CN101861463A - Enclosed compressor - Google Patents
Enclosed compressor Download PDFInfo
- Publication number
- CN101861463A CN101861463A CN200880116077.8A CN200880116077A CN101861463A CN 101861463 A CN101861463 A CN 101861463A CN 200880116077 A CN200880116077 A CN 200880116077A CN 101861463 A CN101861463 A CN 101861463A
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- China
- Prior art keywords
- bearing
- bent axle
- oil
- oil supply
- type compressor
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
Abstract
A enclosed compressor in which an oil supply groove (14b) is not a communication groove open at the upper and lower ends of the groove but a groove extending in the lower end side of a crankshaft (26) only up to a mid-region of a bearing section (14a). As a result, not even a portion of lubricating oil supplied to a lower bearing (14A) is discharged to an oil holding section and the entire amount of the lubricating oil supplied to the lower bearing (14A) is supplied to the lower bearing (14A). The construction reduces suction of waste lubricating oil by an oil pump, so that the oil supply ability of the oil pump is increased and loss in the oil pump is minimized.
Description
Technical field
The present invention relates to hermetic type compressor, specifically further relate to the structure improvement of hermetic type compressor.
Background technique
(overall structure of rotary compressor)
With reference to Fig. 6, the overall structure of rotary compressor is described.In addition, Fig. 6 is the integrally-built sectional arrangement drawing of expression rotary compressor.In the lower end side of housing 1, the compression member 7 that sucks the compressed action fluid disposes accordingly with suction pipe 5a, 5b, and disposes the driver part 8 that makes compression member 7 actions in the mode in the roughly whole zone that occupies the inner space above it.In the inner space that the lower cover 4 by the end portion of housing 1 limits, be formed with the oil storage portion 9 that stores lubricant oil O, in other spaces, be formed with the storage area 10 that stores the compressed action fluid.
(compression member 7)
Compression member 7 has the structure that disposes cylinder chamber up and down two-layerly, is provided with across intermediate plate 18: have the upper cylinder 12a of shape of cross section for the circular 11a of cylinder chamber; And have the lower cylinder 12b of shape of cross section for the circular 11b of cylinder chamber, side below two sides and the lower cylinder 12b on this upper cylinder 12a, having the upper bearing 13 of the 13a of bearing portion of projection (boss) shape and the lower bearing 14 that has a 14a of bearing portion of overshooting shape in central authorities equally in central authorities and be bonded by many bolts 15, is air-tight state thereby make the 11a of cylinder chamber, 11b.
Separately the 11a of cylinder chamber, 11b at upper cylinder 12a and lower cylinder 12b dispose upper piston 19a and lower piston 19b.This upper piston 19a and lower piston 19b are configured in the eccentric part 20a of bent axle 26, the periphery of 20b.
(driver part 8)
Be formed with the oily path 26a that on axis direction, extends at bent axle 26a, centrifugal oil pump 27 be installed in the lower end of bent axle 26.Oil pump 27 is immersed among the lubricant oil O of oil storage portion 9 all the time, rotation along with bent axle 26, lubricant oil O is drawn among the oily path 26a, provides lubricant oil to each sliding position of compression member 7 and driver part 8 from a plurality of lubricant oil supply hole 26b that are arranged at bent axle 26.
At this,, the supply of lubricant oil to the 14a of bearing portion of lower bearing 14 is described with reference to Fig. 7 and Fig. 8.In addition, Fig. 7 is a stereogram of representing only to observe from the 14a of bearing portion side the state of lower bearing 14, and Fig. 8 is the longitudinal section of lower bearing 14.As shown in Figure 7, at the inner peripheral surface of the 14a of bearing portion of lower bearing 14, from the upper end portion to the underpart, be provided with connectivity slot 14c abreast with the axis direction of bent axle 26.The lubricant oil (F1) of discharging from the lubricant oil supplying mouth 26b that is arranged at bent axle 26 is propagated and is supplied to via connectivity slot 14c at the outer surface of bent axle 26 between the slip surface of 14a of bearing portion and bent axle 26 (F2).
As shown in Figure 8, connectivity slot 14c is the open groove of upper and lower end parts, and therefore, the lubricant oil (F1) of discharging from lubricant oil supply hole 26b is not all to supply between the slip surface of 14a of bearing portion and bent axle 26, a part (F3) is not used as lubricant oil, and discharges to oil storage portion 9.
But, at oil pump 27 places, except the needed lubricants capacity of each sliding position, also need to suck the lubricants capacity that does not use and discharge to oil storage portion 9 as lubricant oil, therefore can produce meaningless pumping loss.In addition, as the document that discloses rotary compressor shown in Figure 4, can enumerate following patent documentation 1 disclosed content.In addition, as the document of the technology that discloses the rotary compressor oil supply system, can enumerate down note non-patent literature 1 disclosed content.
Patent documentation 1: TOHKEMY 2004-324652 communique
Non-patent literature 1: the grand English of her rattan, other four, " research of rotary compressor oil supply system ", and Mitsubishi Heavy Industries Ltd's skill newspaper, Mitsubishi Heavy Industry Ltd., in September, 1992, Vol.29, No.5, p.458-462
Summary of the invention
The technical problem to be solved in the present invention is, in the lower bearing that hermetic type compressor adopted, because be arranged at the oil supply of lower bearing is the open connectivity slot of upper and lower end parts, so there is the lubricant oil of not supplying with lower bearing and discharging to oil storage portion, in oil pump, also need to suck the lubricant oil of discharging, therefore produce meaningless pumping loss to oil storage portion.Thus, the present invention proposes in order to address the above problem, and purpose is to provide a kind of hermetic type compressor, and it can improve the oil pump feed ability by cutting down the suction of lubricant oil meaningless in the oil pump, suppresses the generation of pumping loss.
In hermetic type compressor of the present invention, taken in compression member and driver part in the inside of seal container, and had: bent axle; Be configured in the piston of periphery of the eccentric part of above-mentioned bent axle; The cylinder of the cylinder chamber of the above-mentioned piston of specified configuration; With a bearing portion that is used for the above-mentioned bent axle of axle supporting, this hermetic type compressor also comprises: clip the upper bearing and the lower bearing of above-mentioned cylinder and above-mentioned piston from the axle direction side of above-mentioned bent axle, this hermetic type compressor has following structure.
This hermetic type compressor comprises:
Oil pump, it is arranged on the underpart of above-mentioned bent axle, rotation along with above-mentioned bent axle, the lubricant oil that is stored in the oil storage portion of end portion of above-mentioned seal container is drawn in the oily path that is provided with in the mode of extending on the axis direction of above-mentioned bent axle, provides lubricated each sliding position of compression member and driver part; With
Oil supply, it is arranged on the slip surface of the above-mentioned bearing portion of above-mentioned lower bearing, extends along the axle direction of above-mentioned bent axle, with the outer surface supplying lubricating oil to above-mentioned bent axle.
In addition, a distolateral end face in above-mentioned cylinder side of above-mentioned oil supply is open, another of above-mentioned oil supply distolateral in the underpart of above-mentioned bent axle side by obturation.
The invention effect
According to based on hermetic type compressor of the present invention, the oil supply that is arranged at lower bearing is not at the open connectivity slot of upper and lower end parts, but at the underpart of bent axle side oil supply by obturation.Consequently, the part in the lubricant oil of supply lower bearing can not discharged to oil storage portion, but whole oil masses of the lubricant oil of supply lower bearing all are supplied to lower bearing.
Consequently,, the supply capability of oil pump is improved, suppress the generation of pumping loss by in oil pump, cutting down the suction of meaningless lubricant oil.
Description of drawings
To be expression only observe stereogram based on the state of the lower bearing that rotary compressor adopted of embodiments of the present invention from bearing portion side to Fig. 1.
Fig. 2 is based on the longitudinal section of the lower bearing that rotary compressor adopted of embodiments of the present invention.
Fig. 3 be when being illustrated in the lower bearing that adopts background technique to the fuel delivery of each sliding position and when adopting the lower bearing of present embodiment to the figure of the fuel delivery of the lubricant oil of each sliding position.
Fig. 4 is the sectional view of expression based on the size relationship of the lower bearing that rotary compressor adopted of embodiments of the present invention.
Fig. 5 be expression based on the temperature rising lower bearing that rotary compressor adopted of embodiments of the present invention, X/L and bearing (℃) the figure of relation.
Fig. 6 is the integrally-built longitudinal section of the rotary compressor of expression background technique.
Fig. 7 is the lower bearing that rotary compressor adopted of background technique is only observed in expression from bearing portion side the stereogram of state.
Fig. 8 is the longitudinal section of the lower bearing that rotary compressor adopted of background technique.
Symbol description
1 housing
4 lower covers
5a, 5b suction pipe
7 compression member
8 driver parts
9 oil storage portions
10 oil storage space
11a, 11b cylinder chamber
The 12a upper cylinder
The 12b lower cylinder
13 upper bearings
13a bearing portion
13c, 14c exhaust port
The 14A lower bearing
14a bearing portion
The 14b oil supply
The 14c connectivity slot
15 bolts
16 premufflers (muffler)
17 rear mufflers
18 intermediate plates
The 19a upper piston
The 19b lower piston
24 stators
25 rotors
26a oil path
26b lubricant oil supply hole
27 oil pumps
O lubricant oil
Embodiment
Below, with reference to description of drawings each mode of execution based on hermetic type compressor of the present invention.In addition, as an example of the hermetic type compressor of present embodiment, describe in the represented rotary compressor of above-mentioned background technology, using situation of the present invention.
In addition, the basic structure of the rotary compressor of present embodiment, the structure of the illustrated rotary compressor that disposes cylinder chamber up and down same two-layerly with using Fig. 6, takes in compression member 7 and driver part 8 in the inside as the housing 1 of seal container, and have: bent axle 26; Be configured in the upper piston 19a and the lower piston 19b of periphery of eccentric part 20a, the 20b of above-mentioned bent axle 26; The upper cylinder 12a of the 11a of cylinder chamber, the 11b of specified configuration this upper piston 19a and lower piston 19b and lower cylinder 12b; With the 13a of bearing portion, the 14a that are used for a supporting crankshaft 26.
In addition, this hermetic type compressor also comprises: the upper bearing 13 and the lower bearing 14 that clip upper cylinder 12a, upper piston 19a, lower cylinder 12b and lower piston 19b from the axle direction side of bent axle 26.
And, be provided with oil pump 27 in the underpart of bent axle 26, this oil pump 27 is along with the rotation of bent axle 26, the lubricant oil O that is stored in the oil storage portion 9 of end portion of housing 1 is drawn among the oily path 26a that is provided with in the mode of extending on the axis direction of bent axle 26, provides lubricated each sliding position of compression member 7 and driver part 8.
Thus, in the explanation afterwards, for the identical or suitable part of structure of the rotary compressor that uses Fig. 6 explanation, mark identical reference character, no longer repeat specification only describes feature structure part of the present invention in detail.
See figures.1.and.2, the characteristic of the rotary compressor of present embodiment is described.In addition, to be expression only observe the stereogram of state of the lower bearing 14A that rotary compressor adopted of present embodiment from the 14a of bearing portion side to Fig. 1, and Fig. 2 is the longitudinal section of lower bearing 14A.
As shown in Figure 1, the inner peripheral surface at the 14a of bearing portion of lower bearing 14A is provided with oil supply 14b.The distolateral end face in cylinder 12b side (with reference to Fig. 6) of this oil supply 14b is open, and another of oil supply 14b is distolateral to be arranged on the position in zone midway until the 14a of bearing portion in the underpart of bent axle 26 side.
The lubricant oil (F1) of discharging from the lubricant oil supplying mouth 26b (with reference to Fig. 6) that is arranged at bent axle 26 is between the slip surface of propagating and be supplied to via oil supply 14b 14a of bearing portion and bent axle 26 on the outer surface of bent axle 26 (F2).
At this, as shown in Figure 2, oil supply 14b is not the connectivity slot open in the underpart, but only is arranged on the position in zone midway until the 14a of bearing portion in the underpart of bent axle 26 side.Consequently, oil supply 14b becomes by the state of obturation in the underpart of bent axle 26 side, therefore supply with the part of the lubricant oil of lower bearing 14A and can not discharge, but whole oil masses of the lubricant oil of supply lower bearing 14A are supplied to lower bearing 14A to oil storage portion 9 (with reference to Fig. 6).In addition, in Fig. 1, represented that oil supply 14b only is arranged on the structure of the position in zone midway until bearing portion 14a in the underpart of bent axle 26 side, but same with connectivity slot 14c shown in Figure 7, be provided with under the situation of groove to the underpart from the upper end portion of bent axle 26, also can adopt by at miscellaneous parts such as the underpart of groove configuration plate member, make the structure of the underpart side obturation of oil supply.
When Fig. 3 is illustrated in the lower bearing 14 that adopts background technique shown in Figure 8 to the fuel delivery (cc/min) of each sliding position and when adopting the lower bearing 14A of present embodiment to the fuel delivery (cc/min) of the lubricant oil of each sliding position.Fuel delivery (cc/min) to the lubricant oil of upper bearing (A1), upper piston 19a (A2) and lower piston 19b (A3) does not change in background technique and present embodiment.
About fuel delivery (cc/min) to the lubricant oil of lower bearing (A4), compare with background technique, cut down fuel delivery (cc/min) in the present embodiment significantly.This be because, as mentioned above in the lower bearing 14A of present embodiment, the part of the lubricant oil of supplying with can not discharged to oil storage portion 9 (with reference to Fig. 6), but whole oil masses of supplying with the lubricant oil of lower bearing 14A are supplied to lower bearing 14, therefore can avoid utilizing the drawing of unwanted lubricant oil of oil pump 27.
At this,, investigate from the viewpoint of (bearing loss) and the viewpoint of (cooling performance of bearing) for the influence to bearing performance when the underpart of the 14a of bearing portion side is inaccessible of the oil supply 14b shown in the oil supply 14b.
About (bearing loss)
In problem, the most important thing is cooling performance about the fuel delivery of the reliability of bearing.Can be by estimation because the bearing loss that produces makes warm how many amplitudes that rise of oil infer cooling performance.Make that the bearing total length is that L, bearing radius are that r, oil viscosity are that μ, Sliding velocity are that u, gap are that C, oil clearance are δ, then bearing loss W can be represented by following formula (formula 1).In this (formula 1), if think that bearing total length L, bearing radius r, oil viscosity μ, Sliding velocity u are constant, then when oil clearance δ near zero the time, it is big that bearing loss W sharply becomes.
W=(2 π Lr μ u
2) ÷ (C (1-λ
2)
1/2) ... (formula 1)
Wherein, λ=1-(δ/C).
About (cooling performance of bearing)
Under the short situation of the length that makes oil supply, to the fuel delivery linear change of bearing, in addition, oil clearance in this case also with fuel delivery linear change pro rata, at this moment, when the length that makes oil supply more in short-term, fuel delivery reduces, and oil clearance diminishes thereupon, and bearing loss increases.But bearing loss has the big tendency of rapid change when oil clearance becomes small shown in above-mentioned (formula 1).Thus, under the situation that oil clearance becomes small, become state, so the temperature of bearing rises significantly by the big bearing loss of a spot of lubricant oil cooling change.
At this, with reference to Fig. 4 and Fig. 5, the relation that the temperature of the ratio (X/L) of the length (X) of oil supply and bearing total length (L) and bearing is risen describes.In addition, Fig. 4 is the sectional view of the size relationship of expression lower bearing 14A, Fig. 5 be expression X/L with the temperature rising of bearing (℃) the figure of relation.As shown in Figure 5,0.4 between 1 the time, bearing temperature remains below 20 degree at X/L, also is about below 40 degree between 0.4 the time 0.2 at X/L.But when X/L is 0.2 when following, oil clearance diminishes, and bearing loss increases, and cooling performance significantly reduces as a result.Therefore, X/L is preferably between 0.2 to 0.8, more preferably between 0.6 to 0.8.
In addition, in the above-described embodiment, application situation of the present invention is illustrated in the bilevel rotary compressor to existing at cylinder, still, also can be applied to the rotary compressor that cylinder is one deck.In addition,, not only can be applied to rotary compressor, also can be widely used in the hermetic type compressor that other have same compression member structure based on structure of the present invention.
More than, embodiments of the present invention are illustrated, but all aspects in this disclosed mode of execution are illustration, are not limitation of the present invention.Scope of the present invention represented by claim, means to comprise and equal meaning of claim and the whole changes in the scope.
Claims (3)
1. a hermetic type compressor has been taken in compression member (7) and driver part (8), and has been had: bent axle (26) in the inside of seal container (1); Be configured in the piston (19a, 19b) of periphery of the eccentric part (20a, 20b) of described bent axle (26); The cylinder (12a, 12b) of the cylinder chamber (11a, 11b) of the described piston of specified configuration (19a, 19b); With the bearing portion (13a, 14a) that is used for the axle described bent axle of supporting (26), this hermetic type compressor also comprises: the upper bearing (13) and the lower bearing (14) that clip described cylinder (12a, 12b) and described piston (19a, 19b) from the axle direction side of described bent axle (26), this hermetic type compressor is characterised in that, comprising:
Oil pump (27), it is arranged on the underpart of described bent axle (26), rotation along with described bent axle (26), the lubricant oil (O) that will be stored in the oil storage portion (9) of end portion of described seal container (1) is drawn in the oily path (26a) that is provided with in the mode of extending on the axis direction of described bent axle (26), provides lubricated to each sliding position of compression member (7) and driver part (8); With
Oil supply (14b), it is arranged on the slip surface of the described bearing portion (14a) of described lower bearing (14), along the axle direction extension of described bent axle (26), with the outer surface supplying lubricating oil to described bent axle (26), wherein
One distolateral end face in described cylinder (12b) side of described oil supply (14b) is open, and the distolateral underpart side at described bent axle (26) of another of described oil supply (14b) is by obturation.
2. hermetic type compressor as claimed in claim 1 is characterized in that:
The distolateral position in zone midway that is arranged on until described bearing portion (14a) of another of described oil supply (14b).
3. hermetic type compressor as claimed in claim 1 is characterized in that:
In the length that makes described oil supply (14b) is that the bearing total length of X, described bearing portion (14a) is under the situation of L, and the value of X/L is set between 0.2 to 1.0.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007-295657 | 2007-11-14 | ||
| JP2007295657A JP2009121316A (en) | 2007-11-14 | 2007-11-14 | Enclosed compressor |
| PCT/JP2008/069493 WO2009063741A1 (en) | 2007-11-14 | 2008-10-28 | Enclosed compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101861463A true CN101861463A (en) | 2010-10-13 |
| CN101861463B CN101861463B (en) | 2013-09-11 |
Family
ID=40638593
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200880116077.8A Expired - Fee Related CN101861463B (en) | 2007-11-14 | 2008-10-28 | Enclosed compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20100284833A1 (en) |
| EP (1) | EP2216551A1 (en) |
| JP (1) | JP2009121316A (en) |
| CN (1) | CN101861463B (en) |
| WO (1) | WO2009063741A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104612974A (en) * | 2014-12-22 | 2015-05-13 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN113550905A (en) * | 2021-08-26 | 2021-10-26 | 安徽美芝精密制造有限公司 | Bearing of compressor, compressor and refrigeration equipment |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5589532B2 (en) * | 2010-04-27 | 2014-09-17 | 大豊工業株式会社 | Vane pump |
| JP5879716B2 (en) * | 2011-03-23 | 2016-03-08 | 株式会社富士通ゼネラル | Rotary compressor |
| CN112352102B (en) * | 2018-06-27 | 2024-02-23 | 松下电器制冷装置新加坡 | Sealed refrigeration compressor and refrigerating and freezing device using same |
| CN114901947A (en) * | 2019-11-25 | 2022-08-12 | 松下电器制冷装置新加坡 | Hermetic refrigeration compressor and refrigerating and freezing device using same |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2202905B (en) * | 1987-03-12 | 1991-07-24 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| KR920003593B1 (en) * | 1988-02-19 | 1992-05-04 | 가부시기가이샤 히다찌세이사꾸쇼 | Scroll fluid machine with bearing lubrication |
| JP2537523Y2 (en) * | 1991-07-15 | 1997-06-04 | 三菱重工業株式会社 | Rolling piston type compressor |
| JPH081194U (en) * | 1996-01-29 | 1996-07-30 | 三洋電機株式会社 | Horizontal rotary compressor |
| JPH09222083A (en) * | 1996-02-16 | 1997-08-26 | Matsushita Electric Ind Co Ltd | Refrigerating cycle and compressor |
| US6024548A (en) * | 1997-12-08 | 2000-02-15 | Carrier Corporation | Motor bearing lubrication in rotary compressors |
| JP3858743B2 (en) * | 2002-04-03 | 2006-12-20 | ダイキン工業株式会社 | Compressor |
| CN1538071A (en) * | 2003-04-16 | 2004-10-20 | 松下电器产业株式会社 | Rotation compressor |
| JP2004332687A (en) * | 2003-05-12 | 2004-11-25 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JP2006002731A (en) * | 2004-06-21 | 2006-01-05 | Matsushita Electric Ind Co Ltd | Enclosed compressor |
| JP3979407B2 (en) | 2004-08-23 | 2007-09-19 | ダイキン工業株式会社 | Rotary compressor |
| TWI345355B (en) * | 2007-06-11 | 2011-07-11 | Sunonwealth Electr Mach Ind Co | Bearing structure |
-
2007
- 2007-11-14 JP JP2007295657A patent/JP2009121316A/en active Pending
-
2008
- 2008-10-28 WO PCT/JP2008/069493 patent/WO2009063741A1/en active Application Filing
- 2008-10-28 CN CN200880116077.8A patent/CN101861463B/en not_active Expired - Fee Related
- 2008-10-28 US US12/742,370 patent/US20100284833A1/en not_active Abandoned
- 2008-10-28 EP EP08850200A patent/EP2216551A1/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104612974A (en) * | 2014-12-22 | 2015-05-13 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN104612974B (en) * | 2014-12-22 | 2016-08-31 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN113550905A (en) * | 2021-08-26 | 2021-10-26 | 安徽美芝精密制造有限公司 | Bearing of compressor, compressor and refrigeration equipment |
| CN113550905B (en) * | 2021-08-26 | 2022-12-27 | 安徽美芝精密制造有限公司 | Bearing of compressor, compressor and refrigeration equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009063741A1 (en) | 2009-05-22 |
| JP2009121316A (en) | 2009-06-04 |
| EP2216551A1 (en) | 2010-08-11 |
| CN101861463B (en) | 2013-09-11 |
| US20100284833A1 (en) | 2010-11-11 |
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