EP1348077B1 - Kältemittelverdichter - Google Patents

Kältemittelverdichter Download PDF

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Publication number
EP1348077B1
EP1348077B1 EP01272665A EP01272665A EP1348077B1 EP 1348077 B1 EP1348077 B1 EP 1348077B1 EP 01272665 A EP01272665 A EP 01272665A EP 01272665 A EP01272665 A EP 01272665A EP 1348077 B1 EP1348077 B1 EP 1348077B1
Authority
EP
European Patent Office
Prior art keywords
radial bearing
rotor
refrigerant compressor
bearing
compressor according
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.)
Expired - Lifetime
Application number
EP01272665A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1348077A1 (de
Inventor
Rolf Dieterich
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP1348077A1 publication Critical patent/EP1348077A1/de
Application granted granted Critical
Publication of EP1348077B1 publication Critical patent/EP1348077B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the invention relates to a refrigerant compressor, comprising an overall housing, an electric motor arranged in the overall housing with a stator and a rotor seated on a drive shaft, and a screw compressor arranged in the overall housing, a compressor screw of which is seated on the drive shaft and which is connected by a first radial bearing between the Rotor and the compressor screw and a second, arranged on a side opposite the first radial bearing side of the compressor screw radial bearing is rotatably mounted in the overall housing.
  • a compressor is from each one of the JP-A-54154811 or JP-A-54115409 known.
  • the rotor In other known refrigerant compressors, the rotor usually sits on a starting from the first radial bearing on a side opposite the compressor screw side cantilevered portion of the drive shaft, which means that a lot of effort must be operated to not overly large on this freely overhanging portion of the drive shaft To act on moments that cause a gap between the rotor and the stator is reduced to zero and thus the rotor touches the stator, in particular when asymmetric forces on the rotor.
  • the invention is therefore an object of the invention to improve a refrigerant compressor of the generic type such that the risk of contact of the stator by the rotor no longer occurs.
  • the advantage of the solution according to the invention is the fact that the provision of a third radial bearing for the drive shaft per se would have an overdetermination in the storage of the drive shaft result, since the drive shaft due to two radial bearings, namely the both sides of the compressor screw arranged radial bearings, in terms of their orientation is clearly determined relative to the overall housing, so that, assuming that the third radial bearing can not be arranged without misalignment to the other two radial bearings, always the radial bearings are acted upon by the misalignment forces caused by the misalignment.
  • a lying between the first radial bearing and the rotor intermediate portion is flexurally elastic, since this can be formed substantially immediately adjacent to the first radial bearing intermediate portion in a simple manner so that it has the necessary bending elasticity to compensate for misalignment having the third radial bearing.
  • a sizing rule of the outer diameter of the drive section such that it still has the required bending elasticity results from the fact that an outer diameter of at least a portion of the drive section is less than one fifth of the rotor length, more preferably less than one sixth of the rotor length.
  • the solution according to the invention makes it possible, in particular, to use long rotors and thus inexpensive electric motors, with rotor rotors preferably being equal to or larger than 1.7 times the rotor outer diameter, even better than or equal to twice the rotor outer diameter in such long rotors.
  • the third radial bearing is held by a cover of the overall housing. This is a very easy way to realize a bearing receptacle for the third radial bearing and so to integrate into the overall housing, that the structure of the overall housing is structurally easy to implement.
  • the drive shaft is provided with a leading to the third radial bearing lubricant channel.
  • the lubricant channel is formed so that it leads to the first and the second radial bearing.
  • the structure of the overall housing a variety of ways are conceivable. For example, it would be conceivable to divide the overall housing so that the screw compressor and the electric motor are arranged in separate housing sections.
  • the overall housing has a central portion in which the compressor screw and the stator are arranged with the rotor of the electric motor and which is closed on the side of the electric motor by a housing cover and the housing cover opposite completed by an attachable housing end is.
  • a compressor housing of the screw compressor is arranged in the central portion, so that the compressor housing can be positioned even with great precision relative to the central portion.
  • Such a solution is particularly favorable when the compressor housing is integrally formed in the central portion.
  • an advantageous solution provides that a bearing receptacle of the first radial bearing is arranged in the central portion.
  • this bearing receptacle is integrally formed in the central portion.
  • FIG. 1 illustrated embodiment of a designated as a whole with 10 refrigerant compressor according to the invention comprises an overall housing 12, which is formed from a central portion 14, disposed on one side 16 of the central portion 14 housing cover 18 and arranged on an opposite side 20 of the central portion 14 housing end portion 22.
  • a generally designated 24 screw compressor is arranged, which usually comprises two compressor screws, of which a compressor screw 26 can be seen, which in turn are arranged in a rotary compressor housing 28, wherein the compressor housing 28 in one piece in the central portion 14th is formed and extends from an inlet 30 to an outlet 32.
  • the compressor screw 26 sits in turn on a designated as a whole by 34 drive shaft which extends with its longitudinal axis 36 coaxial with the compressor screw 26 and on both sides beyond this, via an inlet-side end 38 of the compressor screw 26 going out with a first bearing portion 40 and a outlet side end 42 of the compressor screw 26 going out with a second bearing portion 44th
  • the first bearing portion 40 of the drive shaft 34 is rotatably supported by a first radial bearing 50 in the central portion 14, wherein the first radial bearing 50 is seated in a first bearing seat 52, which in turn is integrally formed in the central portion 14 and forms an inlet-side firing of the compressor housing 28 ,
  • the second bearing portion 44 is rotatably supported by a second radial bearing 54, wherein the second radial bearing 54 is disposed in a second bearing receptacle 56, which in turn is provided in the housing end portion 22 and part of an outlet-side closure body 58 of the compressor housing 28, which also has an outlet channel 60th having.
  • the outlet-side launcher 58 is connected via the fixation of the housing end portion 22 fixed to the central portion 14 and the compressor housing 28, wherein the central portion 14 and the housing end portion 22 are separated by a common parting plane 62, which at the same time a parting plane 62 between the compressor housing 28th in the central portion 14 and the outlet-side closure body 58 in the housing end portion 22 represents.
  • the drive shaft 34 still extends beyond the first bearing portion 40 on an opposite side of the compressor screw 26 and forms a drive portion 64 which in turn adjoins an immediately adjacent to the first bearing portion 40 intermediate portion 66 and subsequent to the intermediate portion 66, a rotor portion 68 and Finally, following the rotor portion 68, a third bearing portion 70 which is supported by a third radial bearing 72 in a third bearing receptacle 74, which in turn is integrally formed on the housing cover 18 and is fixed on the housing cover 18 to the central portion 14.
  • the rotor 80 has in this case in the direction parallel to the axis 36 of the drive shaft 34 has a rotor length RL and radially to the axis 36, a rotor inner diameter RI, which corresponds to the outer diameter of the rotor portion 68.
  • the rotor has a rotor length RL which is at least 1.7 times, preferably more than twice, the rotor outer diameter RA.
  • the rotor inner diameter RI is less than one-fifth, more preferably less than one-sixth of the rotor length RL.
  • the drive shaft 34 is formed so that the third bearing portion 70 has an outer diameter smaller than an outer diameter of the rotor portion 68 and the outer diameter of the rotor portion 68 is smaller than an outer diameter of the intermediate portion 66 and this in turn approximately in its outer diameter of the first bearing portion 40th
  • the inner diameter of the first radial bearing 50 can be made relatively smaller, which allows the use of a radial bearing with greater load rating (and thus longer life) or a shorter and cheaper bearing with comparable load rating.
  • the outer diameter of the rotor portion 68 and the outer diameter of the intermediate portion 66 are equal, so that preferably the outer diameter of the intermediate portion 66 is also smaller than one-fifth, even better smaller than one-sixth, the rotor length RL.
  • the orientation of the drive shaft 34 is due to the need for precise storage of the compressor screw 26 in the compressor housing 28 predetermined by the first radial bearing 50 and the second radial bearing 54, which are designed as rolling bearings, wherein the second radial bearing 54 is additionally also designed as a thrust bearing.
  • the entire drive shaft 34 is defined by the first radial bearing 50 and the second radial bearing 54 in their orientation relative to the overall housing 12 and thus also to the central portion 14 thereof defined.
  • the rotor 80 of the electric motor 82 has a significant weight and also with the electric motor 82, in particular when starting within the stator 84, 36 asymmetric forces can be exposed to the axis acts on the drive portion 64, in particular the rotor portion 68 a significant bending moment, which causes a gap S between the rotor 80 and the stator 84 can not be maintained at large forces and thus the rotor 80 to the stator 84 touch could.
  • the third designed as a rolling bearing radial bearing 72 is provided, which, however, represents a geometric overdetermination of the drive shaft 34 with respect to the alignment of the same by the radial bearings 50 and 54, in particular there is always such a third radial bearing 72 with misalignment relative to the other radial bearings 50 and 54 is arranged, even if these misalignment are also low.
  • the drive portion 64 in particular the intermediate portion 66 of the same, is formed so that it is flexible transversely to the axis 36, whereby overdetermination of the orientation of the drive shaft 34 by a total of three radial bearings 50, 54 and 72 can be avoided.
  • the intermediate portion 66 is preferably dimensioned so that it is still able to transmit the entire, applied by the rotor 80 torque, but with respect to transversely to the axis 36 directed bending moments - yielding that this flexurally elastic compliance of the intermediate portion 66 is sufficient in order to compensate for the occurring misalignment of the third radial bearing 72 relative to the first and second radial bearings 50, 54 by a movement transverse to the axis 34, and to avoid large constraining forces.
  • the bending elasticity of the intermediate portion 66 can be most easily determined by a diameter thereof, which is preferably smaller than one fifth, even better smaller than one sixth of the rotor length RL, - in the inventive solution is the possibility of rotors 80 with a large rotor length RL use, since the bending moments occurring by this rotor length RL and the bending moments at start of the electric motor by the third, the drive shaft 34 additionally supporting Radial bearing 72 are intercepted and thus, the gap S between the rotor 80 and the stator 84 can be kept low, without the risk that the rotor 80 and the stator 84 touch.
  • the present invention allows rotors 80 having a rotor length RL greater than 1.7 times the rotor outer diameter RA, more preferably greater than 2 times, more preferably greater than 2.1 times the rotor outer diameter RA.
  • the drive shaft 34 is preferably provided with a continuous lubricant channel 90 which is formed so that it via the respective bearing portions 40, 44 and 70, the respective radial bearings 50, 54 and 72nd supplied with lubricant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
EP01272665A 2001-01-05 2001-12-21 Kältemittelverdichter Expired - Lifetime EP1348077B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10101016A DE10101016A1 (de) 2001-01-05 2001-01-05 Kältemittelverdichter
DE10101016 2001-01-05
PCT/EP2001/015247 WO2002053917A1 (de) 2001-01-05 2001-12-21 Kältemittelverdichter

Publications (2)

Publication Number Publication Date
EP1348077A1 EP1348077A1 (de) 2003-10-01
EP1348077B1 true EP1348077B1 (de) 2009-02-11

Family

ID=7670261

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01272665A Expired - Lifetime EP1348077B1 (de) 2001-01-05 2001-12-21 Kältemittelverdichter

Country Status (8)

Country Link
US (2) US6666661B2 (zh)
EP (1) EP1348077B1 (zh)
CN (1) CN1235004C (zh)
AT (1) ATE422617T1 (zh)
DE (2) DE10101016A1 (zh)
DK (1) DK1348077T3 (zh)
ES (1) ES2319862T3 (zh)
WO (1) WO2002053917A1 (zh)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004055360B4 (de) * 2004-11-08 2013-09-12 Atlas Copco Airpower N.V. Motor-Verdichter-Anordnung
DE102004060596A1 (de) 2004-12-02 2006-06-22 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
DE102006035783A1 (de) * 2006-08-01 2008-02-07 Grasso Gmbh Refrigeration Technology Schraubenverdichter
TWM371791U (en) * 2009-05-27 2010-01-01 Hanbell Precise Machinery Co Ltd Screw compressor
US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
DE102011001394B4 (de) 2011-03-18 2015-04-16 Halla Visteon Climate Control Corporation 95 Elektrisch angetriebener Kältemittelverdichter
DE102012102346A1 (de) * 2012-03-20 2013-09-26 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
CN104675700B (zh) * 2013-10-31 2017-04-19 大金工业株式会社 螺杆压缩机
DE102013020535A1 (de) * 2013-12-12 2015-06-18 Gea Refrigeration Germany Gmbh Verdichter
JP6571422B2 (ja) * 2015-07-03 2019-09-04 株式会社神戸製鋼所 パッケージ型空冷式スクリュー圧縮機
US10830239B2 (en) 2015-08-11 2020-11-10 Carrier Corporation Refrigeration compressor fittings
RU2737072C2 (ru) 2015-08-11 2020-11-24 Кэрриер Корпорейшн Компрессор, способ его использования и система паровой компрессии
WO2017058369A1 (en) 2015-10-02 2017-04-06 Carrier Corporation Screw compressor resonator arrays
DE102017100537A1 (de) * 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Verfahren zum Herstellen eines Gehäuses eines Schraubenkompressors

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54115409A (en) * 1978-03-01 1979-09-08 Hitachi Ltd Sealed type screw compressor
JPS54154811A (en) * 1978-05-26 1979-12-06 Hitachi Ltd Screw compressor
US4957417A (en) * 1989-07-14 1990-09-18 Kabushiki Kaisha Kobe Seiko Sho Vertical oilless screw vacuum pump
JPH04159480A (ja) * 1990-10-19 1992-06-02 Hitachi Ltd スクリュー圧縮機
JPH06330874A (ja) * 1993-05-26 1994-11-29 Hitachi Ltd スクリュー圧縮機
JPH07317684A (ja) * 1994-05-25 1995-12-05 Hitachi Ltd 密閉形電動圧縮機および冷却装置
DE19845993A1 (de) * 1998-10-06 2000-04-20 Bitzer Kuehlmaschinenbau Gmbh Schraubenverdichter
JP2001227486A (ja) * 2000-02-17 2001-08-24 Daikin Ind Ltd スクリュー圧縮機
JP2001317480A (ja) * 2000-04-28 2001-11-16 Hitachi Ltd スクリュー圧縮機

Also Published As

Publication number Publication date
ES2319862T3 (es) 2009-05-14
DE50114709D1 (de) 2009-03-26
WO2002053917A1 (de) 2002-07-11
US20040086410A1 (en) 2004-05-06
DE10101016A1 (de) 2002-07-25
ATE422617T1 (de) 2009-02-15
DK1348077T3 (da) 2009-04-14
EP1348077A1 (de) 2003-10-01
CN1235004C (zh) 2006-01-04
US6848891B2 (en) 2005-02-01
US6666661B2 (en) 2003-12-23
CN1406318A (zh) 2003-03-26
US20030049146A1 (en) 2003-03-13

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