed on the complete cycle of the crossing corner portion of an end side surface 10b relative with main bearing portion 6 and outer circumferential face 10a; And the second corner portion 19, this second corner portion 19 is formed on the complete cycle of the corner portion of intersecting by the other end side 10c of supplementary bearing 7 one sides and outer circumferential face 10a.At this, it is Rr1 that the first corner portion 18 forms radius of curvature, and it is Rr2 that the second corner portion 19 forms radius of curvature.
The oil film that clearance C t between the bottom interior surface 6a of the clearance C s between the outer circumferential face 10a of cylinder 10 and the inner peripheral surface 4a of cylinder chamber 4, an end side surface 10b of cylinder 10 and main bearing portion 6 is formed by lubricant oil 31 fills up; By this; The slip rotation of cylinder 10 is good, and can guarantee the tightness in the cylinder chamber 4.
In general; In order to make clearance C t, Cs between cylinder 10 and the cylinder chamber 4 minimum; The radius of curvature R r1 that cylinder 10 slip rotation compressor in cylinder chamber 4 forms the first corner portion 18 equates (Rr1=Rc) with the radius of curvature R c of corner, border portion 16; Wherein, cylinder chamber 4 has corner, border portion 16, the front end shape that Grinding tools cuttves such as facing cutter duplicate in this corner, border portion 16.
But at this moment, the space U that is surrounded by the front-end face 12a of the bottom interior surface 6a of the outer circumferential face 10a of cylinder 10, main bearing portion 6 and blade 12 becomes big, thus higher tightness between the suction side that can't keep cylinder chamber 4 and the discharge side.
Particularly; Form lessly and the size of Grinding tools relatively becomes under the big situation in cylinder chamber 4, 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 bearing portion 6 and blade 12 surrounds becomes remarkable to bubble-tight influence.
Therefore, the radius of curvature R r1 of the first corner portion 18 of the cylinder 10 of this mode of execution forms the little (Rr1＜Rc) of radius of curvature R c than corner, border portion 16.By this; The radius of curvature R c of corner, the border portion 16 that representes with dashed lines X among Fig. 2 and the radius of curvature R r1 of the first corner portion 18 equate that the situation of (Rc=Rr1) compares; The space U that is surrounded by main bearing portion 6, cylinder 10 and blade 12 diminishes, thereby can guarantee higher tightness.
At this; Comparatively it is desirable to; The radius of curvature R r1 of the first corner portion 18 is than the little (Rr1＜Rc) of the radius of curvature R c of corner, border portion 16; And can keep guaranteeing bubble-tight clearance C t, Cs, reach corner, border portion 16 and the first corner portion, 18 contacted degree, neither interfere and also do not rub with oil film.
In addition; The radius of curvature R r2 of the second corner portion 19 of cylinder 10 forms the little (Rr2＜Rr1) of radius of curvature R r1 than the first corner portion 18; Compare with the radius of curvature R r1 of the first corner portion 18 that representes with dot and dash line Y among Fig. 2 and the second corner portion 19, the situation that Rr2 equates, the SPACE V that can be surrounded by the outer circumferential face 10a of the sealing surface 7a of cylinder chamber of the inner peripheral surface 4a of cylinder chamber 4, supplementary bearing 7 and cylinder 10, the space W that is surrounded by the outer circumferential face 10a of the front-end face 12a of the sealing surface 7a of cylinder chamber of supplementary bearing 7, blade 12 and cylinder 10 form lessly.
As stated, if form U, V, W less, then can form the higher cylinder chamber of tightness 4, and can form compression mechanical part 2 the discharge side of suction side that is divided into two into low pressure in the cylinder chamber 4 and high pressure.
And, on the outer circumferential face 10a of cylinder 10, there is not to be provided with all the time the slot part with blade 12 butts, if rotating shaft 9 rotations, eccentric shaft portion 8 and cylinder 10 eccentric rotations, then cylinder 10 rotation swimmingly around eccentric shaft portion 8.By this, the outer circumferential face 10a of cylinder 10 can be not local and the front-end face 12a butt of blade 12, and the part of outer circumferential face 10a can not worn and not torn, and abrasion powder can not disperse to compression mechanical part 2 yet.
In addition, along with cylinder 10 rotations, the lubricant oil that is supplied to the clearance C s between the inner peripheral surface 4a of outer circumferential face 10a and cylinder chamber 4 increases, thereby can obtain good lubricity and tightness.
Below, the running of the compressor 100 that constitutes is as stated described.
In case when motor part 3 being driven from compressor 100 outside supply driving currents, rotating shaft 9 rotations, eccentric shaft portion 8 and cylinder 10 be eccentric rotation in the cylinder chamber 4 of the cylinder part 5 of compression mechanical part 2.
The refrigeration agent of the low-temp low-pressure that then, is 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.The refrigeration agents that are inhaled in the cylinder chamber 4 are compressed the refrigeration agent that becomes HTHP because of the off-centre rotation of cylinder 10; And be expelled in the closed shell 1 via drain passageway and exhaust silencer 15 from the discharge side of cylinder chamber, then from the discharge tube 32 of being located at closed shell 1 top towards closed shell 1 outside the discharge.
Even if as this mode of execution, have the compressor of the one-piece type cylinder 20 that cylinder part 5 and main bearing portion 6 are formed as one; Through the radius of curvature R r1 of the first corner portion 18 of cylinder 10 and the radius of curvature R c of corner, the border portion 16 of the cylinder chamber 4 of the front end shape of duplicating the Grinding tools cutter are made as Rr1＜Rc; And the radius of curvature R r2 of the radius of curvature R r1 and the second corner portion 19 is made as Rr1＜Rr2, the compressor 100 that mechanical seal property and lubricity are high, volumetric efficiency is high just can be provided.
In addition, the outer circumferential face 10a that not be used in cylinder 10 is provided with just rotation glossily of slot part, thus the high compressor 100 of the reliability that can provide cylinder 10 not wear and tear.
In addition; In the one-piece type cylinder of first mode of execution; Main bearing portion 6 is configured in motor part 3 sides, but, also can obtains same effect in that main bearing portion 6 is exchanged up and down, will be configured under the situation of motor part 3 sides as the supplementary bearing 7 of closure member with supplementary bearing 7.
(second mode of execution)
At this, Fig. 3 is the cross-sectional schematic of the major component in the cylinder chamber 4 of expression second mode of execution.The compressor 100 of this mode of execution is the same with the compressor 100 of first mode of execution, in closed shell 1, comprises compression mechanical part 2, motor part 3 and rotating shaft 9, for its explanation of same incomplete structure.
As shown in Figure 3, it is the curved surface of Rc that corner, the border portion 16 of one-piece type cylinder 20 forms towards the radius of curvature of main bearing portion 6 sides depressions (recessed).
When Grinding tools such as using end milling cutter formed cylinder chamber 4 in manufacture process, the amount of feed that only portion 16 places deepen Grinding tools in the corner, border carried out grinding, thereby forms corner, the border portion 16 of above-mentioned depression.
The dotted line Z of Fig. 3 representes the radius of curvature R r1 of the first corner portion 18 in first mode of execution.Through making corner, border portion 16 depressions; Z compares with dotted line; Can make radius of curvature R r1 littler, under the state of keeping clearance C t, Cs, can further reduce the space U that the front-end face 12a by the outer circumferential face 10a of the bottom interior surface 6a of main bearing portion 6, cylinder 10 and blade 12 surrounds.
By this, can provide with the compressor of first mode of execution and compare, the compressor that mechanical seal property is higher, volumetric efficiency is higher 100 at blade 12 places.
In addition, through making corner, border portion 16 depressions, lubricant oil 31 is able to accumulate, thereby has improved 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 in the cylinder chamber 4 of expression the 3rd mode of execution.For the compressor 100 of this mode of execution, omit explanation about the structure identical with the compressor of second mode of execution 100.As with the second mode of execution various structure, as shown in Figure 4, it is Rc that corner, the border portion 16 of one-piece type cylinder 20 constitutes towards the inner peripheral surface 4a side of cylinder chamber 4 depression and radius of curvature.
In this case, the same with second mode of execution, can provide a kind of compressor to compare, the compressor that mechanical seal property is higher, volumetric efficiency is higher 100 at blade 12 places with first mode of execution.In addition, through making corner, border portion 16 depressions, lubricant oil 31 is able to accumulate, thereby has improved the lubricity of cylinder 10.
(the 4th mode of execution)
The compressor 100 of above-mentioned first to the 3rd mode of execution can be arranged in the refrigerating circulatory device of for example air conditioner or heat pump heat supply hydrophone etc.Fig. 5 is about the figure of the refrigerating circulatory device A of the compressor 100 that uses the 4th mode of execution, with reference to Fig. 5 the roughly situation of refrigerating circulatory device A is described.
Refrigerating circulatory device A comprises the four-way valve that is connected with compressor 100 101, first heat exchanger 102, expansion gear 103, second heat exchanger 104, and these members connect with refrigerant piping successively.Enclose in this refrigerating circulatory device A that working fluid is arranged is refrigeration agent.
The refrigeration agent that is compressed machine 100 compressions and discharges is supplied to first heat exchanger 102 via four-way valve 101 shown in the solid line arrow.At this moment, first heat exchanger 102 plays the effect of condenser, from refrigeration agent, captures heat of condensation and makes refrigeration agent condensing.
The duty cryogen that in first heat exchanger 102, is condensed reduces pressure in expansion gear 103 via refrigerant piping and is supplied to second heat exchanger 104.Second heat exchanger 104 plays the effect of vaporizer, from refrigeration agent, captures vaporization heat and makes refrigeration agent evaporation.Vaporized duty cryogen is via refrigerant piping and four-way valve 101 and be sucked into compressor 100, and refrigeration agent can circulate in above-mentioned path, makes the running of refrigerating circulatory device A be able to continue.
In addition, switch stream through utilizing four-way valve 101, refrigeration agent can circulate in the path shown in the with dashed lines arrow in Fig. 5.That is, the refrigeration agent of discharging from compressor 100 flows second heat exchanger 104, expansion gear 103, first heat exchanger 102 from four-way valve 101 successively, in the path that is inhaled into compressor 100 via four-way valve 101, circulates.At this moment, first heat exchanger 102 plays the effect of vaporizer, and second heat exchanger 104 plays the effect of condenser.
As stated, through in refrigerating circulatory device A, using the compressor 100 that volumetric efficiency is high, reliability is high, a kind of performance height and the high refrigerating circulatory device of reliability can be provided.
In addition, above-mentioned first to the 3rd mode of execution is that the situation of a stage compressor is illustrated to compression mechanical part, but also can use a plurality of compression mechanical parts.For example, the compression mechanical part of two-stage can be set also, and the closure member that uses dividing plate that the compression mechanical part of two-stage is separated to seal as the cylinder chamber to one-piece type cylinder.
In addition, the hermetic type compressor that in closed shell, is provided with compression mechanical part and motor part is illustrated, but also can in the housing of style of opening, compression mechanical part be set, and outside housing, dispose motor part, driving element such as motor uses.
In addition, the present invention is not limited to above-mentioned mode of execution itself, the implementation phase can constituting component be out of shape to specialize not breaking away from the scope of the inventive concept.In addition, can form various inventions through disclosed a plurality of constituting component is in the above-described embodiment carried out appropriate combination.Also can from whole constituting components, remove some constituting components.
Claims (4)
1. compressor comprises:
Rotating shaft;
One-piece type cylinder, this one-piece type cylinder form as one the bearing portion that said rotating shaft is supported and constitute with the said cylinder part with the cylinder chamber that is impaled by the cylinder part inner peripheral surface;
Closure member, this closure member have said cylinder chamber are carried out closed end face, and form with said one-piece type cylinder split;
Cylinder, this cylinder have the outer circumferential face relative with the inner peripheral surface of said cylinder chamber, relative with bearing portion one distolateral and relative with said closure member the other end side, and be configured to can eccentric rotation in said cylinder chamber; And
Blade, this blade have the front-end face with the outer circumferential face butt of said cylinder, and are configured in the blade groove of being located at said cylinder part,
The radius of curvature of the first corner portion that will be formed by the outer circumferential face and an end side surface of said cylinder forms littler than the radius of curvature of the inner peripheral surface of said cylinder chamber and corner, the border portion between the bearing portion internal surface.
2. compressor as claimed in claim 1 is characterized in that, the radius of curvature of the second corner portion that will be formed by the outer circumferential face of said cylinder and the other end side forms littler than the radius of curvature of the first corner portion of said cylinder.
3. according to claim 1 or claim 2 compressor is characterized in that, corner, the border portion of said one-piece type cylinder forms with the mode from said cylinder inner peripheral surface or said bearing portion internal surface depression.
4. a refrigerating circulatory device is characterized in that, comprises like each described compressor in the claim 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 true CN102619755A (en) | 2012-08-01 |
| CN102619755B CN102619755B (en) | 2014-12-31 |
Family
ID=46559891
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210031199.5A Active CN102619755B (en) | 2011-01-27 | 2012-01-20 | Compressor and refrigerating cycle apparatus |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2012154263A (en) |
| CN (1) | CN102619755B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112576502A (en) * | 2020-12-03 | 2021-03-30 | 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 (6)
| 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 |
| JPH10131879A (en) * | 1996-10-29 | 1998-05-19 | Matsushita Refrig Co Ltd | Rotary refrigerant compressor |
| US5878488A (en) * | 1996-09-04 | 1999-03-09 | General Motors Corporation | Washerless bolt head seal for compressor housing |
| JP2006112276A (en) * | 2004-10-13 | 2006-04-27 | Calsonic Compressor Inc | Electric gas compressor |
| JP2007085208A (en) * | 2005-09-21 | 2007-04-05 | Mitsubishi Electric Corp | Rotary compressor |
| WO2009041056A1 (en) * | 2007-09-28 | 2009-04-02 | Daikin Industries, Ltd. | Rotary fluid machine |
Family Cites Families (3)
| 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 |
-
2011
- 2011-01-27 JP JP2011014666A patent/JP2012154263A/en active Pending
-
2012
- 2012-01-20 CN CN201210031199.5A patent/CN102619755B/en active Active
Patent Citations (6)
| 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 |
| 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 |
| JP2007085208A (en) * | 2005-09-21 | 2007-04-05 | Mitsubishi Electric Corp | Rotary compressor |
| WO2009041056A1 (en) * | 2007-09-28 | 2009-04-02 | Daikin Industries, Ltd. | Rotary fluid machine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112576502A (en) * | 2020-12-03 | 2021-03-30 | 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 |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012154263A (en) | 2012-08-16 |
| CN102619755B (en) | 2014-12-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| AU2005240929B2 (en) | Rotary compressor | |
| JP6389957B2 (en) | Compressor having oil recovery means | |
| WO2005103496A1 (en) | Rotating fluid machine | |
| CN103939343A (en) | Rolling piston refrigeration compressor with low backpressure | |
| JP3724495B1 (en) | Rotary fluid machine | |
| CN1966983B (en) | Rotating and swing type compressor structure | |
| CN102619755B (en) | Compressor and refrigerating cycle apparatus | |
| CN107893758B (en) | Scroll compressor and air conditioner with same | |
| JP2008008165A (en) | Compressor | |
| JP3801185B2 (en) | Rotary fluid machine | |
| KR102243832B1 (en) | Closed type rotary compressor | |
| JP5781355B2 (en) | Hermetic rotary compressor | |
| CN102112747B (en) | Rotary compressor | |
| JP5797450B2 (en) | Compressor manufacturing method. | |
| WO2019146031A1 (en) | Sealed rotary compressor, and refrigeration and air conditioning device provided with said sealed rotary compressor | |
| JP2016089710A (en) | Rotary compressor | |
| JP5738036B2 (en) | Rotary compressor and refrigeration cycle apparatus | |
| KR100323063B1 (en) | Aaaaa | |
| JP5861456B2 (en) | Rotary compressor | |
| JP3744526B2 (en) | Rotary compressor | |
| JP2008121577A (en) | Rotary fluid machine | |
| CN103782037A (en) | Rotary compressor | |
| KR20000061252A (en) | Closed type compressor for use in air conditioner | |
| JP2014227956A (en) | Gas compressor | |
| KR101587168B1 (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |