EP0828079A2 - Compresseur du type Lysholm - Google Patents

Compresseur du type Lysholm Download PDF

Info

Publication number
EP0828079A2
EP0828079A2 EP97306761A EP97306761A EP0828079A2 EP 0828079 A2 EP0828079 A2 EP 0828079A2 EP 97306761 A EP97306761 A EP 97306761A EP 97306761 A EP97306761 A EP 97306761A EP 0828079 A2 EP0828079 A2 EP 0828079A2
Authority
EP
European Patent Office
Prior art keywords
casing
cusps
cusp
silencer chamber
suction port
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
EP97306761A
Other languages
German (de)
English (en)
Other versions
EP0828079A3 (fr
EP0828079B1 (fr
Inventor
Nobuo Takei
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.)
IHI Corp
Original Assignee
Ishikawajima Harima Heavy Industries Co 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 Ishikawajima Harima Heavy Industries Co Ltd filed Critical Ishikawajima Harima Heavy Industries Co Ltd
Publication of EP0828079A2 publication Critical patent/EP0828079A2/fr
Publication of EP0828079A3 publication Critical patent/EP0828079A3/fr
Application granted granted Critical
Publication of EP0828079B1 publication Critical patent/EP0828079B1/fr
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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • 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 present invention relates to Lysholm compressors which are used, for example, for superchargers in automotive engines and more particularly to casing structures for such compressors. More specifically, the invention relates to a casing structure for a Lysholm compressor which is adapted to accommodate intermeshing male and female rotors and which comprises two part-cylindrical walls which constitute a casing and merge together at two cusps which project inwardly towards one another, a suction port at one axial end of the casing and a discharge port at the other axial end of the casing.
  • Fig. 1 is a schematic perspective view of a known Lysholm compressor of the type referred to above, which comprises parallel intermeshing male and female rotors 1 and 2 rotatably accommodated in an accommodation space 7 within a casing 3.
  • the rotors 1 and 2 are counter-rotated in the directions of the arrows to suck air 5 into the space 7 through a suction or inlet port 4 at one axial end of the casing 3.
  • the air 5 is compressed by the rotors 1 and 2 and is discharged through a discharge port 6 at the other axial end of the casing 3 adjacent to the intermeshing portions 8 of the rotors 1 and 2.
  • the casing 3 comprises part-cylindrical walls 9a and 9b which are of substantially uniform thickness and which surround the majority of the peripheries of the rotors 1 and 2 except for the intermeshing portions 8.
  • the casing 3 further comprises a pair of opposed cusps 10 and 11 which project inwardly from the walls 9a and 9b towards the intermeshing portions 8 of the rotors 1 and 2.
  • the designed ports are not very effective at suppressing the noise. More specifically, the cusps 10 and 11 of the casing 3 have low stiffness and tend to cause vibration of the walls, thereby generating noise; such noise due to vibration of the walls may not be easily suppressed merely by specially designed ports.
  • the compressor described above when used, for example, as a supercharger for an integral combustion engine of a vehicle and noise suppressor means, such as a silencer or resonator, are provided in the piping connected to the suction and discharge ports 4 and 6, it is difficult to arrange this piping with the noise suppressor means in association with other equipment and machinery in the vehicle. Moreover, the arrangement of the noise suppressor means remote from the compressor impairs the noise-suppressing effect.
  • a casing structure for a Lysholm compressor of the type referred to above is characterised in that a silencer chamber is defined between one of the cusps and a first outer wall portion, which is situated outside the said one cusp and is integral with the casing, and has an opening in communication with the suction port.
  • the casing structure is characterised in that a silencer chamber is defined between one of the cusps and a second outer wall portion which is situated outside the said one cusp and is integral with the casing and has an opening in communication with the discharge port.
  • a casing structure in accordance with the present invention may have a silencer chamber defined between a respective one of the cusps and an associated outer wall portion situated outside the cusp and integral with the casing and having an opening in communication with either the suction port or the discharge port. Accordingly to a further aspect of the present invention the noise suppression is further enhanced if two such silencer chambers are provided communicating with the suction port and the discharge, respectively.
  • the invention relates also to a Lysholm compressor comprising male and female rotors which intermesh at a region and/or are rotatably accommodated within a casing structure of the type defined above.
  • the Lysholm compressor shown in Figs. 4 and 5 comprises male and female rotors 1 and 2 and a casing 3 for rotatably accommodating the rotors 1 and 2.
  • the casing 3 comprises two part-cylindrical walls 9a and 9b which are of substantially uniform thickness and surround the majority of the rotors 1 and 2 except for their intermeshing portions 8.
  • the part-cylindrical walls 9a and 9b merge at a pair of opposed cusps 10 and 11 which extend inwardly towards the intermeshing portions 8 of the rotors 1 and 2.
  • the casing 3 is provided at one axial end with a suction port 4 and at the other axial end with a discharge port 6 adjacent the intermeshing portions 8 of the rotors 1 and 2.
  • a stagnation space constituting a suction-side silencer chamber 13 is defined by the cusp 10 and the adjacent portions of the part-cylindrical walls and an outer wall portion 12 outside the cusp 10 and integral with the casing 3.
  • the silencer chamber 13 has a suction-side opening 14 in communication with the suction port 4.
  • the shape, size and other details of the silencer chamber 13 and also of the opening 14 may be freely selected.
  • rotation of the rotors 1 and 2 causes the air 5 induced through the suction port 4 to pass through the accommodation space 7 in the casing 3 whilst being compressed by the rotors 1 and 2, and the compressed air is discharged through the discharge port 6 at the other end of the casing 3 adjacent to the intermeshing portions 8 of the rotors.
  • any noise due to pressure fluctuations of the air 5 sucked through the port 4 can be effectively suppressed due to the presence of the silencer chamber 13.
  • the noise-suppressing effect is maximised since the silencer chamber 13 is adjacent to the source of noise generation by the compressor.
  • the cusp 10 is reinforced and thus stiffened by the presence of the outer wall portion 12, so that any vibration of the cusp 10 is suppressed, thereby suppressing the generation of noise by vibration.
  • Figs. 6 and 7 illustrate a further embodiment of the present invention in which a stagnation space constituting a discharge-side silencer chamber 16 is defined by the other cusp 11 and adjacent portions of the part-cylindrical walls and an outer wall portion 15 outside the cusp 11 and integral with the casing 3.
  • the silencer chamber 16 has a discharge-side opening 17 in communication with the discharge port 6.
  • the shape, size and other details of the silencer chamber 16 and opening 17 may be freely selected.
  • Operation of the second embodiment is similar to that of the first embodiment and any noise due to pressure fluctuations of the air 5 discharged through the port 6 can be effectively suppressed due to the presence of the silencer chamber.
  • the noise-suppressing effect is maximised since the silencer chamber 16 is adjacent to the source of noise generation by the compressor.
  • the cusp 11 is reinforced and thus stiffened by the presence of the outer wall portion 15, so that any vibration of the cusp 11 is suppressed, thereby suppressing the generation of noise due to vibration.
  • Figs. 8 and 9 illustrate a still further embodiment of the invention in which both suction- and discharge-side silencer chambers 13 and 16 like those in Figs. 4 and 5 and in Figs. 6 and 7 are defined by the cusps 10 and 11 and the adjacent portions of the part-cylindrical walls and the silencer outer wall portions 12 and 15, respectively.
  • the silencer chambers 13 and 16 have suction- and discharge-side openings 14 and 17 in communication with the suction and discharge ports 4 and 6, respectively.
  • the noise suppression is attained with no substantial change in size of the casing 3 since, as mentioned above, the silencer chambers are defined between a respective cusp 10,11 and the associated outer wall portion 12,15 integral with the casing 3. Therefore, the compressor may be readily mounted in a vehicle or the like without difficulty in contrast to conventional compressors with silencers or the like connected to the piping leading to the suction and discharge ports.
  • both suction- and discharge-side silencer chambers 13 and 16 fulfils the effects of both the first and second embodiments and suppresses noise at both the suction- and discharge-sides. Moreover, it makes the outer shape of the whole of the casing 3 substantially cylindrical, so that the overall strength and rigidity is further increased. As a result, any vibration of the cusps 10 and 11 is further suppressed thereby further suppressing the generation of noise due to vibration.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Supercharger (AREA)
EP19970306761 1996-09-09 1997-09-02 Compresseur du type Lysholm Expired - Lifetime EP0828079B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP238065/96 1996-09-09
JP23806596 1996-09-09
JP23806596A JPH1082385A (ja) 1996-09-09 1996-09-09 リショルム型コンプレッサのケーシング構造

Publications (3)

Publication Number Publication Date
EP0828079A2 true EP0828079A2 (fr) 1998-03-11
EP0828079A3 EP0828079A3 (fr) 1998-12-23
EP0828079B1 EP0828079B1 (fr) 2003-03-12

Family

ID=17024641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19970306761 Expired - Lifetime EP0828079B1 (fr) 1996-09-09 1997-09-02 Compresseur du type Lysholm

Country Status (3)

Country Link
EP (1) EP0828079B1 (fr)
JP (1) JPH1082385A (fr)
DE (1) DE69719642T2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1340916A3 (fr) * 2002-02-28 2003-11-05 Teijin Seiki Co., Ltd. Pompe à vide du type à vis
EP1831566A4 (fr) * 2004-12-09 2011-03-16 Carrier Corp Suppression de bruit de compresseur
EP1647713A3 (fr) * 2004-10-15 2012-10-24 CNH Italia S.p.A. Pompe pour fluide avec résonateur de Helmholtz
WO2019084019A1 (fr) * 2017-10-25 2019-05-02 Carrier Corporation Passage de gaz d'évacuation interne pour compresseur
CN115355170A (zh) * 2022-07-29 2022-11-18 迈科微真空技术(苏州)有限公司 一种高度集成的真空泵泵体

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10359032A1 (de) * 2003-12-15 2005-07-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
US8056543B2 (en) * 2009-04-24 2011-11-15 GM Global Technology Operations LLC Tuning device with combined backflow function
DE202016001950U1 (de) 2016-03-30 2017-07-03 Leybold Gmbh Vakuumpumpe
CN208089547U (zh) 2017-09-30 2018-11-13 江森自控空调冷冻设备(无锡)有限公司 一种滑阀

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1258543B (de) * 1960-07-16 1968-01-11 Philipp Bormuth Dipl Ing Roots-Geblaese mit Voreinstroemung in die Kolbenkammern
JPS59176490A (ja) * 1983-03-24 1984-10-05 Toyoda Autom Loom Works Ltd スクリユ−圧縮機
DE9006233U1 (de) * 1990-06-01 1991-09-26 H. Spelleken Nachf. Lufttechnik GmbH, 5600 Wuppertal Drehkolbenverdichter
US5312235A (en) * 1993-09-24 1994-05-17 Northern Research & Engineering Corporation Apparatus for reducing pressure pulsations
JPH07217563A (ja) * 1994-01-31 1995-08-15 Ebara Corp スクリュー流体機械の中空ロータ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1340916A3 (fr) * 2002-02-28 2003-11-05 Teijin Seiki Co., Ltd. Pompe à vide du type à vis
US7052259B2 (en) 2002-02-28 2006-05-30 Teijin Seiki Co., Ltd. Vacuum exhausting apparatus
EP1647713A3 (fr) * 2004-10-15 2012-10-24 CNH Italia S.p.A. Pompe pour fluide avec résonateur de Helmholtz
EP1831566A4 (fr) * 2004-12-09 2011-03-16 Carrier Corp Suppression de bruit de compresseur
EP2551527A3 (fr) * 2004-12-09 2014-06-11 Carrier Corporation Suppression de bruit de compresseur
WO2019084019A1 (fr) * 2017-10-25 2019-05-02 Carrier Corporation Passage de gaz d'évacuation interne pour compresseur
CN111247342A (zh) * 2017-10-25 2020-06-05 开利公司 用于压缩机的内部排气通道
US11365735B2 (en) 2017-10-25 2022-06-21 Carrier Corporation Internal discharge gas passage for compressor
CN115355170A (zh) * 2022-07-29 2022-11-18 迈科微真空技术(苏州)有限公司 一种高度集成的真空泵泵体

Also Published As

Publication number Publication date
JPH1082385A (ja) 1998-03-31
EP0828079A3 (fr) 1998-12-23
DE69719642D1 (de) 2003-04-17
DE69719642T2 (de) 2003-10-16
EP0828079B1 (fr) 2003-03-12

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