EP0828079A2 - Lysholm compressors - Google Patents

Lysholm compressors Download PDF

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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)
French (fr)
Other versions
EP0828079A3 (en
EP0828079B1 (en
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
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IHI Corp
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Filing date
Publication date
Application filed by IHI Corp filed Critical IHI Corp
Publication of EP0828079A2 publication Critical patent/EP0828079A2/en
Publication of EP0828079A3 publication Critical patent/EP0828079A3/en
Application granted granted Critical
Publication of EP0828079B1 publication Critical patent/EP0828079B1/en
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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Supercharger (AREA)

Abstract

A Lysholm compressor comprises male and female rotors (1,2) which are rotatably accommodated within a casing structure comprising two part-cylindrical walls (9a,9b) which constitute a casing (3) and merge together at two cusps (10,11) which project inwardly towards one another. A suction port (4) and a discharge port (6) are provided at respective axial ends of the casing (3). A silencer chamber (13,14) is defined between at least one of the cusps (10,11) and respective associated outer wall portions (12, 15) which are situated outside the associated cusp and are integral with the casing (3). The or each silencer chamber (13,16) has a respective opening (14,17) which communicates with the suction port (4) and the discharge port (6), respectively.

Description

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.
As best shown in Fig. 2, which is a schematic vertical sectional view of the compressor in Fig. 1, and Fig 3, which is a view in the direction of the arrows III in Fig. 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.
In the Lysholm compressor shown in Figs. 1 to 3, rotation of the rotors 1 and 2 in the directions of the arrows shown in Fig. 1 causes the air 5 induced through the port 4 to pass through the space 7 whilst being compressed by the rotors 1 and 2, the compressed air 5 then being discharged out of the casing 3 through the port 6.
This construction is disadvantageous in that it generates much noise during operation. It is conventionally proposed for the purpose of suppressing the noise that specially designed suction and discharge ports 4 and 6 be used or that the piping connected to the ports 4 and 6 be provided with noise suppressor means, such as a silencer or resonator (not shown).
However, 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.
Even if noise were satisfactorily suppressed by specially designed ports, the latter would increase the resistance to the air 5 flowing into and out of the space 7, resulting in impairment of the performance of the compressor.
On the other hand, when the compressor described above is 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.
Accordingly it is the object of the present invention to provide a Lysholm compressor and particularly a casing structure therefor which generates less noise and may be readily mounted in a vehicle.
According to one aspect of the present invention 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.
According to a further aspect of the present invention 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.
Thus 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.
Further features of the invention will be apparent from the following description of three preferred embodiments of the invention which is given by way of example with reference to Figures 4 to 9 of the accompanying drawings, in which:
  • Fig. 4 is a schematic vertical sectional view of a first embodiment of the present invention;
  • Fig. 5 is a view in the direction of the arrows V in Fig. 4;
  • Fig. 6 is a view similar to Fig. 4 of a second embodiment of the invention;
  • Fig. 7 is a view in the direction of the arrows VII in Fig. 6;
  • Fig. 8 is a further view similar to Fig. 4 of a third embodiment of the invention; and
  • Fig. 9 is a view in the direction of arrows IX in Fig. 8.
    • Those components which are essentially the same as those described in conjunction with Fig. 1 to 3 are referred to by the same reference numerals.
    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.
    In use, 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.
    In all three embodiments 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.
    In the compressor shown in Figs. 8 and 9, the provision of 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.

    Claims (4)

    1. A casing structure for a Lysholm compressor adapted to accommodate intermeshing male and female rotors (1,2) and which comprises two part-cylindrical walls (9a,9b) which constitute a casing (3) and merge together at two cusps (10,11) which project inwardly towards one another, a suction port (4) at one axial end of the casing (3) and a discharge port (6) at the other axial end of the casing, characterised in that a silencer chamber (13) is defined between one of the cusps (10) and a first outer wall portion (12) which is situated outside the said one cusp (10) and is integral with the casing (3) and has an opening (14) in communication with the suction port (4).
    2. A casing structure for a Lysholm compressor adapted to accommodate intermeshing male and female rotors (1,2) and which comprises two part-cylindrical walls (9a,9b) which constitute a casing (3) and merge together at two cusps (10,11) which project inwardly towards one another, a suction port (4) at one axial end of the casing (3) and a discharge port (6) at the other axial end of the casing, characterised in that a silencer chamber (16) is defined between one of the cusps (11) and a second outer wall portion (12) which is situated outside the said one cusp (11) and is integral with the casing (3) and has an opening (17) in communication with the discharge port (6).
    3. A casing structure as claimed in claim 2, characterised in that a silencer chamber (13) is defined between the other of the cusps (10) and a first outer wall portion (12) which is situated outside the said other cusp (10) and is integral with the casing (3) and has an opening (14) in connection with the suction port (4).
    4. A Lysholm compressor which comprises male and female rotors (1,2) which intermesh at a region (8) and are rotatably accommodated in a casing structure as claimed in any one of claims 1 to 3.
    EP19970306761 1996-09-09 1997-09-02 Lysholm compressors Expired - Lifetime EP0828079B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    JP238065/96 1996-09-09
    JP23806596A JPH1082385A (en) 1996-09-09 1996-09-09 Casing structure of lysholm compressor
    JP23806596 1996-09-09

    Publications (3)

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

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    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP19970306761 Expired - Lifetime EP0828079B1 (en) 1996-09-09 1997-09-02 Lysholm compressors

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    EP (1) EP0828079B1 (en)
    JP (1) JPH1082385A (en)
    DE (1) DE69719642T2 (en)

    Cited By (4)

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    EP1340916A2 (en) * 2002-02-28 2003-09-03 Teijin Seiki Co., Ltd. Screw type vacuum pump
    EP1831566A2 (en) * 2004-12-09 2007-09-12 Carrier Corporation Compressor sound suppression
    EP1647713A3 (en) * 2004-10-15 2012-10-24 CNH Italia S.p.A. Fluid pumping apparatus with Helmholtz-resonator
    WO2019084019A1 (en) * 2017-10-25 2019-05-02 Carrier Corporation Internal discharge gas passage for compressor

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    DE10359032A1 (en) * 2003-12-15 2005-07-14 Bitzer Kühlmaschinenbau Gmbh screw compressors
    US8056543B2 (en) * 2009-04-24 2011-11-15 GM Global Technology Operations LLC Tuning device with combined backflow function
    DE202016001950U1 (en) * 2016-03-30 2017-07-03 Leybold Gmbh vacuum pump
    CN208089547U (en) * 2017-09-30 2018-11-13 江森自控空调冷冻设备(无锡)有限公司 A kind of guiding valve

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    Cited By (10)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP1340916A2 (en) * 2002-02-28 2003-09-03 Teijin Seiki Co., Ltd. Screw type vacuum pump
    EP1340916A3 (en) * 2002-02-28 2003-11-05 Teijin Seiki Co., Ltd. Screw type vacuum pump
    US7052259B2 (en) 2002-02-28 2006-05-30 Teijin Seiki Co., Ltd. Vacuum exhausting apparatus
    EP1647713A3 (en) * 2004-10-15 2012-10-24 CNH Italia S.p.A. Fluid pumping apparatus with Helmholtz-resonator
    EP1831566A2 (en) * 2004-12-09 2007-09-12 Carrier Corporation Compressor sound suppression
    EP1831566A4 (en) * 2004-12-09 2011-03-16 Carrier Corp Compressor sound suppression
    EP2551527A3 (en) * 2004-12-09 2014-06-11 Carrier Corporation Compressor sound suppression
    WO2019084019A1 (en) * 2017-10-25 2019-05-02 Carrier Corporation Internal discharge gas passage for compressor
    CN111247342A (en) * 2017-10-25 2020-06-05 开利公司 Internal exhaust passage for compressor
    US11365735B2 (en) 2017-10-25 2022-06-21 Carrier Corporation Internal discharge gas passage for compressor

    Also Published As

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

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