EP3701151B1 - Lubricant supply passage for compressor background - Google Patents

Lubricant supply passage for compressor background Download PDF

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Publication number
EP3701151B1
EP3701151B1 EP18803497.9A EP18803497A EP3701151B1 EP 3701151 B1 EP3701151 B1 EP 3701151B1 EP 18803497 A EP18803497 A EP 18803497A EP 3701151 B1 EP3701151 B1 EP 3701151B1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
passage
lubricant
fluid machine
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.)
Active
Application number
EP18803497.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3701151A1 (en
Inventor
Masao Akei
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.)
Carrier Corp
Original Assignee
Carrier Corp
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Filing date
Publication date
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Publication of EP3701151A1 publication Critical patent/EP3701151A1/en
Application granted granted Critical
Publication of EP3701151B1 publication Critical patent/EP3701151B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • 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
    • 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
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the subject matter disclosed herein relates generally to fluid machines, and more specifically, to fluid machines, such as compressors.
  • Non-flammable, low GWP refrigerants are replacing existing refrigerants in many applications, but have lower density and do not possess the same cooling capacity as existing refrigerants.
  • Replacement refrigerants require a compressor capable of providing a significantly greater displacement, such as a screw compressor.
  • a fluid machine that includes a casing; a first rotor fixed to a first shaft, the first rotor and the first shaft being rotatable about a first axis, wherein the first shaft is rotatably supported by the casing; a second rotor supported by the second shaft, the second rotor being rotatable about a second axis, wherein the second rotor is configured to rotate about the second shaft and wherein the second shaft is supported by and fixed relative to the casing; a sump having a volume of lubricant contained therein, a first lubricant passage for supplying lubricant from the sump to a dynamic interface associated with the first rotor, and a second lubricant passage for supplying lubricant from the sump to a dynamic interface associated with the second rotor.
  • a pressure differential created within the fluid machine supplies the lubricant from the sump to the first lubricant passage and the second lubricant passage simultaneously.
  • the pressure differential is formed between a high pressure adjacent at least one end of the casing and low pressure at a central location of the first rotor and the second rotor.
  • first rotor and the first shaft are rotatably mounted to the casing without roller element bearings.
  • At least one surface of the casing and the first shaft define the dynamic interface associated with the first rotor.
  • the at least one surface of the casing arranged in direct contact with the first shaft functions as a bearing.
  • the at least one surface of the casing arranged in direct contact with the first shaft includes a first surface arranged in direct contact with a portion of the first shaft adjacent a first end, and a second surface arranged in direct contact with a portion the first shaft adjacent a second end.
  • the first lubricant passage includes a first portion for supplying lubricant to the first surface and a second portion, distinct from the first portion, for supplying lubricant to the second surface.
  • the first lubricant passage further comprises: a cavity formed in a portion of the casing adjacent the first shaft, a passage extending axially through at least a portion of the first shaft, at least one radial hole coupling the cavity and the passage, and a groove extending from the cavity to an interior of a compression pocket formed between the first rotor and the second rotor and the casing.
  • the first lubricant passage further comprises: a counter bore formed at the interface between the casing and the compression pocket.
  • the first lubricant passage comprises: a groove extending from the sump to an interior of a (the) compression pocket formed between the first rotor and the second rotor and the casing.
  • the second rotor comprises a working portion rotatable relative to the second shaft.
  • the second shaft and the working portion define the dynamic interface associated with the second rotor.
  • the second lubricant passage further comprises: a first passage extending axially through at least a portion of the second shaft, a second passage formed in an outer periphery of the second shaft, and at least one radial hole coupling the first passage and the second passage.
  • the second passage extends axially such that a first end of the second passage is fluidly coupled to a first portion of the casing and a second, opposite end of the second passage is fluidly coupled to a second portion of the casing.
  • a counter bore is formed in the casing where at least one of the first lubricant passage and the second lubricant passage enters a compression pocket formed between the first rotor and the second rotor.
  • the fluid machine comprises a recess formed in the casing in fluid communication with the counter bore, the recess being arranged at an angle towards an interface between the first rotor and the second rotor.
  • At least one of an angle, length, width, and depth of the recess is optimized to control a flow of lubricant to the compression pocket.
  • a method of lubricating one or more dynamic interfaces of a fluid machine comprising a casing.
  • the method includes supplying lubricant from a sump to a dynamic interface associated with a first rotor fixed to a first shaft of the fluid machine via a first lubricant passage, wherein the first rotor and the first shaft are rotatable about a first axis, and wherein the first shaft is rotatably supported by the casing; and supplying lubricant from a sump to a dynamic interface associated with a second rotor supported by a second shaft of the fluid machine via a second lubricant passage, wherein the second rotor is rotatable about a second axis, wherein the second rotor is configured to rotate about the second shaft and wherein the second shaft is supported by and fixed relative to the casing.
  • the second lubricant passage is distinct from the first lubricant passage. Supplying lubricant to the dynamic interface associated with the first rotor and the dynamic interface associated with the second rotor occurs automatically and simultaneously in response to a pressure differential created within the fluid machine during operation of the fluid machine.
  • supplying lubricant from the sump to the dynamic interface associated with the first rotor and supplying lubricant from the sump to the dynamic interface associated with the second rotor occurs without a pump or control valve.
  • supplying lubricant from the sump to the dynamic interface associated with the first rotor further comprises: supplying lubricant via a first passage to a first bearing surface, the first passage extending through an opening formed in a first shaft of the first rotor, and supplying lubricant via a second passage to a second bearing surface.
  • the fluid machine 20 is an opposed screw compressor.
  • a fluid machine such as a pump, fluid motor, or engine for example.
  • the fluid machine 20 includes a first rotor 22 intermeshed with a second rotor 24.
  • the first rotor 22 is a male rotor having a male-lobed working portion 26 and the second rotor 24 is a female rotor including a female-lobed portion 28.
  • the first rotor 22 may be a female rotor and the second rotor 24 may be a male rotor.
  • the working portion 26 of the first rotor 22 includes at least one first helical lobe 30 and at least one second helical lobe 32.
  • the first rotor 22 includes two separate portions defining the first helical lobes 30 and the second helical lobes 32.
  • the first rotor 22, including the first and second helical lobes 30, 32 may be formed as a single integral piece.
  • the fluid machine 20 includes a first shaft 34 fixed for rotation with the first rotor 22.
  • the fluid machine 20 further include a casing 36 rotatably supporting the first shaft 34 and at least partially enclosing the first rotor 22 and the second rotor 24.
  • a first end 38 and a second end 40 of the casing 36 are configured to rotatably support the first shaft 34.
  • the first, lower end 38 of the casing 36 is formed by a lower bearing housing 42 and the second, upper end 40 of the casing 36 is formed by a distinct upper bearing housing 44.
  • a rotor case 46 may extend between and couple the lower and upper bearing housings 42, 44.
  • embodiments where the lower bearing housing 42 and/or the upper bearing housing 44 is integrally formed with the rotor case 46 are also contemplated herein.
  • the first shaft 34 of the illustrated embodiments is directly coupled to an electric motor 48 operable to drive rotation of the first shaft 34 about an axis X.
  • Any suitable type of electric motor 48 is contemplated herein, including but not limited to an induction motor, permanent magnet (PM) motor, and switch reluctance motor for example.
  • the first rotor 22 is fixed to the first shaft 34 by a fastener, coupling, integral formation, interference fit, and/or any additional structures or methods known to a person having ordinary skill in the art (not shown), such that the first rotor 22 and the first shaft 34 rotate about axis X in unison.
  • the fluid machine 20 additionally includes a second shaft 50 operable to rotationally support the second rotor 24.
  • the second rotor 24 includes an axially extending bore 52 within which the second shaft 50 is received.
  • the second shaft 50 is stationary or fixed relative to the casing 36 and the second rotor 24 is configured to rotate about the second shaft 50.
  • embodiments where the second shaft 50 is also rotatable relative to the casing 36 are also contemplated herein.
  • the first rotor 22 is shown as including four first helical lobes 30 and at least four second helical lobes 32.
  • the illustrated, non-limiting embodiment is intended as an example only, and it should be understood by a person of ordinary skill in the art that any suitable number of first helical lobes 30 and second helical lobes 32 are within the scope of the disclosure.
  • the first helical lobes 30 and the second helical lobes 32 have opposite helical configurations.
  • the first helical lobes 30 are left-handed and the second helical lobes 32 are right-handed.
  • the first helical lobes 30 may be right-handed and the second helical lobes 32 may be left-handed.
  • the second rotor 24 has a first portion 54 configured to mesh with the first helical lobes 30 and a second portion 56 configured to mesh with the second helical lobes 32.
  • each portion 54, 56 of the second rotor 24 includes one or more lobes 58 having an opposite configuration to the corresponding helical lobes 30, 32 of the first rotor 22.
  • the first portion 54 of the second rotor 24 has at least one right-handed lobe 58a
  • the second portion 56 of the second rotor 24 includes at least one left-handed lobe 58b.
  • the first portion 54 of the second rotor 24 is configured to rotate independently from the second portion 56 of the second rotor 24.
  • Each portion 54, 56 of the second rotor 24 may include any number of lobes 58.
  • the total number of lobes 58 formed in each portion 54, 56 of the second rotor 24 is generally larger than a corresponding portion of the first rotor 24.
  • the first rotor 22 includes four first helical lobes 30
  • the first portion 54 of the second rotor 24 configured to intermesh with the first helical lobes 30 may include five helical lobes 58a.
  • a gas or other fluid such as a low GWP refrigerant for example, is drawn to a central location by a suction process generated by the fluid machine 20.
  • Rotation of the first rotor 22 and the second rotor 24 compresses the refrigerant and forces the refrigerant toward the outer ends 38, 40 of the casing 36 due to the structure and function of the opposing helical rotors 22, 24.
  • the compressed refrigerant is routed by an internal gas passage within the casing 36 and discharged through the upper end 40 of the casing 36.
  • the discharged refrigerant passes through the electric motor 48 and out of the discharge outlet 59.
  • the fluid machine 20 includes one or more lubricant supply passages for providing a lubricant from a sump 61 to the dynamic interfaces of the machine 20.
  • the sump 61 containing a volume of lubricant, such as oil for example is located adjacent and in communication with the lower bearing housing 42.
  • a first shaft passage 60 extends axially through at least a portion of the first shaft 34. In the illustrated, non-limiting embodiment, the first shaft passage 60 extends from adjacent the lower end 38 of the casing 36 to adjacent the upper end 40 of the casing 36.
  • a cavity 68 formed in the upper bearing housing 64 is configured to surround a periphery of part of the first shaft 34.
  • At least one radial hole 70 extends between the first shaft passage 60 to the outer surface of the shaft 34 to deliver lubricant to the cavity 68.
  • two radial holes 70 extending in opposite directions relative to one another from the first shaft passage 60 to the outer surface of the shaft 34.
  • one or more surfaces of the bore formed in the upper bearing portion 44 and configured to contact the first shaft 34 may function as a bearing. For example, with reference for FIG.
  • a first surface 72 disposed adjacent a first side of the cavity 68 is operable as a main bearing and a second surface 74, disposed adjacent a second, opposite side of the cavity 68, is operable as a sub-bearing.
  • the bore formed in a lower bearing portion 62 for receiving a portion of the first shaft 34 includes a surface 76 operable as a bearing.
  • a groove 80 extends over the axial length of the surface 72.
  • This groove 80 is arranged in fluid communication with the cavity 68 and is configured to distribute lubricant from the cavity 68 over the axial length of the first surface 72.
  • a groove 84 extends over the axial length of the surface 76. The groove 84 is configured to distribute lubricant from the sump 61 located adjacent the lower bearing housing 42.
  • a second shaft passage 86 extends axially through the lower bearing housing 42 and at least a portion of the second shaft 50.
  • the second shaft passage 86 extends over about half of the axial length of the second shaft 50.
  • a shaft passage 86 of any length is contemplated herein.
  • an axially extending passage 88 is formed in an outer periphery of the second shaft 50 and at least one radial hole 90 fluidly couples the shaft passage 86 and the axial passage 88.
  • the radial hole is arranged generally centrally relative to the axial passage such that a portion of the lubricant is distributed in two directions relative to the radial hole 90.
  • the axial passage 88 is configured to distribute lubricant at the interface formed between the second shaft 50 and the bore 52 formed in the second rotor 24. In an embodiment, the axial passage 88 extends between the upper and lower bearing housings 44, 42.
  • the lubricant supply passages are intended to lubricate the surfaces 72, 74, and 76 of the upper and lower bearing housings 42, 44 that function as bearings for the first shaft 34, and the interface between the second shaft 50 and the second rotor 24 to reduce friction there between.
  • a counter bore 78, 82, 92, 94 may be formed in the surfaces of the lower bearing housing 42 and the upper bearing housing 44 facing the first and second rotors 22, 24, respectively.
  • the counterbore 78 may be arranged in fluid communication with the groove 80.
  • the counterbore 82 may be arranged in fluid communication with the groove 84.
  • the counterbore 92, 94 may be arranged in fluid communication with the axial passage 88. As a result, lubricant will flow to the counter bores 92, 94 after lubricating the interface between the second shaft 50 and the second rotor 24.
  • a recess 96 may extend from one or more of the counter bores 78, 82, 92, 94 at an angle towards the interface between the first rotor 22 and the second rotor 24.
  • the fluid machine illustrated and described herein includes a recess formed at each of the counter bores, embodiments where none or only some of the counter bores includes a recess are also within the scope of the disclosure.
  • each recess 96 may be optimized to control the amount of lubricant flow to the compression pocket.
  • the recess 96 has a linear contour and is aligned with the interface between the lobes 30, 32 of the first rotor 22 and the corresponding lobes 58a, 58b of the second rotor 24. Accordingly, as shown FIG. 6 , the angle of the recess 96 relative to the axis extending through the origin of both the first and second shafts 34, 50 is between 0 degrees and 60 degrees.
  • the recess 96 By positioning the recess 96 in alignment with the intermeshing engagement of the rotors 22, 24, the recess communicates with both the high pressure and low pressure areas adjacent the first rotor 22 and second rotor 24. As a result, lubricant may flow from the recess 96 into the compression pocket formed between the first and second rotors 22, 24.
  • the length of the recess 96 measured radially from the origin of the bore for receiving a corresponding shaft 34 or 50 is greater than a root radius of the rotor 22 or 24. Further, the length of the recess 96 may be greater than the root radius, but less than the tip radius of the rotor 22 or 24 associated therewith.
  • a width of the recess 96 measured perpendicular to the length, is between 1mm and 10mm, and a depth of the recess 96 extending into the lower or upper bearing housing 42, 44 is between 1-5 times the axial length of the clearance between the rotor 22 or 24 and the adjacent surface of the lower or upper bearing housing 42, 44. It should be understood that in embodiments including a plurality of recesses, the configuration of recesses may be the same, or alternatively, may be different.
  • the fluid machine 20 illustrated and described herein provides a simple and low cost configuration for a lubricant supply system. Because the pressure of the machine 20 is used to draw the fluid to the respective interfaces, costly devices, such as a pump or control valve for example, are not required. Further, because the lubricant is driven by the pressure differential created during operation of the machine 20, a stable supply of lubricant is provided over a wide range of shaft speeds.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP18803497.9A 2017-10-24 2018-10-16 Lubricant supply passage for compressor background Active EP3701151B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201762576430P 2017-10-24 2017-10-24
PCT/US2018/056101 WO2019083778A1 (en) 2017-10-24 2018-10-16 LUBRICANT SUPPLY PASSING FOR COMPRESSOR BOTTOM

Publications (2)

Publication Number Publication Date
EP3701151A1 EP3701151A1 (en) 2020-09-02
EP3701151B1 true EP3701151B1 (en) 2022-03-02

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP18803497.9A Active EP3701151B1 (en) 2017-10-24 2018-10-16 Lubricant supply passage for compressor background

Country Status (5)

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US (1) US20200325899A1 (zh)
EP (1) EP3701151B1 (zh)
CN (1) CN111247343A (zh)
ES (1) ES2909572T3 (zh)
WO (1) WO2019083778A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230086482A1 (en) * 2019-12-17 2023-03-23 Johnson Controls Tyco IP Holdings LLP Lubricant system for a compressor
CN112780554A (zh) 2021-02-26 2021-05-11 珠海格力电器股份有限公司 压缩机和空调
CN112780558A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 转子组件、压缩机及空调
CN112780561A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 转子组件、压缩机及空调
CN112797000A (zh) * 2021-02-26 2021-05-14 珠海格力电器股份有限公司 转子组件、压缩机和空调

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WO2016157450A1 (ja) * 2015-03-31 2016-10-06 株式会社日立産機システム ガス圧縮機

Also Published As

Publication number Publication date
US20200325899A1 (en) 2020-10-15
ES2909572T3 (es) 2022-05-09
CN111247343A (zh) 2020-06-05
WO2019083778A1 (en) 2019-05-02
EP3701151A1 (en) 2020-09-02

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