US20020094294A1 - Gas compressor - Google Patents

Gas compressor Download PDF

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Publication number
US20020094294A1
US20020094294A1 US10/033,853 US3385301A US2002094294A1 US 20020094294 A1 US20020094294 A1 US 20020094294A1 US 3385301 A US3385301 A US 3385301A US 2002094294 A1 US2002094294 A1 US 2002094294A1
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US
United States
Prior art keywords
discharge
oil
gas
cylinder
refrigerant gas
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
US10/033,853
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English (en)
Inventor
Hiroaki Sekiguchi
Makoto Ijiri
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Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of US20020094294A1 publication Critical patent/US20020094294A1/en
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
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet

Definitions

  • the present invention relates to a gas compressor mounted in a vehicle as a part of an automotive air conditioner system or mounted in an exterior unit as a part of an air conditioning system and, in particular, to a gas compressor in which the pressure loss of an oil containing high-pressure refrigerant gas is reduced to thereby achieve an improvement in compressor performance.
  • a conventional example of a gas compressor of this type has a cylinder 1 having a substantially elliptical inner peripheral configuration, side blocks 2 and 3 being respectively mounted to the end surfaces of the cylinder 1 .
  • a rotor 4 is arranged inside the cylinder 1 between the front and rear side blocks 2 and 3 .
  • the rotor 4 is horizontally positioned so as to be rotatable through a rotor shaft 5 integrally provided at its axial center and bearings 6 and 7 of the side blocks 2 and 3 supporting the same.
  • FIG. 4 As shown in FIG. 4, five slit-like vane grooves 8 are formed radially in the rotor 4 , and vanes 9 are respectively attached to these vane grooves 8 , the vanes 9 being capable of jutting out from the outer peripheral surface of the rotor 4 toward the inner wall of the cylinder 1 and retracting into the rotor 4 .
  • the interior of the cylinder 1 is divided into a plurality of small chambers by the inner wall of the cylinder 1 , the inner surfaces of the side blocks 2 and 3 , the outer peripheral surface of the rotor 4 , and the side surfaces of the forward end portions of the vanes 9 .
  • the small chambers thus defined constitute compression chambers 10 , whose volume is repeatedly varied as the rotor 4 rotates in the direction of the arrow RD.
  • the oil containing low-pressure refrigerant gas in a suction chamber 11 is introduced into the compression chambers 10 through suction passages 12 of the cylinder 1 and inlets 13 of the side blocks 2 and 3 . Then, when the volume of the compression chambers 10 starts to decrease, the refrigerant gas in the compression chambers 10 starts to be compressed due to the volume reduction effect. Thereafter, when the volume of the compression chambers 10 approaches to its minimum, discharge valves 15 of cylinder discharge holes 14 provided near the elliptically short diameter portion of the cylinder 1 are opened by the pressure of the compressed oil containing high-pressure refrigerant gas. As a result, the oil containing high-pressure refrigerant gas in the compression chambers 10 are discharged through the cylinder discharge holes 14 .
  • the oil-containing high-pressure refrigerant gas discharged through the cylinder discharge holes 14 flows through discharge chambers 16 and discharge gas passages 24 in the outer periphery of the cylinder 1 before it is led to oil separation filters 18 - 1 of an oil separator 18 mounted to the rear portion of the side block 3 .
  • the oil containing high-pressure refrigerant gas led to the oil separation filters 16 - 1 is separated into an oil component and a gas component as a result, for example, of striking against wire-meshes constituting the oil separation filters 18 - 1 .
  • the gas component flows into a discharge chamber 19 , and is then supplied from the discharge chamber 19 to the condenser side of the air conditioning system by way of a discharge port of a compressor case (not shown).
  • the oil component drips down into an oil sump 20 at the bottom of the discharge chamber 19 to be stored, and is supplied to portions where oil is required through an oil passage 21 of the side blocks 2 and 3 and the cylinder 1 .
  • Examples of the portions where the oil is required include the clearances of the bearings 6 and 7 , flat grooves 22 formed on the sides of the side blocks 2 and 3 facing the cylinder, and vane back pressure spaces 23 at the bottom of the vanes 9 communicating therewith.
  • the above-described conventional gas compressor adopts a structure in which, to enhance the oil separation performance, the discharge gas passages 24 of the oil separator 18 are bent twice at right angles to thereby cause the oil containing high-pressure refrigerant gas to strike against the inner walls of the gas passages 24 twice.
  • This striking construction provides little or no effect of improving the oil separation performance. Rather, it involves an increase in the pressure loss of the oil containing high-pressure refrigerant gas, which leads to deterioration in the compressor performance.
  • the present invention has been made with a view toward solving the above problem in the prior art. It is an object of the present invention to provide a gas compressor which can reduce the pressure loss of the oil containing high-pressure refrigerant gas to thereby achieve an improvement in compressor performance.
  • the present invention relates to a gas compressor comprising a cylinder arranged between a pair of side blocks, a rotor horizontally arranged in the cylinder so as to be rotatable, vanes provided so as to be capable of jutting out toward the inner wall of the cylinder from the outer peripheral surface of the rotor and retracting therein, compression chambers defined by the cylinder, the side blocks, the rotor, and the vanes, cylinder discharge holes for discharging refrigerant gas from the compression chambers, a discharge chamber for temporarily storing the refrigerant gas discharged from the cylinder discharge holes, a linear discharge gas passage for guiding the refrigerant gas from the discharge chamber to the downstream side of the discharge chamber, an oil separator arranged on the downstream side of the discharge gas passage and having an oil separation filter for separating the refrigerant gas and the oil from each other, and a discharge chamber for temporarily storing the refrigerant gas and the oil separated by the oil separation filter.
  • the discharge gas passage is made linear, whereby the oil containing high-pressure refrigerant gas flows smoothly through the discharge gas passage, thereby reducing the pressure loss of the oil containing high-pressure refrigerant gas.
  • present invention relates to a gas compressor, wherein the height of an outlet opening on the oil separator side of the discharge gas passage is set to be the same as the height of an inlet opening of the discharge gas passage, whereby the discharge gas passage extends horizontally.
  • the oil separator side opening of the discharge gas passage communicating with the discharge chamber is set to be of the same height as the inlet opening thereof, whereby the discharge gas passage extends horizontally and is of the shortest length, whereby it is possible to further reduce the pressure loss of the oil containing high-pressure refrigerant gas.
  • the present invention relates to a gas compressor, wherein the oil separation filter of the oil separator is positioned above the outlet opening of the discharge gas passage.
  • the oil separation filter of the oil separator is positioned above the outlet opening of the discharge gas passage, so that a large space can be secured for the oil sump below the oil separation filter.
  • FIGS. 1A, 1B, and 1 C are an explanatory drawing showing a main portion of a gas compressor according to the present invention
  • FIG. 1A is a front view of a built-in oil separator in the gas compressor
  • FIG. 1B is a rear view thereof
  • FIG. 1C is a sectional view taken along the line B-B of FIG. 1B.
  • FIGS. 2A, 2B, and 2 C are an explanatory drawing showing a main portion of a gas compressor in accordance with another embodiment of the present invention
  • FIG. 2A is a front view of a built-in oil separator in the gas compressor
  • FIG. 2B is a rear view thereof
  • FIG. 2C is a sectional view taken along the line B-B of FIG. 2B.
  • FIG. 3 is a sectional view of a gas compressor according to the present invention.
  • FIG. 4 is a sectional view taken along the line A-A of FIG. 3.
  • FIG. 5A, FIG. 5B, and FIG. 5C are an explanatory drawing showing an oil separator mounted in the conventional gas compressor
  • FIG. 5A is a front view of the oil separator
  • FIG. 5B is a rear view thereof
  • FIG. 5C is a sectional view taken along the line B-B of FIG. 5B.
  • the basic construction of the gas compressor of this embodiment is the same as that of the conventional gas compressor shown in FIGS. 3 and 4, in which the cylinder 1 is arranged between a pair of side blocks 2 and 3 and in which the rotor 4 is horizontally arranged inside the cylinder 1 so as to be rotatable, the vanes 9 being provided so as to be capable of jutting out toward the inner wall of the cylinder 1 from the outer peripheral surface of the rotor 4 and retracting therein.
  • the compression chambers 10 defined by the vanes 9 , etc.
  • the volume of the compression chambers 10 repeatedly increases and decreases as the rotor 4 rotates, whereby the oil containing low-pressure refrigerant gas in the suction chamber is taken in and compressed. Further, the compressed oil containing high-pressure refrigerant gas is discharged through the cylinder discharge holes 14 as in the prior art.
  • the component which are the same as those of the conventional gas compressor will be indicated by the same reference numerals, and a detailed description of such components will be omitted.
  • the oil containing high-pressure refrigerant gas discharged through the cylinder discharge holes 14 as described above flows through the discharge chamber 16 and the discharge gas passages 24 and is led to the oil separation filters 18 - 1 attached to the oil separator 18 .
  • discharge gas passages 24 are formed into a linear shape so as to realize linearization thereof.
  • each discharge gas passage 24 opens on the discharge chamber 16 side, and the other end 24 b thereof opens on the oil separation filter 18 - 1 side of the oil separation filter 18 .
  • the section between one end (inlet opening) 24 a of each discharge gas passage 24 and the other end (outlet opening) 24 b thereof extends in a completely straight line, without being bent anywhere.
  • the discharge gas passage 24 is formed linear whichever direction from seen, for example, front or rear view shown in FIG. 1B, plane view like shown in FIG. 1C, and side view like shown in FIG. 3.
  • Each discharge gas passage 24 is formed extending from the discharge chambers 16 to the oil separator 18 through the rear side block 3 in a punching manner. In this embodiment, the angle at which the discharge gas passage 24 reaches the oil separator 18 is not also changed.
  • each discharge gas passage 24 in the conventional gas compressor is bent substantially at right angles immediately after entering the oil separator 18 through the rear side block 3 , whereas, as shown in FIG. 1, each discharge gas passage 24 of the gas compressor of this embodiment is not bent immediately after entering the oil separator 18 through the rear side block 3 , and is formed linear.
  • two cylinder discharge holes 14 , two discharge chambers 16 , two discharge gas passages 24 , and two oil separation filters 18 - 1 of the oil separator 18 are provided. This is due to the substantially elliptical inner peripheral configuration of the cylinder 1 and due to the structure in which five vanes 9 are provided.
  • intake operation and compressing operation are executed at two positions in the cylinder 1 , and the portions of the oil containing high-pressure refrigerant gas respectively compressed at the two positions are separately guided to the oil separator 18 .
  • the two discharge gas passages 24 and 24 are both linear. However, they are not parallel to each other but are in a v-shaped arrangement in which they are directed toward the two oil separation filters 18 - 1 and 18 - 1 arranged side by side at the center of the oil separator 18 .
  • the oil containing high-pressure refrigerant gas discharged through the cylinder discharge holes 14 is led to the oil separation filters 18 - 1 of the oil separator 18 through the discharge chambers 16 and the discharge gas passages 24 .
  • the discharge gas passages 24 are attempted to be linear, the oil containing high-pressure refrigerant gas can be smoothly transferred from the cylinder discharge holes 14 to the oil separation filters 18 - 1 , whereby the pressure loss of the oil containing high-pressure refrigerant gas is reduced, and the compressor performance is improved.
  • the pressure loss of the oil containing high-pressure refrigerant gas also depends on the sectional area of the discharge gas passages 24 ; the larger the sectional area of the discharge gas passages 24 , the less the pressure loss of the oil containing high-pressure refrigerant gas.
  • the sectional area of the discharge gas passages 24 be set to be as large as possible.
  • FIG. 2 shows a configuration of a gas compressor in accordance with another embodiment of the present invention.
  • FIG. 2A is a rear elevational view of an oil separator as seen from the rear side
  • FIG. 2B is an elevational view of the oil separator as seen from the side abutting the rear side block
  • FIG. 2C is a sectional view taken along the line B-B of FIG. 2B.
  • each discharge gas passage 24 in order to further reduce the pressure loss of the oil containing high-pressure refrigerant gas, is set to be the same as the height of the other end 24 b of the discharge gas passage 24 , that is, the height of the oil separator 18 side outlet opening, whereby each discharge gas passage 24 connecting the inlet and outlet openings 24 a and 24 b extends horizontally and is of the shortest length.
  • discharge gas passages 24 extend horizontally, it is possible to minimize the resistance when passing the high-pressure refrigerant gas therethrough, which also leads to a reduction in pressure loss, thereby achieving a further improvement in compressor function.
  • the discharge gas passages are linear, so that the oil containing high-pressure refrigerant gas flows smoothly from the cylinder discharge holes to the oil separation filters of the oil separator through the discharge gas passages, whereby the pressure loss of the oil containing high-pressure refrigerant gas of this type is reduced, thereby achieving an improvement in compressor performance.
  • the discharge gas passages are formed linearly, and the height of the inlet opening communicating with the discharge chamber is set to be the same as the height of the outlet opening on the oil separator side, whereby the discharge gas passages extend horizontally and are of the shortest length,, thereby further reducing the pressure loss of the oil containing high-pressure refrigerant gas passing through the discharge gas passages to thereby achieve a further improvement in compressor performance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US10/033,853 2000-12-22 2001-12-20 Gas compressor Abandoned US20020094294A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000391184 2000-12-22
JP2000-391184 2000-12-22
JP2001-267792 2001-09-04
JP2001267792A JP3987697B2 (ja) 2000-12-22 2001-09-04 気体圧縮機

Publications (1)

Publication Number Publication Date
US20020094294A1 true US20020094294A1 (en) 2002-07-18

Family

ID=26606426

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/033,853 Abandoned US20020094294A1 (en) 2000-12-22 2001-12-20 Gas compressor

Country Status (6)

Country Link
US (1) US20020094294A1 (ja)
EP (1) EP1217215B1 (ja)
JP (1) JP3987697B2 (ja)
CN (1) CN1309960C (ja)
DE (1) DE60109121T2 (ja)
MY (1) MY129076A (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10527041B2 (en) * 2015-05-26 2020-01-07 Hanon Systems Compressor having oil recovery means

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7520210B2 (en) 2006-09-27 2009-04-21 Visteon Global Technologies, Inc. Oil separator for a fluid displacement apparatus
JP5216470B2 (ja) * 2008-08-08 2013-06-19 カヤバ工業株式会社 可変容量型ベーンポンプ
EP3051136B1 (de) * 2015-01-29 2020-04-01 Pfeiffer Vacuum Gmbh Vakuumpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS572704Y2 (ja) * 1978-07-29 1982-01-18
JPS6016794Y2 (ja) * 1978-08-19 1985-05-24 株式会社ボッシュオートモーティブ システム ベ−ン型圧縮機
JPS57148097A (en) * 1981-03-09 1982-09-13 Mitsubishi Heavy Ind Ltd Rotary compressor
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
JP2585380Y2 (ja) * 1992-11-20 1998-11-18 カルソニック株式会社 ロータリコンプレッサ
JPH0712072A (ja) * 1993-06-23 1995-01-17 Toyota Autom Loom Works Ltd ベーン圧縮機
JPH07151083A (ja) * 1993-11-29 1995-06-13 Nippondenso Co Ltd ベーン型圧縮機
JP2913155B2 (ja) * 1995-09-01 1999-06-28 セイコー精機株式会社 気体圧縮機
JPH0979156A (ja) * 1995-09-08 1997-03-25 Seiko Seiki Co Ltd 気体圧縮機
JP2000297773A (ja) * 1999-04-14 2000-10-24 Bosch Automotive Systems Corp 圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10527041B2 (en) * 2015-05-26 2020-01-07 Hanon Systems Compressor having oil recovery means

Also Published As

Publication number Publication date
EP1217215B1 (en) 2005-03-02
CN1362583A (zh) 2002-08-07
EP1217215A3 (en) 2003-02-26
EP1217215A2 (en) 2002-06-26
CN1309960C (zh) 2007-04-11
DE60109121T2 (de) 2005-07-21
MY129076A (en) 2007-03-30
JP2002250289A (ja) 2002-09-06
JP3987697B2 (ja) 2007-10-10
DE60109121D1 (de) 2005-04-07

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