CN204532827U - Hermetic type compressor - Google Patents
Hermetic type compressor Download PDFInfo
- Publication number
- CN204532827U CN204532827U CN201520068352.0U CN201520068352U CN204532827U CN 204532827 U CN204532827 U CN 204532827U CN 201520068352 U CN201520068352 U CN 201520068352U CN 204532827 U CN204532827 U CN 204532827U
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- CN
- China
- Prior art keywords
- seal container
- groove portion
- mechanical part
- compression mechanical
- type compressor
- 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.)
- Withdrawn - After Issue
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Abstract
The utility model relates to a kind of hermetic type compressor.This hermetic type compressor comprises: the seal container (1) of drum; And compression mechanical part (3), it is accommodated in seal container (1), and be formed with abutting support (17) at outer circumferential face, this abutting support (17) abuts with the inner peripheral surface of seal container (1), at the outer circumferential face of compression mechanical part (3), axis along seal container (1) is formed with groove portion (16), at the abutting support (17) opposed with groove portion (16), compression mechanical part (3) and seal container (1) are welded together.
Description
Technical field
The utility model relates to hermetic type compressor.
Background technique
As existing hermetic type compressor, be known to following structure, it possesses in seal container inside: motor part; And compression mechanical part, it is driven by motor part.Compression mechanical part is configured to be possessed: bent axle, and it has the eccentric axial portion for the rotating force of motor part being passed to compression mechanical part; Piston, it is arranged in rotatable mode chimeric with eccentric axial portion; Cylinder body, it has cylindric air chamber; Blade, its mode being arranged to slide freely is chimeric with the blade groove being arranged at cylinder body; And upper bearing (metal) and lower bearing, they are arranged at the axial two ends of cylinder body.
In the existing hermetic type compressor formed as described above, owing to seal container and compression mechanical part being welded and fixed, therefore, stress is produced at cylinder body.Such as, as the stress putting on cylinder body because carrying out being welded and fixed, following stress etc. can be enumerated: the thermal stress produced because there is thermal change from welding position to cylinder interior; The stress produced because cylinder body during welding is pressed against seal container in the opposed faces of welding position; And because welding the stress that the cooling of rear welding position makes seal container produce to the direction contraction of welding position.
The above-mentioned stress acting on cylinder body concentrates on the blade groove formed in a non-symmetrical way relative to the cylinder body of drum, and therefore, in the past, blade groove deformed sometimes.Therefore, in the past, exist and worry as follows: the sliding between blade and blade groove is deteriorated, compression performance reduces, and then causes blade wear/damage.
For this problem, such as, in patent documentation 1 shown below, cylinder body is fixedly welded on seal container in the portion of being welded and fixed at 3 positions, place, be welded and fixed between portion and blade groove across two positions, place of blade groove in the position that these are welded and fixed, be disposed radially groove respectively.In the prior art shown in patent documentation 1, by forming radial slot at cylinder body, the thermal stress produced when making to be welded and fixed is difficult to, to blade groove transmission, suppress the distortion of blade groove thus.
In addition, in patent documentation 2 shown below, utilize screw that bracket is fixed on cylinder body, and bracket and seal container are welded and fixed, thus the distortion that when can not make welding, bracket produces, directly to cylinder body transmission, suppresses the distortion of blade groove thus.In addition, in the prior art described in patent documentation 2, be formed as following structure: otch is set near the welding position of bracket, be difficult to cylinder body transmission to make thermal stress.
Patent documentation 1: Japanese Unexamined Patent Publication 11-324958 publication (the 5th page, Fig. 6)
Patent documentation 2: Japanese Unexamined Patent Publication 9-32731 publication (the 4th page, Fig. 1 and Fig. 2)
But, in the prior art shown in patent documentation 1, the thermal stress produced when only making to be welded and fixed is difficult to blade groove transmission, be difficult to the stress suppressing to produce because cylinder body during welding is pressed against seal container in the opposed faces of welding position, and because welding the stress that the cooling of rear welding position makes seal container produce to the direction contraction of welding position.Therefore, in the prior art involved by patent documentation 1, blade groove still likely deforms.
In addition, in the prior art shown in patent documentation 2, utilize screw that bracket is fixed on cylinder body, and bracket and seal container are welded and fixed, thus, the distortion that bracket can not be made to produce is directly to cylinder body transmission, but but there are the following problems: the additional of bracket is directly connected to the increase of cost and the increase of weight.
Model utility content
The utility model proposes to solve above-mentioned problem, its object is to obtain a kind of hermetic type compressor, by means of the distortion of simple STRUCTURE DEPRESSION blade groove, thus realizes the raising of cost degradation, high reliability and compression efficiency.
Hermetic type compressor involved by the utility model comprises: the seal container of drum; And compression mechanical part, it is accommodated in above-mentioned seal container, and be formed with abutting support at outer circumferential face, this abutting support abuts with the inner peripheral surface of above-mentioned seal container, at the outer circumferential face in compression mechanism portion, axis along above-mentioned seal container is formed with groove portion, at the above-mentioned abutting support opposed with above-mentioned groove portion, is welded together in compression mechanism portion and above-mentioned seal container.
According to the utility model, can be accomplished the hermetic type compressor of raising of cost degradation, high reliability and compression efficiency.
Preferably, at the outer circumferential face of described compression mechanical part, form multiple described abutting support in the mode being formed with multiple described groove portion along its circumference.
Preferably, each in described multiple groove portion is respectively formed between adjacent described abutting support.
Preferably, respectively with each the opposed described abutting support in described multiple groove portion, described compression mechanical part and described seal container are welded together.
Preferably, the quantity in described groove portion equals the quantity in the portion that is welded and fixed of described compression mechanical part and described seal container.
Preferably, the portion of being welded and fixed of described compression mechanical part and described seal container is in central shaft around the described seal container scope of 140 degree ~ 220 degree from described groove portion.
Preferably, described groove portion be formed as that its length reaches the circumferential length of described compression mechanical part along the circumference of described compression mechanical part 1% ~ 20%.
Accompanying drawing explanation
Fig. 1 is the synoptic diagram of the longitudinal cross-section of the hermetic type compressor summarily illustrated involved by mode of execution 1 of the present utility model.
Fig. 2 is the transverse sectional view in the portion that is welded and fixed that the seal container shown in Fig. 1 and compression mechanical part are shown.
Fig. 3 is the enlarged view in the groove portion shown in Fig. 2.
The explanation of reference character:
1... seal container; 2... motor part; 3... compression mechanical part; 4... main shaft; 5... eccentric axial portion; 6... cylinder body; 7... upper bearing (metal); 8... lower bearing; 9... piston; 10... blade groove; 11... blade; 12... spring members; 13... pressing chamber; 14... suction port; 15... portion is welded and fixed; 16... groove portion; 17... support is abutted; 18... through hole; 19... screw; 20... stress; 21... stress; 50... suction silencer; 100... hermetic type compressor.
Embodiment
Below, with reference to accompanying drawing, mode of execution of the present utility model is described.In addition, in the various figures, identical reference character is marked for identical or suitable part, and suitably omit or simplify its explanation.
Mode of execution 1.
Fig. 1 is the synoptic diagram of the longitudinal cross-section of the hermetic type compressor 100 summarily illustrated involved by mode of execution 1 of the present utility model.Fig. 2 is the transverse sectional view in the portion that is welded and fixed 15 that the seal container 1 shown in Fig. 1 and compression mechanical part 3 are shown.As shown in Figure 1, motor part 2 and compression mechanical part 3 is accommodated with in the inside of seal container 1.Motor part 2 via main shaft 4 to compression mechanical part 3 transmission of drive force.In addition, in the following description, by the axis (illustrated above-below direction) of the seal container 1 of drum referred to as axis, by from the central shaft of seal container 1 by and the direction intersected with central shaft referred to as radial direction.
Compression mechanical part 3 comprises eccentric axial portion 5, cylinder body 6, upper bearing (metal) 7, lower bearing 8 and piston 9.Eccentric axial portion 5 is installed on main shaft 4, and the driving force from compression mechanical part 3 is passed to this eccentric axial portion 5.At the axial two ends of cylinder body 6, upper bearing (metal) 7 and lower bearing 8 are installed.Cylinder body 6, upper bearing (metal) 7 and lower bearing 8 form the pressing chamber 13 shown in Fig. 2.Be configured with in pressing chamber 13: eccentric axial portion 5, it is installed on main shaft 4; Piston 9, it is installed on eccentric axial portion 5; And blade 11.
Radial blade groove 10 is formed at cylinder body 6.Blade 11 remains along and radially slides freely by blade groove 10.In the back side of blade 11, between blade 11 and seal container 1, be provided with spring members 12.Blade 11 is pressed towards piston 9 by spring members 12.
In addition, radial suction port 14 is formed with at cylinder body 6.The refrigeration agent sucked from the suction silencer 50 shown in Fig. 1 is imported in pressing chamber 13 by from the suction port 14 shown in Fig. 2.Upper bearing (metal) 7 shown in Fig. 1 and lower bearing 8, be formed and omit illustrated exhaust port, discharged in pressing chamber 13 by the refrigeration agent compressed from exhaust port.Exhaust port is formed as being communicated with pressing chamber 13 in contrary side across blade 11 with the suction port 14 shown in Fig. 2.In addition, be axially formed with such as multiple through hole 18 and multiple screw 19 etc. at cylinder body 6, they form refrigerant flow path.
Next, the action of the hermetic type compressor 100 formed as described above is described.By drive motor portion 2, rotating force is transmitted by main shaft 4.The rotating force being passed to main shaft 4 transmits to the eccentric axial portion 5 being installed on main shaft 4, thus the piston 9 being installed on eccentric axial portion 5 carries out spinning motion (rotation) in pressing chamber 13.
If piston 9 rotates in pressing chamber 13, then in pressing chamber 13, supply the refrigeration agent of low pressure from suction port 14.Further, because piston 9 rotates, thus the volume of pressing chamber 13 reduces, and refrigeration agent is compressed.Discharged in seal container 1 from the exhaust port formed at upper bearing (metal) 7 and lower bearing 8 by the refrigeration agent compressed.Now, blade 11 is pressed on piston 9 by the refrigeration agent by the high pressure be discharged in spring members 12 and seal container 1, thus blade 11 radially slides in blade groove 10 in the mode linked with the action of piston 9.Blade 11 carries out action in like fashion, thus plays the effect separated in the suction side of cylinder body 6 and discharge side.
Next, utilize Fig. 2, seal container 1 and being welded and fixed of compression mechanical part 3 are specifically described.In the present embodiment, the example welded with seal container 1 by cylinder body 6 is described.
Cylinder body 6 is accommodated in the seal container 1 of drum.Cylinder body 6 is roughly drum, and its outer circumferential face abuts with the inner peripheral surface of seal container 1.The outer circumferential face of the cylinder body 6 abutted with the inner peripheral surface of seal container 1 forms and abuts support 17.
At the outer circumferential face of cylinder body 6, be formed with 3 groove portions 16 along its circumference.Each groove portion 16 is formed as seal container 1 is not contacted with cylinder body 6 along the axis of seal container 1.Each groove portion 16 extends vertically in the mode be communicated with the upper surface and lower surface of cylinder body 6, and owing to forming 3 groove portions 16, thus 3 of being formed circumferentially abut support 17.Each groove portion 16 does not contact with seal container 1, and between adjacent abutting support 17.In addition, the circumferential lengths L in each groove portion 16 is preferably 1% ~ 20% of the circumferential length of cylinder body 6.
In the portion that is welded and fixed 15 of the abutting support 17 opposed with groove portion 16, cylinder body 6 and seal container 1 are welded and fixed.That is, at the abutting support 17 being in the opposition side in groove portion 16 across the central shaft of seal container 1 and pressing chamber 13, cylinder body 6 and seal container 1 are welded and fixed.That is, in the present embodiment, across central shaft and the pressing chamber 13 of seal container 1, form groove portion 16 in side and at the outer circumferential face of cylinder body 6, at opposite side, cylinder body 6 and seal container 1 are welded and fixed.In addition, such as welding of cylinder body 6 and seal container 1 is carried out by the mode of the arc weldings such as arc spot welding.
Cylinder body 6 is preferably equal with the quantity in groove portion 16 with the quantity in the portion that is welded and fixed 15 of seal container 1.In the present embodiment, owing to forming 3 groove portions 16, therefore, be welded and fixed portion 15 and be in 3 positions, place.In addition, preferred weld fixing part 15 be in from the groove portion 16 opposed with being welded and fixed portion 15 around seal container 1 central shaft the scope of 140 degree ~ 220 degree.
Fig. 3 is the enlarged view in the groove portion 16 shown in Fig. 2.If weld being welded and fixed portion 15, then produce radial stress 20 in its opposed position.Stress 20 is the stress 20 of the radial direction produced by the reaction from seal container 1 because cylinder body 6 during welding is pressed against seal container 1.Or stress 20 makes seal container 1 shrink because being welded and fixed portion 15 cooling after welding, and the stress 20 of radial direction that seal container 1 pair of cylinder body 6 presses and produces.
In the present embodiment, as shown in Figure 2, groove portion 16 is formed with in the position opposed with being welded and fixed portion 15.That is, along the radial direction being welded and fixed portion 15, groove portion 16 is configured with at the opposition side of cylinder body 6.Therefore, as shown in Figure 3, stress 20 acts on the position corresponding with groove portion 16.Groove portion 16 is to be formed relative to the asymmetrical mode of the peripheral shape of cylinder body 6, and therefore, radial stress 20 concentrates on groove portion 16.Specifically, radial stress 20 acts on the groove portion 16 of cylinder body 6 as stress 21.Therefore, even if when producing larger stress 20, also only there is small distortion in the end in groove portion 16, stress 20 is disperseed.Its result, in the present embodiment, the distortion of the inside of cylinder body 6 is suppressed.
As described above, in the present embodiment, the distortion of the blade groove 10 formed in the inside of cylinder body 6 can be suppressed, therefore, it is possible to reduce the gap between blade groove 10 and blade 11.Therefore, in the present embodiment, the leakage loss in compression section can be reduced, thus the efficiency of compressor can be improved.Its result, in the present embodiment, can realize compressor and possess the energy-saving of air conditioner of compressor.
In addition, preferred weld fixing part 15 be in from the groove portion 16 opposed with being welded and fixed portion 15 around seal container 1 central shaft the scope of 140 degree ~ 220 degree.Like this, be welded and fixed portion 15 by configuration, the stress 20 of the radial direction produced during welding can be made suitably to act on groove portion 16.
In addition, the circumferential lengths L in preferred groove portion 16 is 1% ~ 20% of the circumferential length of cylinder body 6.By forming groove portion 16 in like fashion, can guarantee to abut the frictional force between support 17 and seal container 1, and the stress 20 of the radial direction produced during welding can be made suitably to act on groove portion 16.
As described above, in the present embodiment, in the position opposed with groove portion 16, welding of cylinder body 6 and seal container 1 is carried out.Its result, in the present embodiment, the stress 20 of the radial direction produced during welding concentrates on groove portion 16, and therefore, stress can not directly act on cylinder body 6.Therefore, in the present embodiment, following hermetic type compressor 100 can be obtained: the distortion being formed at the blade groove 10 of cylinder body 6 with simple STRUCTURE DEPRESSION, thus achieve the raising of cost degradation, high reliability and compression efficiency.
The utility model is not limited to above-mentioned mode of execution, can carry out various change in scope of the present utility model.That is, suitably can improve the structure of above-mentioned mode of execution, in addition, also will can replace with other structures at least partially.Further, its configuration mode is not limited to the configuration mode disclosed in mode of execution by the constitutive requirements of particular determination, can be configured at the position that can realize its function.
Such as, in the above-described embodiment, the example in formation 3 groove portions 16 is illustrated, but the quantity in groove portion 16 can suitably change.
In addition, such as, in the above-described embodiment, the example welded with seal container 1 by cylinder body 6 is illustrated, but, also can be applied to the situation of other structures such as upper bearing (metal) 7 or lower bearing 8 being welded with seal container 1.That is, in other vibrational power flow groove portions such as upper bearing (metal) 7 or lower bearings 8 and support can be abutted, and carry out in the position opposed with groove portion and the welding of seal container 1.In this case, the stress of the radial direction produced during welding also concentrates on groove portion, therefore, stress also can be suppressed to directly act on the component parts being formed with groove portion.
Claims (7)
1. a hermetic type compressor, is characterized in that, comprising:
The seal container of drum; And
Compression mechanical part, it is accommodated in described seal container, and is formed with abutting support at outer circumferential face, and this abutting support abuts with the inner peripheral surface of described seal container,
At the outer circumferential face of described compression mechanical part, the axis along described seal container forms groove portion,
At the described abutting support opposed with described groove portion, described compression mechanical part and described seal container are welded together.
2. hermetic type compressor according to claim 1, is characterized in that,
At the outer circumferential face of described compression mechanical part, form multiple described abutting support in the mode being formed with multiple described groove portion along its circumference.
3. hermetic type compressor according to claim 2, is characterized in that,
Each in described multiple groove portion is respectively formed between adjacent described abutting support.
4. the hermetic type compressor according to Claims 2 or 3, is characterized in that,
Respectively with each the opposed described abutting support in described multiple groove portion, described compression mechanical part and described seal container are welded together.
5. the hermetic type compressor according to any one of claims 1 to 3, is characterized in that,
The quantity in described groove portion equals the quantity in the portion that is welded and fixed of described compression mechanical part and described seal container.
6. the hermetic type compressor according to any one of claims 1 to 3, is characterized in that,
The portion of being welded and fixed of described compression mechanical part and described seal container is in central shaft around the described seal container scope of 140 degree ~ 220 degree from described groove portion.
7. the hermetic type compressor according to any one of claims 1 to 3, is characterized in that,
Described groove portion be formed as that its length reaches the circumferential length of described compression mechanical part along the circumference of described compression mechanical part 1% ~ 20%.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-021887 | 2014-02-07 | ||
| JP2014021887A JP6257364B2 (en) | 2014-02-07 | 2014-02-07 | Hermetic compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204532827U true CN204532827U (en) | 2015-08-05 |
Family
ID=53746836
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520068352.0U Withdrawn - After Issue CN204532827U (en) | 2014-02-07 | 2015-01-30 | Hermetic type compressor |
| CN201510050044.XA Active CN104832435B (en) | 2014-02-07 | 2015-01-30 | Hermetic type compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510050044.XA Active CN104832435B (en) | 2014-02-07 | 2015-01-30 | Hermetic type compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6257364B2 (en) |
| CN (2) | CN204532827U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104832435A (en) * | 2014-02-07 | 2015-08-12 | 三菱电机株式会社 | Hermetic compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114017296A (en) * | 2021-11-08 | 2022-02-08 | 广东美芝制冷设备有限公司 | Cylinder, compressor, refrigeration equipment and manufacturing method |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3323353B2 (en) * | 1995-03-02 | 2002-09-09 | 東芝キヤリア株式会社 | compressor |
| JPH10318170A (en) * | 1997-05-20 | 1998-12-02 | Toshiba Corp | Compressor |
| JP3518305B2 (en) * | 1998-01-21 | 2004-04-12 | 三菱電機株式会社 | Fluid machinery |
| JP2001182681A (en) * | 1999-12-27 | 2001-07-06 | Matsushita Electric Ind Co Ltd | Hermetically sealed motor-driven compressor |
| JP2001295783A (en) * | 2000-04-13 | 2001-10-26 | Mitsubishi Electric Corp | Hermetic rotary compressor |
| JP2002339870A (en) * | 2001-05-17 | 2002-11-27 | Mitsubishi Electric Corp | Fixed member flattening method |
| US7604466B2 (en) * | 2005-01-31 | 2009-10-20 | Tecumseh Products Company | Discharge muffler system for a rotary compressor |
| KR100811654B1 (en) * | 2005-07-29 | 2008-03-11 | 삼성전자주식회사 | Rotary compressor |
| JP6257364B2 (en) * | 2014-02-07 | 2018-01-10 | 三菱電機株式会社 | Hermetic compressor |
-
2014
- 2014-02-07 JP JP2014021887A patent/JP6257364B2/en active Active
-
2015
- 2015-01-30 CN CN201520068352.0U patent/CN204532827U/en not_active Withdrawn - After Issue
- 2015-01-30 CN CN201510050044.XA patent/CN104832435B/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104832435A (en) * | 2014-02-07 | 2015-08-12 | 三菱电机株式会社 | Hermetic compressor |
| CN104832435B (en) * | 2014-02-07 | 2017-11-28 | 三菱电机株式会社 | Hermetic type compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6257364B2 (en) | 2018-01-10 |
| JP2015148199A (en) | 2015-08-20 |
| CN104832435B (en) | 2017-11-28 |
| CN104832435A (en) | 2015-08-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150805 Effective date of abandoning: 20171128 |
|
| AV01 | Patent right actively abandoned |