US3736079A - Lubricating oil flow control for a rotary compressor - Google Patents

Lubricating oil flow control for a rotary compressor Download PDF

Info

Publication number
US3736079A
US3736079A US00239064A US3736079DA US3736079A US 3736079 A US3736079 A US 3736079A US 00239064 A US00239064 A US 00239064A US 3736079D A US3736079D A US 3736079DA US 3736079 A US3736079 A US 3736079A
Authority
US
United States
Prior art keywords
rotor
lubricating oil
rotors
chamber
wall
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
US00239064A
Other languages
English (en)
Inventor
D B Kantz
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.)
Ford Motor Co
Original Assignee
Ford Motor Co
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 Ford Motor Co filed Critical Ford Motor Co
Application granted granted Critical
Publication of US3736079A publication Critical patent/US3736079A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • 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
    • F04C29/021—Control systems for the circulation of the lubricant

Definitions

  • ABSTRACT A rotary compressor adapted especially for pumping fluids in a closed circuit of an air conditioning system comprising a pair of meshing helical rotors adapted for rotation about parallel axes and a lubrication oil flow path including registering oil ports in one of said rotors and in an adjacent housing wall whereby fluid is admitted to the lubrication oil circuit intermittently at a rate that is dependent upon the speed of the rotors thereby providing a desired higher lubricating oil flow at high compressor speeds and a reduced flow at lower compressor speeds to establish lubrication, sealing and cooling of the relatively movable parts of the compressor.
  • the improvements of my invention relate generally to rotary compressors of the Lysholm type.
  • Such compressors require the presence of lubricating oil to establish sealing between the rotor members and the surrounding compressor housing and also between the meshing parts of the two rotors.
  • the rotors comprise helical teeth, one rotor having internal helical teeth and the other having registering external helical teeth.
  • Lubricating oil is necessary also to reduce friction and to provide the necessary cooling.
  • the oil is capable of carrying away heat generated due to the compression of the compressible fluid. The heat is dissipated as the oil is circulated through the lubricating oil circuit.
  • the oil is returned to a sump and is forced to the inlet side of the lubricating oil circuit by the discharge pressure of the compressor. The oil then is recycled.
  • a lubricating oil pump for supplying fluid to the inlet side of the lubricating oil circuit and to drive the lubricating oil pump, which may be a positive displacement pump, by connecting it mechanically through'a drive system to one of the rotor members.
  • a flow restricting control orifice is provided on the inlet side of the lubricating oil circuit in prior art arrangements. Because the pressure drop across the oriflce is substantially uniform, the oil flow for lubricating, sealing and cooling the compressor is relatively constant. The oil flow requirements during high speed operation are substantially greater than the requirements for low speed operation. The lubricating system, therefore, must be calibrated to satisfy the maximum flow requirements at high speeds. This results in a generally inefficient lubricating oil system at lower speeds since excess oil is pumped.
  • the portion of the housing adjacent the end of that rotor member is provided with a lubricating oil inlet chamber which communicates with the lubricating oil inlet port, which in turn communicates with the oil sump in the air conditioner system.
  • the metering chambers in the rotor member are charged with lubricating oil as each chamber successively registers with the lubricating oil chamber in the adjacent housing wall.
  • Oil in the chamber then is carried to a discharge point where it is centrifuged into the compressor cavity and mixed with the compressed fluid, which in some instances is Freon gas.
  • the frequency of the discharge increases.
  • a decrease in rotor speed will result in a decrease in the rate of lubricating oil supply.
  • This pumping action is accomplished without the addition of extraneous pumping elements and without the necessity for providing a calibrated fluid flow circuit for the lubricating oil.
  • the compressor efficiency is determined in part by the amount of Freon gas that becomes dissolved in the lubricating oil as the latter traverses the lubricating oil circuit. This represents a short-circuit for the compressed gas, and the presence of the short-circuit decreases the compressor efficiency since the Freon gas that is dissolved cannot be used for cooling purposes. If the rate of lubricating oil flow is decreased at lower speeds, the short-circuiting losses due to the loss of compressed Freon gas is reduced.
  • the pressure at which the lubricating oil is supplied to the system tends to increase at low speeds because of the higher back pressure that then develops in the condenser.
  • the condenser receives, in most instances, an inadequate air supply for cooling purposes when the compressor is operated at low speed. This tends to aggravate the lubricating oil losses at low speeds since the presence of a higher oil pressure tends to cause an increased rate of flow of lubricating fluid to the compressor mechanisms when any increased flow is not required.
  • the improved system of my invention also overcomes mechanical and pumping horsepower losses that accompany some prior art systems that require the presence of a positive displacement lubricating oil supply pump.
  • FIG. 1 shows a side elevation view of a compressor that is capable of using the improvements of my invention.
  • FIG. 2 is an end view of the compressor shown in FIG. 1.
  • FIG. 3 is a cross-sectional view taken along the plane of section line 3-3 of FIG. 2.
  • FIG. 4 is a partial side elevation view as seen from the plane of section line 44 of FIG. 2.
  • FIG. 5 is a cross-sectional view taken along the plane of section line 55 of FIG. 4.
  • FIG. 6 is a schematic representation of the ends of the rotors shown in FIG. 3 acting in their respective rotor chambers in the compressor housing.
  • FIG. 7 is a detailed view of an externally threaded helical rotor of the assembly of FIG. 3.
  • FIG. 8 is an end view of the rotor of FIG. 7.
  • FIG. 9 is a detail view of the other rotor shown in the assembly view of FIG. 3.
  • FIG. 10 is an end view of the rotor of FIG. 9.
  • the compressor shown in FIG. 1 is adapted to be used in an automotive vehicle air conditioning system. It includes a compressor housing 10 which is adapted to be mounted in a stationary portion of the vehicle chassis in the engine compartment of the vehicle. It includes a drive pulley 12 which can be connected to the vehicle engine crankshaft by a suitable drive belt. Numeral l4 designates the housing 4. An electromagnetic clutch structure can be applied and deactivated to establish a driving connection between pulley l2 and the drive rotor of the compressor. There are two rotors, one of which is the drive rotor 26, mounted within the housing 10. Numeral 16 designates an end plate for closing the rotor chambers within the housing 10.
  • FIGS. 4 and 5 An inlet port 18 for the compressor is shown in FIGS. 4 and 5.
  • Port 18 is formed in housing 10 as part of an integral casting. It is defined in part by a fitting 20 which is connected to a Freon fluid conduit. Port 18 communicates with rotor chamber 22 in the main housing 10, as indicated in FIG. 5.
  • An outlet port 24 also is formed in the cover 16 as part of an integral casting.
  • a helical rotor 26 is mounted within rotor chamber 28. Rotor 26 meshes with a second helical rotor 30 mounted for rotation about an axis parallel to the axis of rotor 26. Rotor 26 comprises external helical threads which register with internal helical threads on driven rotor 30. The periphery of the threads for rotor 26 are in close registry contact with the wall of the chamber 28 and sealed with an oil film. A corresponding sliding contact occurs between the periphery of the internal helical threads 30 and the wall of the rotor chamber 32. A suitable lubricating oil film is disposed between the relatively movable surfaces.
  • One axial end of the rotor 30 is provided with radially extending metering chambers 34, 36 and 38.
  • the radially inward ends of the chamber 34, 36 and 38 register with a lubricating oil inlet collector port 40 formed in the adjacent wall of the cover 15.
  • Port 40 communicates with oil inlet passage 42, which in turn communicates with the oil sump not shown.
  • the radially outward end of metering chambers 34, 36 and 38 communicate with a lubricating oil discharge chamber 44 formed in the adjacent face of the cover 16 in the general region of the rotor chamber 28.
  • the radial disposition of the chamber 44 with respect to the axis of rotation of the rotor 30 is such that a portion of the end face of the rotor 30 covers a portion of the chamber 44 where the remaining portion of the chamber 44 is exposed at all times to the chamber 28.
  • the metering chambers 34, 36 and 38 selectively register with the port 40. Oil inlet pressure then is admitted to each of the chambers selectively thereby filling the chambers. Upon continued rotation of the rotor 30, each of the chambers selectively registers with the chamber 44. Oil under centrifugal pressure in the chambers 34, 36 and 38 then is centrifuged outwardly into the chamber 28. There the oil mixesv with the compressed Freon and is distributed throughout the surfaces of the rotors and the registering surfaces of the rotor chambers. This oil provides an effective rotor seal between the rotors and between the rotors and the chamber walls. It also lubricates the relatively movable surfaces and carries away heat due to the compression of the fluid and due to the mechanical friction.
  • the frequency of the discharges from the metering chambers increases thereby increasing the total fluid flow through the lubricating circuit.
  • the lubricating flow requirements increase as the speed increases and the increased metering action provides the necessary volume. Conversely the flow of lubricating oil decreases at lower speeds when the lubricating oil flow requirements are reduced.
  • Rotor 26 acts as a driving rotor. It is connected to or formed integrally with driveshaft 46 to which is splined a clutch driveplate 48.
  • the rotor carriesan electromagnetic winding 50 which is adapted to establish a flux field when it is energized thereby establishing a driving connection between driveplate 48 and armature 52.
  • Driveplate 48 in turn, is connected to power input shaft 54 which in turn carries drive pulley l2.
  • Pulley 12 is journalled by bearing 56 on a stub shaft 58 which forms a part of a clutch housing 14.
  • a rotary compressor for gaseous fluids comprising a first pump rotor with external helical teeth, a second pump'rotor with internal helical teeth, the helical teeth on said rotors registering with each other as they rotate about parallel axes, a rotor housing, a pair of rotor chambers communicating with each other formed in said housing, one chamber receiving the external tooth rotor and the second chamber receiving the internal tooth rotor, said housing including an end wall closing said rotor chambers, said wall being disposed adjacent end surfaces on said rotors, the end surface on one of said rotors having formed therein radially disposed metering chambers, a lubricating oil inlet chamber formed in said wall at a radial location where it is adapted to register with radially inward portions of said metering chamber, said lubricating oil inlet chamber being in fluid communication with a lubricating oil supply passage, a fluid discharge chamber formed in said wall at a radially outward location relative to the

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
US00239064A 1972-03-29 1972-03-29 Lubricating oil flow control for a rotary compressor Expired - Lifetime US3736079A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US23906472A 1972-03-29 1972-03-29

Publications (1)

Publication Number Publication Date
US3736079A true US3736079A (en) 1973-05-29

Family

ID=22900429

Family Applications (1)

Application Number Title Priority Date Filing Date
US00239064A Expired - Lifetime US3736079A (en) 1972-03-29 1972-03-29 Lubricating oil flow control for a rotary compressor

Country Status (5)

Country Link
US (1) US3736079A (de)
JP (1) JPS4915009A (de)
CA (1) CA973136A (de)
DE (1) DE2313587A1 (de)
GB (1) GB1389973A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
US6485279B2 (en) * 2000-12-26 2002-11-26 Carrier Corporation Thrust load reliever
US20120037473A1 (en) * 2010-08-13 2012-02-16 Eaton Corporation Integrated clutch supercharger
US9086012B2 (en) 2010-08-13 2015-07-21 Eaton Corporation Supercharger coupling
US20200003211A1 (en) * 2017-02-09 2020-01-02 Daikin Industries, Ltd. Screw compressor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4826412A (en) * 1987-05-01 1989-05-02 Kabushiki Kaisha Kobe Seiko Sho Mechanically driven screw supercharger
JP2006083713A (ja) * 2004-09-14 2006-03-30 Yamaha Marine Co Ltd 過給装置の潤滑構造
JP4614853B2 (ja) 2005-09-26 2011-01-19 ヤマハ発動機株式会社 過給機の取付構造

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2737341A (en) * 1950-02-25 1956-03-06 Trico Products Corp Rotary pump
US3073513A (en) * 1960-04-26 1963-01-15 Svenska Rotor Maskiner Ab Rotary compressor
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US3518975A (en) * 1967-05-09 1970-07-07 Reinhold Schmidt Rotary-piston engine
US3649140A (en) * 1970-05-11 1972-03-14 Borg Warner Oil metering system for rotary compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2737341A (en) * 1950-02-25 1956-03-06 Trico Products Corp Rotary pump
US3073513A (en) * 1960-04-26 1963-01-15 Svenska Rotor Maskiner Ab Rotary compressor
US3462072A (en) * 1967-05-03 1969-08-19 Svenska Rotor Maskiner Ab Screw rotor machine
US3518975A (en) * 1967-05-09 1970-07-07 Reinhold Schmidt Rotary-piston engine
US3649140A (en) * 1970-05-11 1972-03-14 Borg Warner Oil metering system for rotary compressor

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
US6485279B2 (en) * 2000-12-26 2002-11-26 Carrier Corporation Thrust load reliever
US20120037473A1 (en) * 2010-08-13 2012-02-16 Eaton Corporation Integrated clutch supercharger
US8464697B2 (en) * 2010-08-13 2013-06-18 Eaton Corporation Integrated clutch supercharger
CN103180630A (zh) * 2010-08-13 2013-06-26 伊顿公司 整体式离合器增压器
US8776767B2 (en) 2010-08-13 2014-07-15 Eaton Corporation Integrated clutch supercharger
US9086012B2 (en) 2010-08-13 2015-07-21 Eaton Corporation Supercharger coupling
CN103180630B (zh) * 2010-08-13 2015-08-19 伊顿公司 整体式离合器增压器
US20200003211A1 (en) * 2017-02-09 2020-01-02 Daikin Industries, Ltd. Screw compressor

Also Published As

Publication number Publication date
JPS4915009A (de) 1974-02-09
CA973136A (en) 1975-08-19
DE2313587A1 (de) 1973-10-04
GB1389973A (en) 1975-04-09

Similar Documents

Publication Publication Date Title
US3811805A (en) Hydrodynamic thrust bearing arrangement for rotary screw compressor
US3558248A (en) Screw type refrigerant compressor
US4645429A (en) Rotary compressor
US3796526A (en) Screw compressor
US3744942A (en) Rotary sliding vane compressor with hydrostatic bearings
US3988080A (en) Rotary vane compressor with outlet pressure biased lubricant
US3214087A (en) Rotary piston machine
US3016184A (en) Rotary compressors
US2824687A (en) Rotary compressor
US3736079A (en) Lubricating oil flow control for a rotary compressor
US3743453A (en) Compact rotary sliding vane compressor for an automotive air-conditioning system
CN1865706B (zh) 开放式驱动涡旋机
US3490382A (en) Gearing and lubricating means therefor
US4431356A (en) Hermetic refrigeration rotary motor-compressor
US4795325A (en) Compressor of rotary vane type
KR970003266B1 (ko) 내부윤활유 펌프를 갖춘 수평방향 회전장치
US3877853A (en) Vane controlling system for rotary sliding vane compressor
WO2018012411A1 (ja) 開放型冷媒圧縮機
US5169299A (en) Rotary vane compressor with reduced pressure on the inner vane tips
US6093007A (en) Multi-rotor helical-screw compressor with thrust balance device
US3649140A (en) Oil metering system for rotary compressor
KR101011202B1 (ko) 베인 로터리형 공기펌프
JPS63500112A (ja) 潤滑油ポンプと潤滑油通路を備えた内燃機関
US1595381A (en) Oil pump
US3250459A (en) Gear-rotor motor-compressor