EP1574715A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

Info

Publication number
EP1574715A1
EP1574715A1 EP05012629A EP05012629A EP1574715A1 EP 1574715 A1 EP1574715 A1 EP 1574715A1 EP 05012629 A EP05012629 A EP 05012629A EP 05012629 A EP05012629 A EP 05012629A EP 1574715 A1 EP1574715 A1 EP 1574715A1
Authority
EP
European Patent Office
Prior art keywords
scroll
frame
pressure
value
oscillating
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.)
Granted
Application number
EP05012629A
Other languages
English (en)
French (fr)
Other versions
EP1574715B1 (de
Inventor
Kiyoharu Ikeda
Yoshihide Ogawa
Takeshi Fushiki
Teruhiko Nishiki
Takashi Sebata
Fumiaki Sano
Shin Sekiya
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 Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Electric Corp filed Critical Mitsubishi Electric Corp
Priority claimed from EP01904326A external-priority patent/EP1359323B1/de
Publication of EP1574715A1 publication Critical patent/EP1574715A1/de
Application granted granted Critical
Publication of EP1574715B1 publication Critical patent/EP1574715B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C18/02—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

Definitions

  • the compliant frame 3 has two upper and lower cylindrical surfaces 3d and 3e in its outer circumferential portion.
  • the cylindrical surfaces 3d and 3e are supported in the radial direction of the scroll compressor by cylindrical surfaces 15a and 15b provided in the inner circumferential portion of the guide frame 15, respectively.
  • a main bearing 3c and an auxiliary main bearing 3h for supporting a main shaft 4 in the radial direction of the scroll compressor are formed in the center portions of the compliant frame 3.
  • the main shaft 4 is driven to rotate by a motor 7.
  • a frame space 15f is defined by sealing materials 16a and 16b disposed on cylindrical surfaces 15c and 15d, respectively.
  • a sucked refrigerant of low pressure enters the compression chamber 1d through the suction pipe 10a.
  • the compression chamber 1d is defined by the plate-like scroll teeth of the fixed scroll 1 and the plate-like scroll teeth of the oscillating scroll 2.
  • the oscillating scroll 2 driven by the motor 7 makes an eccentric turning motion while reducing the volume of the compression chamber 1d.
  • the sucked refrigerant becomes high in pressure.
  • the sucked refrigerant is discharged into the closed vessel 10 through the discharge port 1f of the fixed scroll 1.
  • the refrigerating machine oil 10e overcomes the force loaded by the intermediate pressure regulating spring 3m disposed in the regulating valve receiving space 3p.
  • the refrigerating machine oil 10e pushes the intermediate pressure regulating valve 3i. Accordingly, the refrigerating machine oil 10e is introduced into the suction pressure atmosphere space 1g and sucked into the compression chamber 1d together with the low pressure refrigerant gas.
  • the tooth tip contact force Ftip or the thrust contact force Fth can be adjusted desirably by adjusting the pressure Pm1 in the boss portion outside space or the pressure Pm2 in the frame space.
  • positive values must be always ensured for the two forces in order that the compressor performs out a normal compressing operation. Ftip>0 Fth>0
  • the sealing materials usually constituted by a U-ring for preventing discharge pressure gas from entering the frame space 15f and another U-ring for preventing gas from leaking from the frame space 15f to the suction pressure atmosphere are provided in the direction shown in Fig. 8.
  • Teflon or the like is often used as the material of the U-rings.
  • the sealing materials are formed so as to prevent discharge pressure gas from entering the frame space 15f.
  • the sealing materials cannot prevent the flow reverse to that of the discharge pressure gas.
  • the refrigerant gas in the frame space 15f leaks out into the closed space so that the pressure Pm2 in the frame space does not increase.
  • the force required to move the compliant frame 3 toward the compression chamber becomes insufficient. In other words, it takes a long time to start a normal compressing operation.
  • the compliant frame 3 and the oscillating scroll 2 moving in the axial direction of the compressor in contact with the compliant frame 3 fluctuate in the clearance of the axial relief amount.
  • damage, seizing, or the like is caused to the bearings by the occurrence of one-s ided bearing of the bearings.
  • US-A-6 135 739 discloses a scroll compressor in accordance with the preamble of claim 1.
  • a scroll compressor which is provided in a closed vessel and which comprises: a fixed scroll and an oscillating scroll respectively having plate-like scroll teeth engaging with each other so as to form a compression chamber therebetween; a compliant frame for supporting the oscillating scroll in an axial direction of the scroll compressor while supporting a main shaft in a radial direction of the scroll compressor for driving the oscillating scroll, the compliant frame being displaceable in the axial direction; and a guide frame for supporting the compliant frame in the radial direction, the oscillating scroll being made movable in the axial direction due to movement of the compliant frame in the axial direction relative to the guide frame, refrigerant gas undergoing compression is extracted from the compression chamber and introduced into a closed frame space formed by disposing two sealing materials on cylindrical surfaces or flat surfaces formed by the compliant frame and the guide frame, and pressure Pm2 (MPa) in the frame space is set to fall in a range of not less than 1.2 times and not more than 2 times the suction pressure Ps (MPa) of the compressor.
  • each sealing material is formed into an O-ring, the cost of the sealing material can be reduced. Further, even during starting of the compressor, the compliant frame and the oscillating scroll move toward the compression chamber quickly without leaking the pressure of the frame space into the closed vessel. Thus, a normal compressing operation can be started. Accordingly, the scroll compressor is obtained which is low in cost and high in reliability.
  • the frame space 15f is filled with intermediate pressure refrigerant gas supplied continuously or intermittently through an extraction hole 2 j and a communication passageway 3s.
  • the pressure Pm2 in the frame space is set in accordance with the position of the compressor chamber 1d with which the extraction hole 2j communicates, so that the value ⁇ shown in the express ion (3) becomes about 1.6.
  • tooth tip contact force Ftip does not assume a negative value.
  • the oscillating scroll 2 and the fixed scroll 1 are prevented from separating from each other so that a normal compressing operation can be ensured.
  • the thrust contact force Fth or the thrust sliding loss can be reduced as described previously in connection with the conventional apparatus.
  • the value ⁇ is set to be too large, that is, if the pressure Pm1 of the boss portion outside space 2h is set to be too high, the thrust contact force Fth assumes a negative value.
  • the oscillating scroll 2 and the compliant frame 3 are separated from each other, or the differential pressure ⁇ P for feeding oil to the oscillating bearing 2c and the main bearing 3c cannot be ensured.
  • Fig. 2 shows an ordinary running temperature range quarantined by the compressor. Oil feeding has to be ensured in such a wide range.
  • the condition that makes it difficult for the compressor to feed oil appears to be at a running point (low compression ratio) at which the difference between condensation temperature CT and evaporation temperature ET is minimum, that is, the difference between discharge pressure Pd and suction pressure Ps is minimum.
  • this running point is a right lower point in the running temperature range, and the ratio CT/ET is 30/10°C.
  • the difference min(Pd-Ps) between the discharge pressure Pd and the suction pressure Ps at this point varies in accordance with the refrigerant to be used.
  • the points are summarized in Fig. 9.
  • a differential pressure head for feeding oil to the oscillating bearing 2 and the main bearing 3c becomes the differential pressure ⁇ P between the closed vessel pressure (i.e., discharge pressure) Pd and the boss portion outside space pressure Pm1 as shown in the expression (2).
  • the value ⁇ has to be set smaller than 0.51 ( ⁇ ⁇ 0.51) when R22 is used as a working refrigerant, and the value a has to be set smaller than 0.8 ( ⁇ 0.8) when R410A is used as a working refrigerant. Otherwise, an area where no oil is fed appears in the running pressure range of the compressor. Therefore, the value ⁇ has to be set not larger than any one of the above-mentioned values.
  • Fig. 3 shows the rated performance ratio ⁇ when the value ⁇ is varied with R407C as a working refrigerant.
  • the rated performance ratio is expressed by the performance ratio on the assumption that the performance MAX value is 100%.
  • the effect of relieving the thrust contact force Fth cannot be obtained sufficiently, and there is a tendency that the thrust sliding loss increases so that the performance deteriorates gradually.
  • the value ⁇ is increased gradually, the effect of relieving the thrust sliding loss is exhibited so that the performance is improved.
  • the performance reaches a peak (100%) when the value ⁇ is about 0.3. If the value ⁇ is increased further, the thrust sliding loss becomes smaller. However, the thrust contact force Fth becomes somewhat insufficient.
  • Fig. 4 shows the correlation between the value ⁇ and the rated performance ratio when R410A i.e., a high pressure working refrigerant is used. In Fig. 4, the correlation in the above-mentioned case of R407C is also shown.
  • Fig. 5 shows the rated performance ratio when the value ⁇ is varied in the scroll compressor of this embodiment.
  • the rated performance ratio is expressed in terms of the performance ratio by taking the performance MAX value as 100% in the same manner as described above.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP05012629A 2001-02-07 2001-02-07 Spiralverdichter Expired - Lifetime EP1574715B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP01904326A EP1359323B1 (de) 2001-02-07 2001-02-07 Spiralverdichter

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP01904326A Division EP1359323B1 (de) 2001-02-07 2001-02-07 Spiralverdichter

Publications (2)

Publication Number Publication Date
EP1574715A1 true EP1574715A1 (de) 2005-09-14
EP1574715B1 EP1574715B1 (de) 2006-09-27

Family

ID=34814165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05012629A Expired - Lifetime EP1574715B1 (de) 2001-02-07 2001-02-07 Spiralverdichter

Country Status (1)

Country Link
EP (1) EP1574715B1 (de)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5277563A (en) * 1992-08-10 1994-01-11 Industrial Technology Research Institute Scroll compressor with axial sealing apparatus
EP1002953A1 (de) * 1998-11-20 2000-05-24 Mitsubishi Denki Kabushiki Kaisha Spiralverdichter

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5277563A (en) * 1992-08-10 1994-01-11 Industrial Technology Research Institute Scroll compressor with axial sealing apparatus
US6135739A (en) * 1997-10-01 2000-10-24 Mitsubishi Denki Kabushiki Kaisha Scroll compressor
EP1002953A1 (de) * 1998-11-20 2000-05-24 Mitsubishi Denki Kabushiki Kaisha Spiralverdichter

Also Published As

Publication number Publication date
EP1574715B1 (de) 2006-09-27

Similar Documents

Publication Publication Date Title
JP4440564B2 (ja) スクロール圧縮機
US6389837B1 (en) Scroll compressor
US11022120B2 (en) Scroll compressor with first and second compression chambers having first and second discharge start points
US6533561B1 (en) Scroll type compressor
KR100540251B1 (ko) 스크롤 압축기
KR100463283B1 (ko) 스크롤형 압축기
US20080304994A1 (en) Scroll Fluid Machine
EP1359323B1 (de) Spiralverdichter
US5562435A (en) Structure for preventing axial leakage in a scroll compressor
US7806672B2 (en) Rotary compressor with pressing mechanism and adjusting mechanism to vary a magnitude of a load in response to a pressure difference between the suction fluid and discharge fluid
CA2292330C (en) Scroll compressor having axial compliance valve
JP4930022B2 (ja) 流体機械
US6679690B2 (en) Scroll compressor including guide frame and compliant frame
EP0400951A1 (de) Axialdichtungseinrichtung für Spiralverdichter
EP1574715B1 (de) Spiralverdichter
WO2014103136A1 (ja) スクロール圧縮機
JP2008309078A (ja) スクロール圧縮機
JPH09158849A (ja) スクロール式圧縮機
JP7262013B2 (ja) スクロール圧縮機
KR20010014606A (ko) 용적형 유체 기계
US7641456B2 (en) Scroll compressor with back pressure chamber cavity for assisting in start-up
CN104832434B (zh) 旋转式压缩机及具有其的制冷系统装置
JP2006009640A (ja) スクロール圧縮機
JP2019019768A (ja) スクロール圧縮機
JP2009052463A (ja) スクロール圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AC Divisional application: reference to earlier application

Ref document number: 1359323

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): ES GB IT

17P Request for examination filed

Effective date: 20050822

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MITSUBISHI DENKI KABUSHIKI KAISHA

AKX Designation fees paid

Designated state(s): ES GB IT

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 1359323

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): ES GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060927

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070107

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070628

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20080125

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100207

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20141217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150207

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20170201

Year of fee payment: 17

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150207

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20170221

Year of fee payment: 17

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20180104

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180207

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180207

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180207