US3833318A - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
US3833318A
US3833318A US00371822A US37182273A US3833318A US 3833318 A US3833318 A US 3833318A US 00371822 A US00371822 A US 00371822A US 37182273 A US37182273 A US 37182273A US 3833318 A US3833318 A US 3833318A
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US
United States
Prior art keywords
chambers
housing means
rotary compressor
wall
cylinder
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
US00371822A
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English (en)
Inventor
S Nakayama
M Kurahashi
T Sugiura
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.)
Toyota Industries Corp
Original Assignee
Toyoda Automatic Loom Works 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 Toyoda Automatic Loom Works Ltd filed Critical Toyoda Automatic Loom Works Ltd
Application granted granted Critical
Publication of US3833318A publication Critical patent/US3833318A/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
    • F04C29/02—Lubrication; 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • LaPointe ABSTRACT positioned at the ends of a hollow shell, a horizontal cylinder disposed in the shell and having pressure plates attached to the front and rear ends thereof and further comprising a front housing means interposed between the front housing and the front pressure plate for defining a first front chamber connected by fluid passage means to said inlet port, between the inner wall of said front housing and the outer wall of said front housing means, and a second front chamber connected by fluid passage means to said suction chambers of said cylinder, between the inner wall of said front housing means and the outer face of said front pressure plate, said front housing means having a through-hole to connect said first and second front chambers, and channels adjacent to said oil reservoir to connect said first and second front chambers to said oil reservoir, and;
  • a rear housing means interposed between the rear housing and the rear pressure plate for defining a first rear chamber connected fluid passage means to said inlet port, between the inner wall of said rear housing and the outer wall of said rear housing means, and a second rear chamber by fluid passage means connected to said suction chambers of said cylinder, between the inner wall of said rear housing means and the outer face of said rear pressure plate, said rear housing means having a through-hole to connect said first and second rear chambers, and channels adjacent to said oil reservoir to connect said first and second rear chambers to said oil reservoir.
  • the present invention relates to a rotary compressor having slidable vanes, which is conveniently applied for aircooling of the vehicle and more particularly, relates to a specific arrangement within such rotary compressor as having a horizontal axially extending hollow shell defining an outermost casing which has a lubricant reservoir at the lower-most portion therein and an inlet port at an upper portion thereof for introducing refrigerant gas to be compressed, front and rear housings positioned at ends of the hollow shell, a horizontal cylinder stationarily disposed in the shell and having pressure plates attached to front and rear ends thereof to define a closed room within the cylinder, and a rotor eccentric and rotatable within the closed room of the cylinder and provided with a number of radial slots for slidably inserting vanes therein whereby the cylinder and the rotor define a space between the inner and outer surfaces thereof for compressing the refrigerating gas
  • Japanese Utility Model Registration No. 903,216 published June 8, 1970, discloses a type of rotary compressor having slidable vanes, in which there is provided a recess which is formed in an outer wall section of the cylinder including a wall portion facing the refrigerant inlet provided in the outermost shell so as to extend along the cimcumference of the cylinder while having an axial width larger than the diameter of the inlet.
  • the recess provides a refrigerant suction space between the outer wall of the cylinder and the inner wall of the shell.
  • a principal object of the present invention is to provide a rotary compressor having slidable vanes which can eliminate the above-mentioned objectionable feature of the known compressor, and in which refrigerants returned from an evaporator into the cylinder of the compressor can undergo repeated oil separating operations for almost entirely separating oil content in the returned refrigerant while they are flowing from the inlet for the compressor into the compressing chamber within the cylinder, in order to raise compression efficiency and accordingly, air-cooling efficiency of the compressor.
  • the rotary compressor mentioned in the beginning of the present disclosure is characterized in that there are further provided front housing means interposed between the front housing and the front pressure plate for defining a first front chamber in fluid communication with the inlet port, between the inner wall of said front housing and the outer wall of said front housing means, and a second front chamber in fluid communication with the suction chambers of said cylinder, between the inner wall of said front housing means and the outer face of said front pressure plate, said front housing means having a through-hole thereby to. connect said first and second front chambers, and channels adjacent to said oil reservoir to connect said first and second front chambers to said oil reservoir, and;
  • a rear housing means interposed between the rear housing and the rear pressure plate for defining a first rear chamber in fluid communication with said inlet port, between the inner wall of said rear housing and the outer wall of said rear housing means, and a second rear chamber in fluid communication with connected to said suction chambers of said cylinder, between the inner wall of said rear housing means and the outer face of said rear pressure plate, said rear housing means having a throughhole thereby to connect said first and second chambers, and channels adjacent to said oil reservoir to connect said first and second rear chambers to said oil reservoir.
  • FIGS. 1 and 2 are outermost views of the axially opposing ends of a rotary compressor according to the preferred embodiment of the present invention
  • FIG. 3 is a cross sectional view along a vertical plane between the opposing ends shown in FIGS. 1 and 2;
  • FIG. 4 is a longitudinal cross sectional view along the line X, X of FIG. 3;
  • FIG. 5 is a longitudinal cross sectional view along the line X"!
  • X Of FIG. 6 is a front view of a rear pressure plate employed in the rotary compressor of FIG. 1;
  • FIGS. 7 and 8 are rear and front views of a rear pressure housing of the rotary compressor of FIG. 1;
  • FIGS. 9 and 10 are rear and front views of a front pressure housing of the rotary compressor of FIG. 1.
  • FIGS. 1 and 2 show both ends of a rotary compressor according to a preferred embodiment of the present invention, which includes a longitudinal axis and said both ends face each other at both ends of said axis.
  • Returned refrigerants from an evaporator (refer to FIGS. 1 and 2) of an air-cooling circuit flow into the rotary. compressor through an inlet, and after being compressed therein, are delivered through an outlet and to a condenser in the air-cooling circuits as shown by an arrow labeled to condenser in FIGS. 1 and 2.
  • l0 and 2 respectively show a drive shaft along the longitudinal axis and an oil reservoir which is provided at the bottom of this compressor.
  • Cylinder 3 is stationarily fitted into shell 1, the front and rear ends of said cylinder being closed by pressure plates 4 and 5.
  • Front and rear pressure housings 6 and 7 are placed between said housing 8 and pressure plate 4, and housing 9 and pressure plate 5, respectively.
  • Refrigerant inlet passage 19 is formed by a part of the space between individual inner walls of shell 1, housing 8 and housing 9, and individual outer walls of cylinder 3, pressure plates 4, and pressure housings 6 and 7.
  • One end of said passage 19 is for the passage of fluids connected to a first front chamber 17 defined by the space between the inner side wall of front housing 8 and the outer side wall of front pressure housing 6 through a recess 19a of pressure plate 4 and a recess 19c of pressure housing 6.
  • the other end of said passage 19 is connected for the passage of fluids to a first rear chamber 18 defined by the space between the inner side wall of rear housing 9 and the outer side wall of rear pressure housing 7 through a recess 19b of pressure plate 5 and a recess 19d of pressure housing 7.
  • the sectional areas of both said first chambers are constructed so as to be larger than that of said refrigerant inlet passage 19.
  • a second front chamber 22 is defined by the space between the inner side wall of pressure housing 6 and the outer side wall of pressure plate 4, and a second rear chamber 23 is defined by the space between the inner side wall of pressure housing 7 and the outer side wall of pressure plate 5.
  • the first front chamber 17 and the second front chamber 22, and the first rear chamber 18 and the second rear chamber 23 communicate with each other by through-holes 24 and 25, respectively.
  • Holes 24 and 25 are respectively perforated through the pressure housings 6 and 7 at a position above the center axes of said pressure housings and as distant as possible from the passage 19 (refer to FIGS. 7 thru Sectional areas of the two first chambers 17 and 18 are constructed so as to be larger than those of the two second chambers 22 and 23, which are, in turn, larger than those of the two upper through-holes 24 and 25.
  • Alternative holes 28 and 29 are respectively perforated through pressure plates 4 and 5, at different positions from said holes 24 and 25, and communicating passages between second chambers 22 and 23 and a gas-tight chamber 35.
  • the lower portions of first chambers 17 and 18, and of second chambers 22 and 23 are provided with guide channels 20, 21, 34 and 37 to discharge lubricating oils separated from the refrigerants by these chambers into oil reservoir 2.
  • Inlet 26 provided near the center of shell 1 meets at right angles with refrigerant inlet passage 19, and drive shaft 10 is rotatably positioned slightly eccentrically to the axis of cylinder 3 and supported by said housings and also, for example, by bearings 11 and 12.
  • the drive shaft 10 mounts a rotor 13 thereon so that rotor 13 is housed in the cylinder 3.
  • the inner peripheral wall surface of said cylinder 3 associates with the outer peripheral wall surface of rotor 13 to define a space forming a gas-tight arch shaped chamber 35 (refer to FIG. 3).
  • Said gas-tight chamber 35 is separable, by a plurality of slidable leaf vanes fitted into a corresponding number of vane channels 14 formed radially around the rotor 13, into several chambers, as shown for example in FIG. 3. It will be seen that gas-tight chambers 35A and 35B are located on the inlet side, and communicate with said holes 28 and 29 (refer to FIG. 4) in order to suck the refrigerant therethrough, and gas-tight chambers 35C and 35D are located on the compression side and communicate with an outlet hole 27 in the pressure plate 5 (refer to FIG. 6), and the chamber positioned between the chamber 35B and the chamber 35C is an intermediate chamber between the inlet side and the outlet side.
  • Numerals 31 and 32 indicate channels for directing oil in the reservoir 2 to various moving parts in the compressor in order to lubricate the parts.
  • Numeral 33 indicates a pump for suction of the oil in the reservoir 2 through the channels 31 and 32. The pump 33 is connected to the drive shaft 10 and is operable upon rotation of the drive shaft 10.
  • Gaseous refrigerants evaporated through an evaporator (not shown) are returned to the compressor after having circulated in the predetermined air-cooling circuits.
  • the returned refrigerants are directly led to a refrigerant inlet passage 19 through inlet 26 extending through the shell 1.
  • the refrigerants Upon entering inlet passage 19 the refrigerants are divided into two branches by flowing into the front and rear sections of said passage 19.
  • a first oil separating operation is accomplished by inertia, since the refrigerants are forced to change direction at an angle of substantially
  • the diverged streams of refrigerant pass in opposite directions through the refrigerant inlet passage 19, and reach the two first chambers 17 and 18, respectively, wherein the refrigerants are directed to the bottoms of said chambers 17 and 18 through recesses 19c and 19d formed in the peripheries of pressure housings 6 and 7, as shown by arrows in FIG. 4.
  • the speeds of the refrigerants will decrease at this time because the sectional area of each of the chambers 17 and 18 is larger than that of the passage 19.
  • the refrigerants in the second chambers 22 and 23 with their oil content removed by the above three oil separating operations are delivered toward the center portion of said gas-tight chambers 35A and 35B (refer to FIG. 3) on the inlet side, from the front and rear sides of the chamber 35, through arch shaped holes 28 and 29 (refer to FIG. 6) perforated through pressure plates 4 and 5.
  • Refrigerants reaching gas-tight chambers 35A and 35B on the inlet side are rotated to gastight chambers 35C and 35D (refer to FIG. 3) on the outlet side, during which time said refrigerants are compressed in said chambers. This is because said gastight chambers are gradually decreased in volume from the inlet side to the outlet side, with revolution of the rotor 13.
  • Refrigerants then, are delivered to a condenser through the outlet hole 27 and an outlet 36 provided in pressure plate 5 and rear pressure housing 7, respectively.
  • lubricating oils separated by said first chambers 17 and 18, and by said second chambers 22 and 23 may be entrained up in refrigerant flows and respectively enter into the second chambers 22 and 23, and gastight chamber 35.
  • the holes 24, 25, 28 and 29 are positioned in the upper portions of said two first and two second chambers. Said separated lubricating oils are expelled into the oil reservoir 2 through their own guide channels.
  • inlet refrigerants change direction to the right and left, since inlet 26 meets at right angles with refrigerant inlet passage 19.
  • first oil separating operation can be accomplished by inertia.
  • the second and the third oil separating operations can be accomplished by said first chambers and said second chambers.
  • this invention can also achieve an increase in the volume to be sucked in without changing the volume of the inlet chamber, thereby attaining a remarkable increase in suction efficiency.
  • Refrigerants are separated from the oil flow toward the center of gas-tight chambers on the inlet side from both side ends of the chambers. Consequently, the refrigerants from both directions will collide with each other at approximately the center portion of gas-tight chambers on the inlet side, and their kinetic energy is thereby changed to heat energy promoting the rise of gas pressure.
  • this invention also provides an increased air-cooling and heating capability over the prior art compressor. Also, in accordance with the concept of the present invention, several small oil separation chambers are separately disposed in place of provision of a single voluminous oil separation chamber in the known compressors.
  • the present invention allows appropriate distribution of small oil separation chambers in a predesigned space provided for an assembled compressor and, therefore, a compressor which requires a relatively small installation space, can be provided.
  • a rotary compressor having a horizontal axially extending hollow shell defining an outermost casing which has a lubricant reservoir at the lowermost'portion therein and an inlet port at an upper portion thereof for introducing refrigerant gas to be compressed
  • front and rear housings positioned at ends of the hollow shell
  • a horizontal cylinder stationarily disposed in the shell and having pressure plates attached to front and rear ends thereof to define a closed room within the cylinder
  • a front housing means interposed between a front housing and the front pressure plate for defining a first front chamber fluidly connected to said inlet port, between the inner wall of said front housing and the outer wall of said front housing means, and a second front chamber fluidly connected to said suction chambers of said cylinder, between the inner wall of said front housing means and the outer face of said front pressure plate, said front housing means having a through-hole to connect said first and second front chambers, and channels adjacent to said oil reservoir to connect said first and second front chambers to said oil reservoir,
  • a rear housing means interposed between the rear housing and the rear pressure plate for defining a first rear chamber fluidly connected to said inlet port, between the inner wall of said rear housing and the outer wall of said rear housing means, and a second rear chamber fluidly connected to said suction chambers of said cylinder, between the inner wall of said rear housing means and the outer face of said rear pressure plate, said rear housing means having a through-hole to connect said first and second rear chambers, and channels adjacent to said oil reservoir to connect said first and second rear chambers to said oil reservoir.
  • a rotary compressor as defined in claim 2 wherein said two branches of the refrigerant gas are introduced into the end of said compressing chamber through inlet holes of said respective pressure plates, said inlet holes directing said refrigerant gas branches to collide with each other at approximately the center portion of said compressing chamber.
  • a rotary compressor as defined in claim 1 wherein said second front and rear chambers are fluidly connected to said suction chambers through-holes perforated in said pressure plates respectively, and wherein said through-holes of said front and rear housing means and said holes of said pressure plates are circumferentially out of alignment, with respect to the center of said shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)
US00371822A 1972-07-27 1973-06-20 Rotary compressor Expired - Lifetime US3833318A (en)

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JP1972088852U JPS4947208U (de) 1972-07-27 1972-07-27

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DE (1) DE2332411C3 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4091638A (en) * 1976-12-13 1978-05-30 Borg-Warner Corporation Cooling system for hermetic compressor
US4340339A (en) * 1979-02-17 1982-07-20 Sankyo Electric Company Limited Scroll type compressor with oil passageways through the housing
US4830590A (en) * 1987-04-03 1989-05-16 Diesel Kiki Co., Ltd. Sliding-vane rotary compressor
EP0362757A2 (de) * 1988-10-07 1990-04-11 Alcatel Cit Drehkolbenmaschine der Art einer Schraubenpumpe
US4932845A (en) * 1987-11-21 1990-06-12 Sanden Corporation Scroll type compressor with lubrication in suction chamber housing
US5088897A (en) * 1989-03-02 1992-02-18 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with internal refrigerant and lubricant separating system
US5330335A (en) * 1991-07-31 1994-07-19 Sanden Corporation Horizontally oriented rotary machine having internal lubication oil pump
US5772407A (en) * 1995-04-28 1998-06-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating piston type compressor improved to distribute lubricating oil sufficiently during the starting phase of its operation
US20060245939A1 (en) * 2005-04-27 2006-11-02 Tetsuhiko Fukanuma Compressor
US20070175239A1 (en) * 2006-02-01 2007-08-02 Yoshinori Inoue Refrigerant compressor
US20100154442A1 (en) * 2008-12-22 2010-06-24 Michael Steven Schoenoff Portable Refrigerant Recovery Machine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1878403A (en) * 1928-10-18 1932-09-20 Sulzer Ag Refrigerating machine
US2677944A (en) * 1950-12-01 1954-05-11 Alonzo W Ruff Plural stage refrigeration apparatus
US3312387A (en) * 1964-12-30 1967-04-04 Borg Warner Lubrication system for rotary compressor
US3352485A (en) * 1965-10-22 1967-11-14 Toyoda Automatic Loom Works Swash plate compressor for use in air conditioning system for vehicles
US3676024A (en) * 1971-03-02 1972-07-11 Nissan Motor Apparatus for separating lubricant from a refrigerant lubricant mixture in a reciprocating type automotive air conditioner compressor
US3730648A (en) * 1970-04-13 1973-05-01 S Komiya Swash plate type compressor for automobile air-conditioning

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1878403A (en) * 1928-10-18 1932-09-20 Sulzer Ag Refrigerating machine
US2677944A (en) * 1950-12-01 1954-05-11 Alonzo W Ruff Plural stage refrigeration apparatus
US3312387A (en) * 1964-12-30 1967-04-04 Borg Warner Lubrication system for rotary compressor
US3352485A (en) * 1965-10-22 1967-11-14 Toyoda Automatic Loom Works Swash plate compressor for use in air conditioning system for vehicles
US3730648A (en) * 1970-04-13 1973-05-01 S Komiya Swash plate type compressor for automobile air-conditioning
US3676024A (en) * 1971-03-02 1972-07-11 Nissan Motor Apparatus for separating lubricant from a refrigerant lubricant mixture in a reciprocating type automotive air conditioner compressor

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4091638A (en) * 1976-12-13 1978-05-30 Borg-Warner Corporation Cooling system for hermetic compressor
US4340339A (en) * 1979-02-17 1982-07-20 Sankyo Electric Company Limited Scroll type compressor with oil passageways through the housing
US4830590A (en) * 1987-04-03 1989-05-16 Diesel Kiki Co., Ltd. Sliding-vane rotary compressor
US4932845A (en) * 1987-11-21 1990-06-12 Sanden Corporation Scroll type compressor with lubrication in suction chamber housing
EP0362757A2 (de) * 1988-10-07 1990-04-11 Alcatel Cit Drehkolbenmaschine der Art einer Schraubenpumpe
FR2637655A1 (fr) * 1988-10-07 1990-04-13 Cit Alcatel Machine rotative du type pompe a vis
EP0362757A3 (en) * 1988-10-07 1990-04-18 Alcatel Cit Rotary machine of the screw pump type
US4983106A (en) * 1988-10-07 1991-01-08 Societe Anonyme Dite: Alcatel Cit Rotary screw machine with multiple chambers in casing for lubrication-coding fluid
US5088897A (en) * 1989-03-02 1992-02-18 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type compressor with internal refrigerant and lubricant separating system
US5330335A (en) * 1991-07-31 1994-07-19 Sanden Corporation Horizontally oriented rotary machine having internal lubication oil pump
US5772407A (en) * 1995-04-28 1998-06-30 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocating piston type compressor improved to distribute lubricating oil sufficiently during the starting phase of its operation
US20060245939A1 (en) * 2005-04-27 2006-11-02 Tetsuhiko Fukanuma Compressor
EP1717445A1 (de) * 2005-04-27 2006-11-02 Kabushiki Kaisha Toyota Jidoshokki Verdichter
US20070175239A1 (en) * 2006-02-01 2007-08-02 Yoshinori Inoue Refrigerant compressor
US20100154442A1 (en) * 2008-12-22 2010-06-24 Michael Steven Schoenoff Portable Refrigerant Recovery Machine
US8800306B2 (en) * 2008-12-22 2014-08-12 Bosch Automotive Service Solutions Llc Portable refrigerant recovery machine

Also Published As

Publication number Publication date
DE2332411C3 (de) 1980-09-25
JPS4947208U (de) 1974-04-25
DE2332411B2 (de) 1980-02-07
DE2332411A1 (de) 1974-02-07

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