EP3037665A1 - Compresseur hermétique - Google Patents

Compresseur hermétique Download PDF

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Publication number
EP3037665A1
EP3037665A1 EP14864603.7A EP14864603A EP3037665A1 EP 3037665 A1 EP3037665 A1 EP 3037665A1 EP 14864603 A EP14864603 A EP 14864603A EP 3037665 A1 EP3037665 A1 EP 3037665A1
Authority
EP
European Patent Office
Prior art keywords
housing
bearing housing
section
bearing
hermetic 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Withdrawn
Application number
EP14864603.7A
Other languages
German (de)
English (en)
Other versions
EP3037665A4 (fr
Inventor
Takamitsu Himeno
Kazuhiko Inoguchi
Takashi Watanabe
Taichi Tateishi
Susumu Matsuda
Yoshiyuki Kimata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3037665A1 publication Critical patent/EP3037665A1/fr
Publication of EP3037665A4 publication Critical patent/EP3037665A4/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods

Definitions

  • the present invention relates to a hermetic compressor and in particular, to a hermetic compressor in which a member which is referred to as a bearing housing is fixed to a housing by caulking.
  • a hermetic compressor which is used to compress a refrigerant in an air conditioning apparatus and other apparatuses which are provided with a refrigeration cycle is known.
  • the hermetic compressor has a configuration in which, for example, a scroll compression mechanism and an electric motor which is a driving source thereof are accommodated in a housing which forms an outer shell.
  • the scroll compression mechanism compresses a fluid by disposing a fixed scroll and an orbiting scroll, which are provided with spiral wraps, in combination with each other, and gradually reducing the volume of a compression chamber which is formed between the wraps, by revolving the orbiting scroll with respect to the fixed scroll.
  • a compression mechanism In a hermetic compressor, a compression mechanism is fixed to a housing through a bearing housing, and as one type of fixing means, caulking is known (for example, PTL 1 and PTL 2).
  • caulking due to higher-speed rotation in an operation of a compression mechanism, in addition to an increase in the pressure specifications of a refrigerant in a hermetic compressor, a load of a portion fixing a bearing housing increases, and thus, to that end, caulking is effective.
  • PTL 2 proposes a fixing structure in which an engagement margin having sufficient strength with respect to a high-pressure refrigerant is formed by providing a caulked section obtained by plastically deforming a housing, at a plurality of locations.
  • a bearing housing has a function to receive a thrust load occurring due to an operation of a compression mechanism and a function to rotatably support a main shaft which transmits a drive force of a driving source to a compression mechanism.
  • the present invention has been made based on such a technical problem and has an object to prevent damage to a housing in a caulked section, even if an excessive thrust load occurs in a compression mechanism, in a hermetic compressor in which a bearing housing is fixed to the housing by caulking.
  • a hermetic compressor including: a housing which forms an outer shell hermetically sealed with respect to the outside; a compression mechanism which is accommodated in the housing; and a bearing housing which is provided with a support section that receives a thrust load occurring due to an operation of the compression mechanism, and a bearing section that rotatably supports a main shaft which transmits a drive force of a driving source to the compression mechanism, in which the bearing housing is fixed to the housing by caulking in which a plastically deformed portion of the housing is pressed-fitted into a recess which is provided in the bearing housing, and the bearing housing has a deformation-releasing groove provided at a position corresponding to the caulking and in a surface on the side facing the compression mechanism.
  • the present invention even if an excessive thrust load acts on the bearing housing, a portion further toward the inner periphery side than the deformation-releasing groove, is preferentially deformed, whereby the thrust load is prevented from being transmitted to the caulking which is located further toward the outer periphery side than the deformation-releasing groove. Therefore, it is possible to prevent an opening edge of the recess of the bearing housing from damaging the housing at a caulked section.
  • an opening edge of the recess which is provided in the bearing housing is R-machined, because it is possible to prevent local stress from occurring in the housing due to receiving a load from the opening edge of the recess.
  • the recess which is provided in the bearing housing is formed in a tapered shape which is tapered toward an inner part from an opening edge, because a large press-fit margin of the housing which is fastened to the recess can be obtained.
  • a self-aligning mechanism in response to the occurrence of an especially excessive thrust load, can be interposed between the recess and the plastically deformed portion of the housing.
  • the self-aligning mechanism functions, thereby absorbing the deformation, and therefore, it is possible to prevent damage to the housing.
  • a scroll compressor 1 according to this embodiment is provided with a housing 3, a fixed scroll 5, an orbiting scroll 7, a main shaft 9, and a rotation-preventing section 11, as shown in Fig. 1 , and a bearing housing 19 is fixed to the housing 3 by caulking. Further, in the scroll compressor 1, a deformation-releasing groove 19f which prevents damage from occurring in a caulked section, even if an excessive thrust load is applied, is provided in the bearing housing 19.
  • the deformation-releasing groove 19f will be described.
  • the housing 3 is a hermetically-sealed container in which members configuring a compression mechanism, such as the fixed scroll 5 and the orbiting scroll 7, are accommodated and installed, as shown in Fig. 1 .
  • a discharge cover 13, a suction pipe (not shown), a discharge pipe 17, and the bearing housing 19 are provided in the housing 3.
  • the discharge cover 13 is for separating the interior of the housing 3 into a high-pressure chamber HR and a low-pressure chamber LR.
  • the suction pipe is for leading a low-pressure refrigerant from the outside to the low-pressure chamber LR
  • the discharge pipe 17 is for leading a high-pressure refrigerant from the high-pressure chamber HR to the outside.
  • the bearing housing 19 is for supporting the compression mechanism composed of the fixed scroll 5 and the orbiting scroll 7 and rotatably supporting the main shaft 9.
  • the main shaft 9 is for transmitting a rotational driving force of an electric motor (not shown), which is provided on the lower side of the interior of the housing 3, to the orbiting scroll 7.
  • the main shaft 9 is substantially perpendicularly and rotatably supported in the interior of the housing 3.
  • An eccentric pin 9a which drives the orbiting scroll 7 so as to revolve is provided at an upper end portion of the main shaft 9.
  • the eccentric pin 9a is a columnar member which is provided at a position eccentric by an orbiting revolution radius r of the orbiting scroll 7 from the rotation center of the main shaft 9 on an upper end face of the main shaft 9.
  • the fixed scroll 5 and the orbiting scroll 7 are for compressing a fluid which has flowed into the low-pressure chamber LR of the housing 3, and then discharging the fluid to the high-pressure chamber HR.
  • the fixed scroll 5 and the orbiting scroll 7 are disposed such that the fixed scroll 5 and the orbiting scroll 7 are respectively disposed on the upper side and the lower side in the interior of the housing 3 and both the scrolls 5 and 7 are engaged with each other.
  • the fixed scroll 5 is supported on the bearing housing 19 from the lower side through the orbiting scroll 7, thereby being disposed at a fixed position of the housing 3.
  • a discharge port 21 through which the compressed fluid is discharged is provided at the back face center (the upper surface center in Fig. 1 ) of an end plate 5a of the fixed scroll 5.
  • the orbiting scroll 7 is supported on the bearing housing 19 so as to be able to revolve with respect to the fixed scroll 5.
  • a boss 23 into which the eccentric pin 9a of the main shaft 9 is inserted is provided at the back face center (the lower surface center in Fig. 1 ) of an end plate 7a of the orbiting scroll 7.
  • a recessed portion 25 in which a ring 27 of the rotation-preventing section 11 is disposed is formed on a circle having a predetermined radius from the center of the orbiting scroll 7.
  • the recessed portion 25 is formed in a substantially circular shape when viewed from the main shaft 9 side.
  • the bearing housing 19 is a substantially annular member which is supported on the housing 3 by a caulked section 30.
  • the bearing housing 19 is provided with a bearing section 19b which is located on the inner periphery side and rotatably supports the main shaft 9, a fixed section 19c which is located on the outer periphery side and faces the housing 3, a support section 19d which is provided further toward the outer periphery side than the bearing section 19b and supports the orbiting scroll 7, and a connecting section 19e which connects the fixed section 19c and the support section 19d, as shown in Fig. 3(a) .
  • the bearing housing 19 supports the orbiting scroll 7 in a vertical direction at the support section 19d, and therefore, if a refrigerant is compressed between the orbiting scroll 7 and the fixed scroll 5, the support section 19d receives a thrust load Fs.
  • the caulked section 30 is provided at a plurality of locations, whereby even if the bearing housing 19 receives an excessive thrust load Fs, the bearing housing 19 can take the load.
  • the deformation-releasing groove 19f is formed in the bearing housing 19 such that, even if the bearing housing 19 receives an excessive thrust load, the housing 3 is prevented from being damaged due to receiving a local load from the bearing housing 19. The deformation-releasing groove 19f will be described in more detail along with the caulked section 30 which will be described later.
  • a plurality of caulked sections 30 disposed at regular intervals, for example, 120-degree intervals, in a circumferential direction are formed at proper places of the side face of the compression mechanism in order to fix the bearing housing 19 accommodated in the housing 3.
  • the caulked section 30 is formed by fitting a portion of the housing 3 into a recess 19a formed by recessing a portion of the bearing housing 19, as shown in Fig. 2(c) .
  • the recess 19a is formed in advance, as shown in Fig. 2 (a) .
  • the caulked section 30 is formed by plastically deforming a portion of the housing 3 in a recessed portion shape by pressing a punch 40 so as to drive it toward the recess 19a from the outside of the housing 3, as shown in Fig. 2(c) .
  • the caulked sections 30 having sufficient strength in this method are formed at an equal pitch in the circumferential direction at a plurality of locations, it is possible to reliably fix the bearing housing 19 by the caulked sections 30 with an engagement margin having sufficient strength formed therein, even with respect to the housing 3 with a plate thickness increased for coping with a high-pressure refrigerant.
  • the caulked section 30 between the housing 3 and the bearing housing 19 it is preferable to plastically deform a location corresponding to the caulked section 30, of the housing 3, by heating (for example, in a range of 700°C to 800°C) the location, because workability can be greatly improved.
  • the deformation-releasing groove 19f is formed along the circumferential direction in the bearing housing 19, as shown in Figs. 1 , 3 , and 4 .
  • the deformation-releasing groove 19f is formed in the upper surface of the connecting section 19e, that is, the surface on the side facing the compression mechanism composed of the fixed scroll 5 and the orbiting scroll 7, of the connecting section 19e.
  • the support section 19d which receives the thrust load Fs serves as a point of action Pa and the caulked section 30 serves as a fulcrum Ps. Therefore, a bending moment M in a clockwise direction in the drawing occurs in the bearing housing 19 with the caulked section 30 as the fulcrum Ps.
  • the deformation-releasing groove 19f is provided in a range of a line segment connecting the fulcrum Ps and the point of action Pa and on the side to which the thrust load Fs is applied, with the line segment as a boundary.
  • the deformation-releasing groove 19f can be formed in the form of a ring connected continuously in the circumferential direction, as shown in Fig. 4(a) , and can also be formed to be divided into a plurality of sections in the circumferential direction, as shown in Fig. 4(b) .
  • the deformation-releasing groove 19f needs to be provided corresponding to the caulked section 30.
  • the expression, corresponding to the caulked section 30, refers to the deformation-releasing groove 19f being formed to overlap a line segment connecting each of the caulked sections 30 and the center of the bearing housing 19. If so, it is possible to obtain the above-described effect of preventing the thrust load Fs from being transmitted to the caulked section 30.
  • the deformation-releasing groove 19f has been thus far described as having an arc shape in a plan view.
  • the present invention is not limited thereto, and as long as the effect of preventing the thrust load Fs from being transmitted to the caulked section 30 is exhibited, a shape in a plan view does not matter.
  • the deformation-releasing groove 19f may be formed in a straight line shape and may be formed in a chevron shape peaking toward the outer periphery side.
  • the depth of the deformation-releasing groove 19f the more easily the portion on the inner periphery side is deformed.
  • the strength of the bearing housing 19 decreases, it is desirable to select a depth taking into account these two factors.
  • a range of about 1/10 to 2/10 of the wall thickness of a portion (in this embodiment, the connecting section 19e) in which the deformation-releasing groove 19f is provided is set as a reference. It is favorable if the width of the deformation-releasing groove 19f is also set according to the same guideline.
  • the wall thickness of the bearing housing 19 the wall thickness of the portion in which the deformation-releasing groove 19f is provided
  • the wall thickness of the bearing housing 19 the wall thickness of the portion in which the deformation-releasing groove 19f is provided
  • the depth of the deformation-releasing groove 19f is set to be in a range of 1 mm to 2 mm and the width is set to be in a range of about 1 mm to 2 mm. Further, in a case where the wall thickness of the bearing housing 19 is 20 mm, it is favorable if the depth of the deformation-releasing groove 19f is set to be in a range of 2 mm to 4 mm and the width is set to be in a range of about 2 mm to 4 mm.
  • a radius of curvature in the R-machining is set to be greater than or equal to 1 mm in order to reduce stress concentration.
  • the shape of the recess 19a will be described. As shown in Fig. 5(b) , it is preferable to machine the recess 19a in a tapered shape which is tapered toward the inner part of the recess 19a from the opening edge. If it approaches the inner part of the recess 19a, the opening diameter becomes narrower, and therefore, a large press-fit margin of the housing 3 which is fastened to the recess 19a can be obtained. Therefore, it is possible to increase fastening force between the bearing housing 19 and the housing 3 in the caulked section 30, and therefore, fixation by the caulked section 30 can be more reliably made.
  • a preferred range is present in the degree of the inclination of the taper, and thus, if the diameter of the opening edge of the recess 19a is set to be ⁇ D and the diameter of the inner part side is set to be ⁇ d, according to the following expression, the effect due to the formation of the taper becomes remarkable. ⁇ d ⁇ 0.998 ⁇ ⁇ D
  • the second embodiment corresponds to a case where a thrust load is larger.
  • description will be made with a focus on differences from the first embodiment, and the same elements as those in the first embodiment are denoted by the same reference numerals in Fig. 6 .
  • a self-aligning bearing 50 is interposed in the caulked section 30.
  • the self-aligning bearing 50 is provided with an inner ring 51, an outer ring 53, a rolling element 55 which is provided between the inner ring 51 and the outer ring 53, and a cage (not shown), as shown in Fig. 6(a) .
  • the self-aligning bearing 50 has an alignment property that the axes of the inner ring 51, the rolling element 55, and the cage can freely rotate around the bearing center, because the raceway surface of the outer ring 53 is a spherical surface and the center of curvature coincides with the bearing center.
  • an allowable aligning angle is in a range of about 0.07 radians to 0.12 radians (a range of 4 degrees to 7 degrees).
  • the self-aligning bearing 50 is interposed between the recess 19a and a plastically deformed portion of the housing 3 with the inner ring 51 provided to radially face the housing 3 side and the outer ring 53 provided to radially face the bearing housing 19 side, as shown in Fig. 6 .
  • the self-aligning bearing 50 is assembled to be interposed between the housing 3 and the bearing housing 19.
  • the caulked section 30 of the second embodiment even if a very large thrust load acts, whereby deformation occurs in the bearing housing 19, the self-aligning bearing 50 functions, thereby absorbing the deformation, as shown in Fig. 6(b) , and therefore, it is possible to prevent damage to the housing 3.
  • the self-aligning bearing 50 shown in the second embodiment may be applied to the caulked section 30 of the hermetic compressor shown in the first embodiment.
  • the scroll compressor has been described as an example of the hermetic compressor.
  • the present invention to a scroll compression mechanism part of a hermetic compressor which is provided with both a rotary compression mechanism and a scroll compression mechanism as a compression mechanism.
  • the structure of the bearing housing 19 is arbitrary as long as it has a function to support a thrust load occurring due to an operation of a compression mechanism and a function to slidably support a main shaft which transmits a drive force of a driving source to a compression mechanism.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP14864603.7A 2013-11-19 2014-06-13 Compresseur hermétique Withdrawn EP3037665A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013238611A JP6199708B2 (ja) 2013-11-19 2013-11-19 密閉型圧縮機
PCT/JP2014/003163 WO2015075851A1 (fr) 2013-11-19 2014-06-13 Compresseur hermétique

Publications (2)

Publication Number Publication Date
EP3037665A1 true EP3037665A1 (fr) 2016-06-29
EP3037665A4 EP3037665A4 (fr) 2016-12-28

Family

ID=53179150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14864603.7A Withdrawn EP3037665A4 (fr) 2013-11-19 2014-06-13 Compresseur hermétique

Country Status (3)

Country Link
EP (1) EP3037665A4 (fr)
JP (1) JP6199708B2 (fr)
WO (1) WO2015075851A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3311933A1 (fr) * 2016-10-20 2018-04-25 Mitsubishi Heavy Industries Thermal Systems, Ltd. Outil de calfeutrage, procédé de fabrication de structure de calfeutrage et procédé de fabrication de compresseur

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017137846A (ja) * 2016-02-05 2017-08-10 三菱重工業株式会社 回転機械
CN109723642A (zh) * 2019-03-05 2019-05-07 苏州为山之环境技术有限公司 一种具有铆焊结构壳体的涡旋压缩机
DE102020215911A1 (de) 2020-12-15 2022-06-15 Siemens Energy Global GmbH & Co. KG Dichtung
DE102021126248A1 (de) * 2021-10-11 2023-04-13 Hanon Systems Kältemittelverdichter

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JP4949811B2 (ja) 2006-11-17 2012-06-13 三菱重工業株式会社 密閉型圧縮機の圧縮機構固定構造
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Publication number Priority date Publication date Assignee Title
EP3311933A1 (fr) * 2016-10-20 2018-04-25 Mitsubishi Heavy Industries Thermal Systems, Ltd. Outil de calfeutrage, procédé de fabrication de structure de calfeutrage et procédé de fabrication de compresseur

Also Published As

Publication number Publication date
WO2015075851A1 (fr) 2015-05-28
JP2015098812A (ja) 2015-05-28
JP6199708B2 (ja) 2017-09-20
EP3037665A4 (fr) 2016-12-28

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