US20090068035A1 - Refrigerant compressor arrangement - Google Patents

Refrigerant compressor arrangement Download PDF

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Publication number
US20090068035A1
US20090068035A1 US12/185,982 US18598208A US2009068035A1 US 20090068035 A1 US20090068035 A1 US 20090068035A1 US 18598208 A US18598208 A US 18598208A US 2009068035 A1 US2009068035 A1 US 2009068035A1
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US
United States
Prior art keywords
drive shaft
rotor
arrangement according
bearing section
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.)
Abandoned
Application number
US12/185,982
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English (en)
Inventor
Jesper Valbjoern
Kristoffer Riemann Hansen
Anders Jakob Madsen
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.)
Secop GmbH
Original Assignee
Danfoss Compressors GmbH
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 Danfoss Compressors GmbH filed Critical Danfoss Compressors GmbH
Assigned to DANFOSS COMPRESSORS GMBH reassignment DANFOSS COMPRESSORS GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HANSEN, KRISTOFFER RIEMANN, MADSEN, ANDERS JAKOB, VALBJOERN, JESPER
Publication of US20090068035A1 publication Critical patent/US20090068035A1/en
Assigned to SECOP GMBH (FORMERLY KNOWN AS DANFOSS HOUSEHOLD COMPRESSORS GMBH) reassignment SECOP GMBH (FORMERLY KNOWN AS DANFOSS HOUSEHOLD COMPRESSORS GMBH) ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DANFOSS FLENSBURG GMBH (FORMERLY KNOWN AS DANFOSS COMPRESSORS GMBH)
Abandoned 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections

Definitions

  • the invention concerns a refrigerant compressor arrangement with a compressor block comprising a compressor unit with a cylinder formed in the compressor block, and with a motor having a stator and a rotor, the rotor being unrotatably connected to a drive shaft driving the compressor unit, the drive shaft being supported in a bearing section of the compressor block.
  • Such a refrigerant compressor arrangement is, for example, known from DE 195 16 811 C2.
  • the compressor is formed as a piston compressor, in which a piston, which is connected to a crank pin of the drive shaft via a connecting rod, reciprocates in a cylinder, thus sucking in and compressing refrigerant.
  • the bearing section has a radial bearing and an axial bearing for the drive shaft. The bearing section ends above the rotor.
  • a similar refrigerant compressor arrangement is known from DE 35 21 742 A1. Also here, a cylinder is formed on the upper side of the compressor block, a piston, driven by the drive shaft via a connecting rod, reciprocating in the cylinder.
  • the bearing section, in which the drive shaft is supported, is offset somewhat into the rotor.
  • the refrigerant compressor arrangement requires a certain total height.
  • the space required by the refrigerant compressor arrangement will not be available as refrigeration space.
  • the invention is based on the task of providing refrigerant compressor arrangements with a small total height.
  • this task is solved in that the bearing section penetrates an active area of the stator and that the rotor and the drive shaft are connected to each other outside the active area on the side of the rotor facing away from the compressor unit.
  • the active area of the stator is the area, in which the real driving forces are generated. In the simplest case, this is the core lamination forming the stator.
  • the stator also has windings and end windings, which extend over the stator core lamination. However, here practically no forces or torques are generated, which are used to drive the rotor. If the bearing section is permitted to penetrate the active area of the stator, the drive shaft can be supported over a relatively large axial length. Therefore, otherwise the bearing section can be dimensioned to be somewhat weaker than with a shorter length.
  • the stator can then be moved closer to the compressor block, which further saves total height.
  • a bearing made in one piece will not be exposed to displacements between two or more parts.
  • the motor is a permanent magnet energized synchronous motor with inner rotor.
  • the stator comprises a stator lamination core formed by identically shaped and punched metal sheets, the stator lamination core having a central opening for adopting the rotor.
  • the inner surface of this central opening is formed by a number of pole teeth, which are connected to the radial outer metal sheet body by means of radial supports. Between the pole teeth groves are provided for adopting coil windings, which are wound around the supports to form so-called salient poles.
  • the use of such a motor substantially reduces the axial extension of the upper and lower winding heads in comparison with normally used asynchronous motors.
  • the stator can be moved closer to the compressor block, which further reduces the total height of the refrigerant compressor arrangement.
  • the rotor has a support part, on which several permanent magnets are located.
  • the fixing of the permanent magnets to the support part occurs by means of appropriate means, for example adhesives or special holders.
  • the rotor is supported very stably in the compressor block, which also provides a fixing for the stator, relatively small air gaps can be realised, so that the electric motor has a good efficiency.
  • the rotor is connected to the drive shaft via the support part.
  • the support part assumes a further task. It transmits a torque from the permanent magnets to the drive shaft.
  • the support part is adjacent to the bottom of the bearing section. This does not necessarily mean that the bearing section and the support part must touch each other. A small axial distance between the support part and the bearing section is even desirable, to prevent an additional friction. If, however, the support part is located relatively close to the bearing section, only a relatively small total height is required for fixing the rotor to the drive shaft.
  • a fixing section with which the support part is fixed on the drive shaft, is shorter in the axial direction than a magnet section, on which the permanent magnets are located. Also this is a measure for keeping the axial total height of the refrigerant compressor arrangement small.
  • the fixing section merely has to be able to transmit the torque to the drive shaft. Often, the total height required for this is smaller than the total height of the permanent magnets.
  • an oil pump opening at the lower end of the drive shaft is in connection with a bore in the drive shaft, said bore being inclined in relation to the rotation axis of the drive shaft.
  • the oil pump opening serves as inlet for the oil pump. It is immersed in an oil sump formed at the bottom of an enclosure, in which the refrigerant compressor arrangement is located.
  • a diagonal or inclined bore will be sufficient to transport oil from the oil sump to the spots, where the oil is needed. An oil pump as such is thus no longer needed, even though such an oil pump can still be used.
  • As the bore is inclined a certain centrifugal force will transport the oil upwards.
  • This transport occurs already with relatively small speeds, that is, already during the start, so that an earlier lubrication of the moving parts of the refrigerant compressor arrangement can be ensured. Due to the small total height, an operation with sufficient lubrication is also possible, if the refrigerant compressor arrangement is operated at low or variable speeds. This provides energetic advantages in relation to a pure on/off operation.
  • the oil pump opening is located in an attachment, which is adjacent to the lower end of the drive shaft.
  • the oil pump opening is not provided directly in the drive shaft, but in an additional attachment. This simplifies the manufacturing of the drive shaft.
  • the attachment forms part of the support part. This means that the attachment with the oil pump opening is handled together with the support part.
  • the attachment is made in one piece with the support element.
  • the attachment can additionally be used as stop when connecting the support part to the drive shaft.
  • the support element and the attachment are made as a common sintered part. If the support part and the attachment are made as one sintered piece almost no additional costs will occur in connection with the integration of the attachment in the support part.
  • the bore is connected to a helical groove on the outside of the drive shaft via a radial channel, which is covered by the bearing section at the area of the lower end of the bearing section. Oil from the bore can then reach the helical groove that is covered by the bearing section through the radial channel. The oil that is available in the helical groove is then transported further upwards by the rotation of the drive shaft in the bearing section, so that the oil can reach all parts, which have to be lubricated.
  • crank pin is located at the upper end of the drive shaft, eccentrically to the drive shaft, said crank pin surrounding an upwardly open hollow, which is connected to the bore.
  • This hollow serves as an oil reservoir, which is filled through the bore.
  • oil that is available in the oil reservoir will be slung out through the opening and sprayed inside an enclosure that surrounds the refrigerant compressor arrangement.
  • the crank pin can also have an opening in its wall, through which opening the oil reaches an intermediate space between the crank pin and the crank eye of the connecting rod.
  • the lower part of the bearing section has a reduced outer diameter.
  • Directional details, like “lower” refer to the normal mounting direction of the refrigerant compressor arrangement.
  • the bearing section In the lower area the bearing section has its largest distance to the crank pin, so that the forces generated by the crank pin when acted upon by the connecting rod are no longer too large.
  • a reduction of the wall thickness of the bearing section will cause no problems.
  • the reduction of the bearing section will leave more space for the rotor or the support part of the rotor, respectively.
  • FIG. 1 a longitudinal section through a refrigerant compressor arrangement
  • FIG. 2 a section of FIG. 1 with the rotor in a different rotation angle position
  • FIG. 3 a modified embodiment of the arrangement according to FIG. 2
  • FIG. 4 a third embodiment in the view according to FIG. 2 .
  • FIG. 1 shows a longitudinal section through a refrigerant compressor arrangement 1 .
  • the refrigerant compressor arrangement 1 comprises an enclosure 2 with an upper part 3 and a lower part 4 .
  • the upper part 3 comprises a flange 5 and the lower part 4 comprises a flange 6 .
  • the flanges 5 , 6 are connected to each other by welding, so that the enclosure 2 is hermetically closed.
  • a unit 7 with a motor 8 and a compressor unit 9 In the enclosure is located a unit 7 with a motor 8 and a compressor unit 9 .
  • the unit 7 is supported on the lower part 4 of the enclosure 2 by means of springs 10 , 11 .
  • the motor 8 has a stator 12 and a rotor 13 .
  • the stator 12 comprises a stator core lamination 14 , which is stacked of identically formed and punched metal sheets.
  • the stator core lamination 14 On the radial inside, the stator core lamination 14 has several pole teeth 15 , which again are formed by webs and salient poles on the inside of a central stator opening. In the grooves formed between the pole teeth 15 , windings 16 are located, each surrounding a web. Between the stator core lamination 14 and the windings 16 , isolating layers in the form of an upper end plate 17 and a lower end plate 18 are located.
  • the end plates 17 , 18 completely cover the axial end faces of the stator core lamination 14 as well the surfaces of the pole teeth 15 , except for the radial inner pole faces, which surround the central stator opening. In other words, the end plates 17 , 18 form a complete coating and electrical isolation of the groove surfaces.
  • the rotor 13 has several permanent magnets 19 , which are located on a metal support part 20 .
  • the permanent magnets 19 are fixed to the support part 20 by suitable means, for example adhesives or special holders.
  • the motor 8 is a permanent magnet energized synchronous motor with inner rotor.
  • the use of such a motor 8 ensures that, compared to previously used asynchronous motors, the axial extension of the parts of the windings 16 extending upwards and downwards from the stator core lamination 14 is substantially smaller. Thus, in the axial direction the motor 8 has a relatively small total height.
  • the motor 8 is located under a compressor block 21 .
  • the directional terms “up” and “down” refer to a usual mounting direction of the refrigerant compressor arrangement 1 .
  • the compressor unit 9 is located on the upper side of the compressor block 21 . It comprises a cylinder 22 , in which a piston 23 can reciprocate to increase or reduce a pressure chamber 24 .
  • a piston 23 can reciprocate to increase or reduce a pressure chamber 24 .
  • refrigerant gas is sucked in through a suction connection 25 , and during a reduction of the pressure chamber 24 the refrigerant gas is ejected through an outlet pipe 26 .
  • a valve plate 27 is provided, which is fitted on the front side of the cylinder 22 .
  • the valve plate 27 again is covered by a cylinder head cover 28 .
  • crank shaft 29 The driving of the piston 23 occurs via a crank shaft 29 , which engages a crank pin 30 , which is located at the upper side of a drive shaft 31 and eccentrically to the axis of the drive shaft 31 .
  • the drive shaft 31 is supported in the compressor block 21 .
  • the compressor block 21 has a bearing section 32 forming a radial bearing 33 and an axial bearing 34 .
  • the bearing section 32 penetrates the stator core lamination 14 of the stator 12 , that is, the active area of the stator 12 . Forces, which make the rotor 13 rotate, are practically only generated in this area.
  • the drive shaft 31 penetrates the bearing section 32 , that is, projects from the lower end of the bearing section 32 .
  • the drive shaft 31 is unrotatably connected to the rotor 13 .
  • the connection occurs via the support part 20 , which also carries the permanent magnets 19 .
  • the fixing of the support part 20 on the drive shaft 31 in the fixing section 36 can, for example, occur in that the support part 20 is shrunk or pressed onto the drive shaft. With a small gap, this support part 20 is adjacent to the lower end of the bearing section 32 .
  • the support part 20 forms a fixing section 36 , whose axial extension is smaller than the axial extension of the permanent magnets 19 . Also this makes it possible to keep the axial extension of the motor 8 , and thus also the total height of the refrigerant compressor arrangement 1 , small.
  • the lower end of the drive shaft 31 projects into an oil sump 37 (for reasons of clarity, the oil is not shown here).
  • the drive shaft 31 has an oil pump opening 38 , which is, as can be seen from FIG. 2 , connected to a bore 39 in the drive shaft 31 , which is inclined in relation to a rotation axis 40 , that is, encloses an angle together with the rotation axis 40 .
  • a radial channel 41 branches off, whose outside is covered by the bearing section 32 , and which ends in a helical groove 42 , which is provided at the circumferential wall of the drive shaft 31 and is covered in its full length by the bearing section 32 .
  • the helical groove supplies oil to the axial bearing 34 , so that all surfaces, at which the drive shaft 31 performs a movement in the compressor block 21 , are lubricated with oil.
  • the crank pin 30 has a hollow 43 with an upward opening 44 , the hollow being connected to the bore 39 via a channel 45 (partly seen in FIG. 2 ).
  • the hollow 43 in the crank pin 30 is filled with oil.
  • an opening 46 a share of the oil can reach an area between the connecting rod 29 and the crank pin 30 in order to lubricate this area.
  • a further share of the oil is slung through the opening 44 onto the inside of the upper part 3 of the enclosure 2 , from where it drops off to lubricate other parts of the unit 7 .
  • the lower end of the bearing section 32 has an area 47 with a reduced outer diameter.
  • the support part 20 may have a larger wall thickness. The bearing section 32 no longer has to adopt large forces here.
  • FIG. 3 shows a modified embodiment, in which same and functionally same elements have the same reference numbers.
  • the oil pump opening 38 is now located in an attachment 48 , which is fitted at the lower end of the drive shaft 31 and at the support part 20 .
  • Such an embodiment facilitates the manufacturing of the drive shaft 31 .
  • the suction function of the oil pump must no longer be considered.
  • it will be sufficient only to connect the attachment 48 to the support part 20 so that here no special measures have to be taken with regard to a connection to the drive shaft 31 .
  • attachment 48 is made in one piece with the support part 20 .
  • the support part is made of metal.
  • the combination of support part 20 and attachment 48 can be made as a sintered part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
US12/185,982 2007-08-16 2008-08-05 Refrigerant compressor arrangement Abandoned US20090068035A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007038432.9 2007-08-16
DE102007038432A DE102007038432A1 (de) 2007-08-16 2007-08-16 Kältemittelverdichtereinrichtung

Publications (1)

Publication Number Publication Date
US20090068035A1 true US20090068035A1 (en) 2009-03-12

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ID=40279430

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/185,982 Abandoned US20090068035A1 (en) 2007-08-16 2008-08-05 Refrigerant compressor arrangement

Country Status (4)

Country Link
US (1) US20090068035A1 (it)
CN (1) CN101368556B (it)
DE (1) DE102007038432A1 (it)
IT (1) IT1391039B1 (it)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102330655A (zh) * 2011-07-11 2012-01-25 加西贝拉压缩机有限公司 制冷压缩机的电机安装结构
WO2013114813A1 (ja) * 2012-01-31 2013-08-08 アルバック機工株式会社 ポンプ装置
AT17173U8 (de) * 2019-12-19 2021-09-15 Anhui meizhi compressor co ltd Hermetisch gekapselter Kältemittelverdichter

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056646A (en) * 1927-07-08 1936-10-06 Westinghouse Electric & Mfg Co Refrigerating apparatus
US2069767A (en) * 1932-12-23 1937-02-09 Gen Motors Corp Compressing apparatus
US2243466A (en) * 1940-03-25 1941-05-27 Gen Motors Corp Refrigerating apparatus
US3187994A (en) * 1962-09-04 1965-06-08 Danfoss Ved Ing M Clausen Hermetically sealed motor compressors particularly suitable for small refrigerating machines
US4365941A (en) * 1979-05-09 1982-12-28 Hitachi, Ltd. Scroll compressor provided with means for pressing an orbiting scroll member against a stationary scroll member and self-cooling means
US5090876A (en) * 1989-02-28 1992-02-25 Seiko Epson Corporation Scroll type fluid handling machine
US5957671A (en) * 1995-05-08 1999-09-28 Danfoss Compressors Gmbh Refrigerant compressor with an electric motor having an insulation film
US6369480B1 (en) * 1996-02-23 2002-04-09 Matsushita Electric Industrial Co., Ltd. Compressor using a motor
US20040191094A1 (en) * 2003-02-12 2004-09-30 Takeshi Kojima Electric compressor
US20050089416A1 (en) * 2003-10-27 2005-04-28 Samsung Gwang Ju Electronics Co., Ltd. Hermetic compressor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD226627A1 (de) 1984-09-20 1985-08-28 Dkk Scharfenstein Veb Lager fuer hermetische kaeltemittelverdichter mit oelumlaufkuehlung

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056646A (en) * 1927-07-08 1936-10-06 Westinghouse Electric & Mfg Co Refrigerating apparatus
US2069767A (en) * 1932-12-23 1937-02-09 Gen Motors Corp Compressing apparatus
US2243466A (en) * 1940-03-25 1941-05-27 Gen Motors Corp Refrigerating apparatus
US3187994A (en) * 1962-09-04 1965-06-08 Danfoss Ved Ing M Clausen Hermetically sealed motor compressors particularly suitable for small refrigerating machines
US4365941A (en) * 1979-05-09 1982-12-28 Hitachi, Ltd. Scroll compressor provided with means for pressing an orbiting scroll member against a stationary scroll member and self-cooling means
US5090876A (en) * 1989-02-28 1992-02-25 Seiko Epson Corporation Scroll type fluid handling machine
US5957671A (en) * 1995-05-08 1999-09-28 Danfoss Compressors Gmbh Refrigerant compressor with an electric motor having an insulation film
US6369480B1 (en) * 1996-02-23 2002-04-09 Matsushita Electric Industrial Co., Ltd. Compressor using a motor
US20040191094A1 (en) * 2003-02-12 2004-09-30 Takeshi Kojima Electric compressor
US20050089416A1 (en) * 2003-10-27 2005-04-28 Samsung Gwang Ju Electronics Co., Ltd. Hermetic compressor

Also Published As

Publication number Publication date
ITTO20080621A1 (it) 2009-02-17
IT1391039B1 (it) 2011-10-27
CN101368556A (zh) 2009-02-18
CN101368556B (zh) 2011-10-05
DE102007038432A1 (de) 2009-02-19

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Legal Events

Date Code Title Description
AS Assignment

Owner name: DANFOSS COMPRESSORS GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:VALBJOERN, JESPER;HANSEN, KRISTOFFER RIEMANN;MADSEN, ANDERS JAKOB;REEL/FRAME:021905/0471;SIGNING DATES FROM 20081007 TO 20081020

AS Assignment

Owner name: SECOP GMBH (FORMERLY KNOWN AS DANFOSS HOUSEHOLD CO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DANFOSS FLENSBURG GMBH (FORMERLY KNOWN AS DANFOSS COMPRESSORS GMBH);REEL/FRAME:026100/0634

Effective date: 20110406

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION