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EP0650561A1 - Palier axial pour compresseurs hermetiques a piston alternatif - Google Patents

Palier axial pour compresseurs hermetiques a piston alternatif

Info

Publication number
EP0650561A1
EP0650561A1 EP94913459A EP94913459A EP0650561A1 EP 0650561 A1 EP0650561 A1 EP 0650561A1 EP 94913459 A EP94913459 A EP 94913459A EP 94913459 A EP94913459 A EP 94913459A EP 0650561 A1 EP0650561 A1 EP 0650561A1
Authority
EP
European Patent Office
Prior art keywords
axial bearing
face
crankshaft
axial
bearing
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.)
Withdrawn
Application number
EP94913459A
Other languages
German (de)
English (en)
Inventor
Manfred Krueger
Dietmar Erich Bernhard Lilie
Adilson Luiz Manke
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.)
Empresa Brasileira de Compressores SA
Original Assignee
Empresa Brasileira de Compressores SA
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 Empresa Brasileira de Compressores SA filed Critical Empresa Brasileira de Compressores SA
Publication of EP0650561A1 publication Critical patent/EP0650561A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure

Definitions

  • the present invention refers to an axial bearing for reciprocating hermetic compressors with a vertical shaft, of the type used in small refrigerating systems.
  • Reciprocating hermetic compressors usually consist of a motor, mounted inside a hermetically sealed shell. These compressors comprise a cylinder block, supporting a main bearing, inside which rotates a vertical crankshaft, which is provided with a pump rotor at its bottom. During the compressor operation, the rotation of the crankshaft carries, through the pump rotor, lubricant oil from a sump, provided at a lower portion of the compressor shell, up to the bearing and other components.
  • This lubrication of a hydrodynamic nature has the function of forming an oil film between the parts presenting a mutual relative movement, thereby avoiding the contact and, consequently, the wear therebetween.
  • This type of marginal lubrication occurs mainly between the axial bearing and the crankshaft.
  • This axial bearing is mounted to the cylinder block assembly, between the upper portion of the main bearing, in order not to present a relative movement between the latter and the supporting base or peripheral flange of the crankshaft eccentric.
  • Said axial bearing is in the form of a supporting cylindrical ring, with its opposite end faces being parallel to each other. The loads exerted on said axial bearing refer to the weight of the electric motor and crankshaft.
  • an axial bearing for reciprocating hermetic compressors of the type including: a hermetic shell, in which inside is mounted a cylinder block, provided with a main bearing, which carries at its upper portion an axial bearing, supporting a 1 .
  • Fig. 1 is a median vertical sectional view of a compressor of the type used in the present invention
  • Fig. 2 is a perspective view of an axial bearing according to the prior art
  • FIGS 3a - 3f are perspective views of a different construction for an axial bearing, according to the present invention.
  • a reciprocating hermetic compressor comprises a hermetic shell 1, inside which is adequately supported a motor-compressor assembly, formed by a cylinder block 3, whereto is attached an electric motor 4, whose rotor 4a is attached to a crankshaft 5, supported by a bearing 6, which is machined to the cylinder block 3.
  • the crankshaft 5 presents, at its upper portion, a peripheral flange 5a for supporting an eccentric end portion 5b of the crankshaft 5 and, at its lower portion, a pump rotor carrying oil from an oil sump 8 to the parts of the cylinder block 3 in need of lubrication during the compressor operation.
  • the peripheral flange 5a maintains a permanent contact with a secondary axial bearing 9 for supporting said crankshaft 5, according to a contact plane orthogonal to the crankshaft 5, as seen in fig. 2.
  • the axial bearing 9 is in the form of an annular cylindrical body, with a contact face 9a contacting a superficial portion of the peripheral flange 5a and an opposite attaching face 9b to be mounted and attached to a an upper portion of the main bearing 6.
  • said opposite surfaces of the axial bearing 9 are parallel to each other and orthogonal to the crankshaft 5.
  • the rotation of the crankshaft 5 around its geometric axis causes a relative movement between the lower face of the peripheral flange 5a of said crankshaft 5 and the contact face 9a of the axial bearing 9.
  • This relative movement may present severe frictional characteristics, due to the impossibility of forming an adequate lubricant oil film, thereby causing excessive power losses in this bearing.
  • Due to the machining imperfections of the parts the occurrance of thermal deformation or small inclinations of the crankshaft during its rotation cause the formation of a fragile oil film, which is not strong enough to substantially reduce the losses due to visco-mechanical friction in this bearing.
  • the reduction of the compressor power losses, due to friction between the axial bearing 9 and the crankshaft 5, is achieved by using a hydrodynamic axial bearing 10, which allows the permanent formation of an oil film between the frictional surfaces of said axial bearing 10 and crankshaft 5.
  • This oil film acts on said crankshaft 5, lifting the latter during its rotation and minimizing the contact between the frictional surfaces.
  • the formation of an oil film at this region results from a converging wedge shaped spacing between the contact face 10 of the axial bearing 10 and the lower face of the peripheral flange 5a.
  • this spacing in the form of a converging wedge results from the loss of parallelism between said contact face 10a and the lower adjacent face of the peripheral flange 5a.
  • the contact face 10a presents a progressive continuous inclination, along the circumferencial extension of said contact face 10a, relatively to the geometric axis of the axial bearing 10, from a region of said contact face 10a pertaining to the contact plane with the lower face of the peripheral flange 5a, forming a hydrodynamic wedge in the space located between the portion of said contact face 10a spaced from the adjacent face of the peripheral flange 5a of the crankshaft 5, caused by the filling of said space with the lubricant oil.
  • This space forms a cavity which collects the oil and which is capable of retaining a volume of oil necessary to lubricate the two adjacent surfaces and create a hydrodynamic pressure acting under the peripheral flange 5a, lifting said flange during the compressor operation.
  • the oil located in this oil collecting cavity is conducted, by dragging, towards a wall of said cavity, in a direction opposite to that of the lubricant oil flow, thereby forming with said wall the hydrodynamic wedge.
  • the converging wedge between the frictional surfaces of the axial bearing 10 and peripheral flange 5a is achieved by machining, at the contact face 10a of the axial bearing 10, superficial lowered portions 11, which are angularly distributed on said contact face 10a, in order to form on said face alternated steps, where the oil is deposited, said oil coming from the oil sump 8 during the rotation of the crankshaft 5.
  • the amount of the superficial lowered portions 11, as well as the shape and dimensions thereof are defined in function of the desired operational characteristics, machining facility, structural strength of the part, etc..
  • the superficial lowered portions 11 present radial walls, orthogonal to the contact plane between the bearing 10 and the crankshaft 5, said walls being straight or arcuated radial walls, as illustrated respectively in figures 3d and 3e.
  • the effect of the hydrodynamic wedge, when the solution uses superficial lowered portions 11, will be obtained by varying the thickness of the oil film, due to the presence of the end wall of said lowered portions 11, said end wall being in a direction opposite to that of the rotation of the crankshaft 5 and, consequently, of the lubricant oil deposited in said lowered portions 11.
  • the pressure exerted by said lubricant fluid will act on the peripheral flange 5a, as described above.
  • said lowered portions 11 could present distinct radial profiles for their end walls, said profiles not being exactly orthogonal to the plane of the internal surface of said lowered portions 11.
  • the superficial lowered portions 11 present a respective internal face, preferably parallel to the contact plane with the crankshaft 5.
  • the machining of the first face 10a may also be made radially, beginning from the external peripheral edge of said contact face 10a and directed to the internal edge of the latter, so that the largest distance between the adjacent surfaces of the axial bearing 10 and peripheral flange 5a occurs at said internal edge of said axial bearing 10, figure 3f.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Compressor (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

Un palier axial pour compresseurs hermétiques à piston alternatif comprend: un carter hermétique (1) dans lequel est monté un bloc-cylindre (3), pourvu d'un palier principal (6) qui porte, sur sa partie supérieure, un palier axial (9, 10) supportant un vilebrequin (5), une cuvette (8) contenant de l'huile définie au niveau de la partie intérieure du carter (1), ce palier axial (9, 10) présentant une surface de contact (9a, 10a) sur laquelle est supportée une surface inférieure adjacente d'un rebord périphérique (5a) du vilebrequin (5). Au moins une partie de la face de contact (10a) du palier axial (10) est abaissée par rapport à un plan de contact orthogonal au vilebrequin (5), formant au moins une partie abaissée (11) qui est alimentée en continu par l'huile provenant de la cuvette (8), formant un biseau hydrodynamique convergent respectif afin de supporter le rebord périphérique (5a).
EP94913459A 1993-04-30 1994-04-28 Palier axial pour compresseurs hermetiques a piston alternatif Withdrawn EP0650561A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BR9301036 1993-04-30
BR9301036A BR9301036A (pt) 1993-04-30 1993-04-30 Mancal axial para compressores herméticos alternativos
PCT/BR1994/000016 WO1994025768A1 (fr) 1993-04-30 1994-04-28 Palier axial pour compresseurs hermetiques a piston alternatif

Publications (1)

Publication Number Publication Date
EP0650561A1 true EP0650561A1 (fr) 1995-05-03

Family

ID=4056104

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94913459A Withdrawn EP0650561A1 (fr) 1993-04-30 1994-04-28 Palier axial pour compresseurs hermetiques a piston alternatif

Country Status (4)

Country Link
EP (1) EP0650561A1 (fr)
JP (1) JPH07508337A (fr)
BR (1) BR9301036A (fr)
WO (1) WO1994025768A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR9600687A (pt) * 1996-03-13 1998-01-21 Brasil Compressores Sa Mancal axial para compressor hermético
KR100310444B1 (ko) * 1999-06-25 2001-09-29 이충전 밀폐형 왕복동 압축기의 주축베어링 윤활장치
BR0105159B1 (pt) * 2001-08-31 2010-02-09 arranjo de mancal axial para compressor hermÉtico.
JP6571130B2 (ja) * 2017-06-12 2019-09-04 大同メタル工業株式会社 半割スラスト軸受
JP6576976B2 (ja) * 2017-06-12 2019-09-18 大同メタル工業株式会社 半割スラスト軸受

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1269663A (fr) * 1960-06-27 1961-08-18 Perfectionnements aux groupes compresseurs pour machines frigorifiques
EP0092920B1 (fr) * 1982-04-22 1987-03-04 Holset Engineering Company Limited Turbocompresseur
US4726695A (en) * 1986-06-12 1988-02-23 Anatech, Inc. Hydrodynamic thrust bearing
JPH02271106A (ja) * 1989-04-10 1990-11-06 Hitachi Ltd すべり軸受装置
DE4217268C2 (de) * 1992-05-25 1995-01-26 Juergen Dillmann Hydrodynamisch wirksames kombiniertes Radial-Axialgleitlager

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9425768A1 *

Also Published As

Publication number Publication date
WO1994025768A1 (fr) 1994-11-10
BR9301036A (pt) 1994-11-22
JPH07508337A (ja) 1995-09-14

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Legal Events

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19941227

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Effective date: 19961104