WO2012028098A1 - Compresseur à volute - Google Patents

Compresseur à volute Download PDF

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Publication number
WO2012028098A1
WO2012028098A1 PCT/CN2011/079170 CN2011079170W WO2012028098A1 WO 2012028098 A1 WO2012028098 A1 WO 2012028098A1 CN 2011079170 W CN2011079170 W CN 2011079170W WO 2012028098 A1 WO2012028098 A1 WO 2012028098A1
Authority
WO
WIPO (PCT)
Prior art keywords
counterbore
taper
scroll compressor
oil
main bearing
Prior art date
Application number
PCT/CN2011/079170
Other languages
English (en)
Inventor
Weihua Guo
Xiaogeng Su
Original Assignee
Emerson Climate Technologies (Suzhou) Research & Development Co., 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
Priority claimed from CN2010205158146U external-priority patent/CN201982295U/zh
Priority claimed from CN2010102725638A external-priority patent/CN102384082A/zh
Application filed by Emerson Climate Technologies (Suzhou) Research & Development Co., Ltd. filed Critical Emerson Climate Technologies (Suzhou) Research & Development Co., Ltd.
Publication of WO2012028098A1 publication Critical patent/WO2012028098A1/fr

Links

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
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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

Definitions

  • the present disclosure relates to a scroll compressor.
  • a scroll compressor is a new type of displacement compressor that has been developed since 1980s. Due to their features of high efficiency, small volume, light mass, low noise, simple structure and stable operation, scroll compressors are widely used in air conditioning, refrigeration and air compression equipment.
  • FIG. 1 is a sectional view of the structure of a conventional scroll compressor
  • FIG. 2 is an exploded view of a portion of the structure of a conventional scroll compressor.
  • a main bearing thrust face 11 as in FIG. 1
  • 21 as in FIG. 2
  • the main bearing thrust face requires the application of a proper amount of lubricating oil.
  • FIG. 3 is a partial sectional view of a thrust face 31 and a counterbore of a main bearing housing 32 in the scroll compressor shown in FIG. 1;
  • FIG. 4 illustrates a structural relationship between a thrust bearing 41, a main bearing 42 and a driving bearing 43 in the scroll compressor shown in FIG. 1;
  • FIG. 5 illustrates a diagram of the path along which the lubricating oil in the oil sump at the bottom of the scroll compressor flows to the top.
  • an oil pump centrifugal oil pump or displacement pump
  • the driving bearing as indicated by the arrow on the left in FIG. 5
  • the lubricating oil within the clearance between the external diameter of a hub of the orbiting scroll and the internal diameter of the counterbore is pushed, and a certain amount of the lubricating oil will be pushed (pressed) to a thrust bearing face (as indicated by the arrow on the top right in FIG. 5).
  • the amount of the lubricating oil reaching the thrust bearing face is determined by the factors including: 1) the amount of oil pumped by the oil pump into the counterbore (capability of the oil pump); 2) the oil level in the counterbore (which is determined by the position of an oil-exiting hole 51 in the counterbore, as indicated by the horizontal arrow on the right in FIG. 5), a higher position of the oil-exiting hole resulting in a higher oil level in the counterbore and hence a larger amount of oil reaching the thrust bearing face; 3) the clearance between the external diameter of the hub of the orbiting scroll and the internal diameter of the counterbore; and 4) the translational rotational velocity of the orbiting scroll (RPM of the motor, normally 2900RPM).
  • An inverter powering a compressor is capable of working in a wide frequency or rotational speed range, usually at a ratio of the highest rotational velocity to the lowest rotational velocity as large as six.
  • the velocity of the translation of the orbiting scroll may be reduced to less than 1000RPM.
  • the "stir" by the hub of the orbiting scroll may be insufficient to push the oil to the thrust face, causing oil shortage at the thrust face.
  • the compressor with a high amount of oil circulation (2% by weight) has a system refrigeration effect reduced by 2.8% and an energy efficiency ratio reduced by 1.9%.
  • the present disclosure provides a novel scroll compressor, in which the amount of oil reaching a thrust bearing face is adjusted by controlling the size of a taper of a counterbore of a main bearing housing.
  • a scroll compressor which is characterized in that at least a portion of a counterbore of a main bearing housing of the scroll compressor has a taper.
  • only a lower half of the counterbore of the main bearing housing has a negative taper.
  • the whole counterbore of the main bearing housing has a taper.
  • the taper is larger than or equal to arctg(g/co r), wherein g is the acceleration of the gravity, ⁇ is the angular velocity for an oil drip rotating in the counterbore, and r is the rotation radius.
  • FIG. 1 is a sectional view of the structure of a conventional scroll compressor
  • FIG. 2 is an exploded view of a portion of the structure of a conventional scroll compressor
  • FIG. 3 is a partial sectional view of a thrust face in the scroll compressor shown in FIG. 1;
  • FIG. 4 illustrates a structural relationship between a thrust bearing, a main bearing and a driving bearing in the scroll compressor shown in FIG. 1;
  • FIG. 5 illustrates a diagram of the path along which the lubricating oil in the oil sump at the bottom of the scroll compressor flows to the top;
  • FIG. 6 is a schematic diagram illustrating the structure of a counterbore of a main bearing housing having a negative taper according to an embodiment of the present disclosure
  • FIG. 7 is a schematic diagram illustrating an application of a counterbore of a main bearing housing having a negative taper according to an embodiment of the present disclosure
  • FIG. 8 is a schematic diagram illustrating the structure of a counterbore of a main bearing housing having a negative taper using a step according to another embodiment of the present disclosure
  • FIG. 9 is a schematic diagram illustrating the structure of a counterbore of a main bearing housing having a positive taper according to an embodiment of the present disclosure
  • FIG. 10 is a schematic diagram illustrating an application of a counterbore of a main bearing housing having a positive taper according to an embodiment of the present disclosure
  • FIG. 11 is a schematic diagram illustrating an application of a counterbore of a main bearing housing having a positive taper on a horizontal compressor according to an embodiment of the present disclosure
  • FIG. 12 is a schematic diagram illustrating the calculation of the taper according to an embodiment of the present disclosure.
  • FIG. 13 shows the required tapers of the counterbore for different rotational velocities of an oil drip in the case of a positive taper application, when the axial component of the force applied by the inner wall of the counterbore on the oil drop is larger than the weight of the oil drop itself.
  • the counterbore of the main bearing housing has a cylinder structure. Pushed by the hub of the orbiting scroll, the lubricating oil in the counterbore rotates along the inner wall of the counterbore. Hence, most of the lubricating oil rotates on the inner wall of the counterbore under the influence of a centrifugal force, and part of the lubricating oil is pushed up to the thrust bearing face to lubricate the thrust bearing face.
  • At least a portion of the internal diameter of a counterbore of a main bearing housing of the scroll compressor has a taper.
  • the amount of oil reaching the thrust bearing face can be adjusted by designing the size of the taper.
  • the movement direction of the lubricating oil can be controlled by means of a centrifugal force, thereby increasing or reducing the amount of oil supplied upwards, for different purposes.
  • FIG. 6 is a schematic diagram illustrating the structure of a counterbore 61 of a main bearing housing having a negative taper according to an embodiment of the present disclosure
  • FIG. 7 is a schematic diagram illustrating an application of a counterbore of a main bearing housing having a negative taper according to an embodiment of the present disclosure.
  • the force applied on the oil by the inner wall of the counterbore while it is rotating in the counterbore has a downward axial component, thereby accelerating the exit of oil from the oil-exiting hole 71.
  • the amount of oil reaching the thrust bearing face is reduced, which leads to a corresponding reduced amount of oil reaching the thrust face and squeezed out of the thrust face.
  • the amount of oil drawn in by the intake cavity of the scrolls is also reduced, and hence the amount of oil circulation of the system is reduced as well.
  • a negative taper may help reduce the amount of oil circulation into the system.
  • the amount of oil circulation refers to the weight percentage of the oil in the oil-refrigerant mixture entering the refrigeration system. A large amount of oil circulation may reduce the heat transfer efficiency of the copper pipe, and therefore the amount of the system oil circulation is typically desired to be as low as possible.
  • the lower half of the counterbore of the main bearing housing may have a negative taper, as shown in FIG. 8, which is a schematic diagram illustrating the structure of a counterbore of a main bearing housing having a negative taper according to another embodiment of the present disclosure.
  • the negative taper as shown in FIG. 8 may be made with a step, wherein the diameter of the lower half of the counterbore is greater than the diameter of the upper half of the counterbore.
  • a negative taper is introduced to the counterbore of the main bearing housing, thereby reducing the amount of oil reaching the thrust bearing face.
  • the counterbore of the main bearing housing of the scroll compressor may have a positive taper.
  • FIG. 9 is a schematic diagram illustrating the structure of a counterbore 91 of a main bearing housing having a positive taper according to an embodiment of the present disclosure.
  • the lubricating oil on the thrust face is not evenly distributed.
  • the lower half of the thrust face has a larger amount of oil than the upper half, which may cause the lubricating oil shortage on the upper half of the thrust face, and abrasion of the thrust face.
  • the oil supply on the upper half of the thrust bearing face can be increased to improve the lubrication of the upper half of the thrust bearing, and thus the reliability is enhanced.
  • FIG. 12 is a schematic diagram illustrating the calculation of the taper according to an embodiment of the present disclosure.
  • m is the mass of an oil drop
  • g is the acceleration of the gravity
  • ⁇ is the angular velocity for the oil drip rotating in the counterbore
  • r is the rotation radius
  • FIG. 13 shows the required tapers of the counterbore for different rotational velocities of an oil drip in the case of a positive taper application, when the axial component of the force applied by the inner wall of the counterbore on the oil drop is larger than the weight of the oil drop itself.
  • the taper of the counterbore should have a value larger than those shown in the table of FIG. 13.
  • the taper of the counterbore can be determined from experiments. It is noted that an overly large negative taper has a great possibility of causing oil shortage at the thrust face. Many factors may affect the amount of oil on the thrust bearing face, e.g., the amount of oil pumped by the oil pump into the counterbore of the main bearing housing, the position of the oil-exiting hole in the counterbore of the main bearing housing, and the translational velocity of the orbiting scroll.
  • the best angle of the taper selected when using negative tapers to reduce the amount of oil reaching the thrust bearing face can be confirmed through experiments. It is recommended herein to use the same value as the positive taper angle proposed in FIG. 13 as a starting value for the taper in the experiments.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention porte sur un nouveau compresseur à volute permettant de régler la quantité d'huile qui atteint une face de palier de butée par commande de la dimension d'un cône d'un lamage d'un corps de palier principal. Un compresseur à volute selon un mode de réalisation de la présente invention est caractérisé en ce qu'au moins une partie du lamage d'un corps de palier principal du compresseur à volute présente un cône.
PCT/CN2011/079170 2010-08-31 2011-08-31 Compresseur à volute WO2012028098A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201010272563.8 2010-08-31
CN2010205158146U CN201982295U (zh) 2010-08-31 2010-08-31 涡旋压缩机
CN201020515814.6 2010-08-31
CN2010102725638A CN102384082A (zh) 2010-08-31 2010-08-31 涡旋压缩机

Publications (1)

Publication Number Publication Date
WO2012028098A1 true WO2012028098A1 (fr) 2012-03-08

Family

ID=45772168

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/079170 WO2012028098A1 (fr) 2010-08-31 2011-08-31 Compresseur à volute

Country Status (1)

Country Link
WO (1) WO2012028098A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0842470A (ja) * 1994-08-02 1996-02-13 Daikin Ind Ltd スクロール型流体機械
JPH0861255A (ja) * 1994-08-25 1996-03-08 Daikin Ind Ltd スクロール型流体機械
JPH0861267A (ja) * 1994-08-25 1996-03-08 Daikin Ind Ltd スクロール型流体機械
CN101223365A (zh) * 2005-05-23 2008-07-16 丹佛斯商业压缩机公司 涡旋式制冷剂压缩机

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0842470A (ja) * 1994-08-02 1996-02-13 Daikin Ind Ltd スクロール型流体機械
JPH0861255A (ja) * 1994-08-25 1996-03-08 Daikin Ind Ltd スクロール型流体機械
JPH0861267A (ja) * 1994-08-25 1996-03-08 Daikin Ind Ltd スクロール型流体機械
CN101223365A (zh) * 2005-05-23 2008-07-16 丹佛斯商业压缩机公司 涡旋式制冷剂压缩机

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