WO2007123635A1 - Arbre d'entraînement pour compresseur - Google Patents

Arbre d'entraînement pour compresseur Download PDF

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Publication number
WO2007123635A1
WO2007123635A1 PCT/US2007/007625 US2007007625W WO2007123635A1 WO 2007123635 A1 WO2007123635 A1 WO 2007123635A1 US 2007007625 W US2007007625 W US 2007007625W WO 2007123635 A1 WO2007123635 A1 WO 2007123635A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
compressor
bearing
intermediate portion
angle
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.)
Ceased
Application number
PCT/US2007/007625
Other languages
English (en)
Inventor
Xioageng SU
Weihua Guo
Yong Cao
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.)
Copeland LP
Original Assignee
Emerson Climate Technologies Inc
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 US11/390,964 external-priority patent/US20070231170A1/en
Application filed by Emerson Climate Technologies Inc filed Critical Emerson Climate Technologies Inc
Priority to CN2007800109568A priority Critical patent/CN101410621B/zh
Publication of WO2007123635A1 publication Critical patent/WO2007123635A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0436—Iron
    • F05C2201/0439—Cast iron
    • F05C2201/0442—Spheroidal graphite cast iron, e.g. nodular iron, ductile iron

Definitions

  • the present disclosure relates to compressors, and more specifically to a drive shaft for a compressor.
  • a drive shaft experiences loads from a variety of sources including a compression mechanism being driven, counterweights, and rotor torque, as well as reaction loads from bearings. These loads cause bending of the drive shaft during operation of the compressor. Operating loads in scroll compressors rotate with the drive shaft. As such, the drive shaft typically has a first portion in tension and a second portion in compression during each revolution of the drive shaft. The stress at a specific location may vary, but there is not a reversal of tension and compression.
  • a compressor drive shaft may include a first bearing portion, a second bearing portion, and an intermediate portion disposed therebetween.
  • the intermediate portion may include a continuous, nonlinear, central axis in an unloaded state.
  • a compressor may include a shell, first and second bearing housings, a drive shaft, a motor, and a compression mechanism.
  • the first bearing housing may be contained within the shell and may have a first bearing contained therein.
  • the second bearing housing may be contained within the shell and may have a second bearing contained therein.
  • the drive shaft may have a first bearing portion, a second bearing portion, and an intermediate portion disposed therebetween.
  • the first bearing portion may be located within the first bearing and the second bearing portion may be located within the second bearing, the drive shaft may have a rotational axis generally parallel to bearing surfaces of the first and second bearings.
  • the intermediate portion may include a continuous, nonlinear, central axis in an unloaded state.
  • the motor may be contained within the shell and may be drivingly coupled to the drive shaft.
  • the compression mechanism may be in a driven engagement with the drive shaft.
  • a method of forming a compressor drive shaft may include supporting the drive shaft at a first location along a length thereof and applying a load that exceeds a yield point of the drive shaft to a second location along a length thereof to permanently deform the drive shaft a predetermined amount to a nonlinear form.
  • Figure 1 is a section view of a compressor
  • Figure 2 is a section view of an alternate compressor
  • Figure 3 is an exaggerated view of a compressor drive shaft under an operating load
  • Figure 4 is an exaggerated view of a pre-bent compressor drive shaft under no load
  • Figure 5 is a perspective view of a drive shaft bending apparatus
  • Figure 6 is a schematic illustration of the drive shaft bending apparatus of Figure 5 applying a load to the drive shaft
  • Figure 7 is a schematic illustration of an alternate drive shaft bending apparatus.
  • a compressor 10 is shown as a hermetic scroll refrigerant-compressor of the low-side type, i.e., where the motor and compressor are cooled by suction gas in the hermetic shell, as illustrated in the vertical section shown in Figure 1.
  • Compressor 10 may include a cylindrical hermetic shell 16, a compression mechanism 18, a main bearing housing 20, a motor assembly 22, a refrigerant discharge fitting 24, and a suction gas inlet fitting 26.
  • the hermetic shell 16 may house the compression mechanism 18, main bearing housing 20, and motor assembly 22.
  • Shell 16 may include an end cap 28 at the upper end thereof.
  • the refrigerant discharge fitting 24 may be attached to shell 16 at opening 30 in end cap 28.
  • the suction gas inlet fitting 26 may be attached to shell 16 at opening 32.
  • the compression mechanism 18 may be driven by motor assembly 22 and supported by main bearing housing 20.
  • the main bearing housing 20 may be affixed to shell 16 at a plurality of points in any desirable manner.
  • the motor assembly 22 may generally include a motor 34, a frame 36 and a drive shaft 38.
  • the motor 34 may include a motor stator 40 and a rotor 42.
  • the motor stator 40 may be press fit into frame 36, which may in turn be press fit into shell 16.
  • Drive shaft 38 may be rotatably driven by rotor 42.
  • Windings 44 may pass through stator 40.
  • Rotor 42 may be press fit on drive shaft 38.
  • a motor protector 46 may be provided in close proximity to windings 44 so that motor protector 46 will de-energize motor 34 if windings 44 exceed their normal temperature range.
  • Drive shaft 38 may include an eccentric crank pin 48 having a flat 49 thereon and one or more counter-weights 50 at an upper end 52.
  • Drive shaft 38 may include a first bearing portion 53 rotatably journaled in a first bearing 54 in main bearing housing 20 and a second bearing portion 55 rotatably journaled in a second bearing 56 in frame 36.
  • Drive shaft 38 may include an oil- pumping concentric bore 58 at a lower end 60.
  • Concentric bore 58 may communicate with a radially outwardly inclined and relatively smaller diameter bore 62 extending to the upper end 52 of drive shaft 38.
  • the lower interior portion of shell 16 may be filled with lubricating oil.
  • Concentric bore 58 may provide pump action in conjunction with bore 62 to distribute lubricating fluid to various portions of compressor 10.
  • Compression mechanism 18 may generally include an orbiting scroll 64 and a non-orbiting scroll 66.
  • Orbiting scroll 64 may include an end plate 68 having a spiral vane or wrap 70 on the upper surface thereof and an annular flat thrust surface 72 on the lower surface. Thrust surface 72 may interface with an annular flat thrust bearing surface 74 on an upper surface of main bearing housing 20.
  • a cylindrical hub 76 may project downwardly from thrust surface 72 and may include a journal bearing 78 having a drive bushing 80 rotatively disposed therein.
  • Drive bushing 80 may include an inner bore in which crank pin 48 is drivingly disposed.
  • Crank pin flat 49 may drivingly engage a flat surface in a portion of the inner bore of drive bushing 80 to provide a radially compliant driving arrangement, such as shown in assignee's U.S. Pat. No. 4,877,382, the disclosure of which is herein incorporated by reference.
  • Non-orbiting scroll 66 may include an end plate 82 having a non-orbiting spiral wrap 84 on lower surface 86 thereof. Non-orbiting spiral wrap 84 may form a meshing engagement with wrap 70 of orbiting scroll 64, thereby creating an inlet pocket 88, intermediate pockets 90, 92, 94, 96, and outlet pocket 98. Non-orbiting scroll 66 may have a centrally disposed discharge passageway 100 in communication with outlet pocket 98 and upwardly open recess 102 which may be in fluid communication with discharge fitting 24. A flip seal 104 may be located around recess 102 and abut shell 16, thereby providing sealed communication between discharge passageway 100 and discharge fitting 24, while allowing axial displacement of non-orbiting scroll 66 relative to shell 16. [0023] Non-orbiting scroll 66 may be mounted to main bearing housing
  • Non-orbiting scroll suspension system see assignee's U.S. Pat. No. 5,055,010, the disclosure of which is hereby incorporated herein by reference.
  • seals may also be included for sealing between the end cap 28 and non-orbiting scroll 66.
  • Figure 1 shows a first exemplary sealing member being a flip seal 104, as described in Assignee's U.S. Pat. No. 6,821 ,092, the disclosure of which is herein incorporated by reference.
  • Other seals, such as floating seals, may be used as well.
  • Axial pressure biasing may be included in compressor 10, as disclosed in Assignee's aforesaid U.S. Pat. No. 4,877,382.
  • a capacity modulation system may also be included in the system, as described in Assignee's aforesaid U.S. Pat. No. 6,821 ,092.
  • an Oldham coupling which may generally include a ring 108 having a first pair of keys 110 (one of which is shown) slidably disposed in diametrically opposed slots 112 (one of which is shown) in non-orbiting scroll 66 and a second pair of keys (not shown) slidably disposed in diametrically opposed slots in orbiting scroll 64.
  • Compressor 310 may include a cylindrical hermetic shell 316, a compression mechanism 318, a main bearing housing 320, a motor assembly 322, a refrigerant discharge fitting 324, and a suction gas inlet fitting 326.
  • the hermetic shell 316 may house the compression mechanism 318, main bearing housing 320, and motor assembly 322.
  • Shell 316 may include an end cap 328 at the upper end thereof and a transversely extending portion 329.
  • the refrigerant discharge fitting 324 may be attached to shell 316 at opening 330 in end cap 328.
  • the suction gas inlet fitting 326 may be attached to shell 316 at opening 332.
  • the compression mechanism 318 may be driven by motor assembly 322 and supported by main bearing housing 320.
  • the main bearing housing 320 may be affixed to shell 16 at a plurality of points in any desirable manner.
  • the motor assembly 322 may generally include a motor 334, a frame 336 and a drive shaft 338.
  • the motor 334 may include a motor stator 340 and a rotor 342.
  • the motor stator 340 may be press fit into frame 336, which may in turn be press fit into shell 316.
  • Drive shaft 338 may be rotatably driven by stator 340.
  • Windings 344 may pass through stator 340.
  • Rotor 342 may be press fit on drive shaft 338.
  • a motor protector 346 may be provided in close proximity to windings 344 so that motor protector 346 will de-energize motor 334 if windings 344 exceed their normal temperature range.
  • Drive shaft 338 may include an eccentric crank pin 348 having a flat 349 thereon and one or more counter-weights 350 at an upper end 352.
  • Drive shaft 338 may include a first bearing portion 353 rotatably joumaled in a first bearing 354 in main bearing housing 320 and a second bearing portion 355 rotatably journaled in a second bearing 356 in frame 336.
  • Drive shaft 338 may include an oil-pumping concentric bore 358 at a lower end 360. Concentric bore 358 may communicate with a radially outwardly inclined and relatively smaller diameter bore 362 extending to the upper end 352 of drive shaft 338.
  • the lower interior portion of shell 316 may be filled with lubricating oil.
  • Concentric bore 358 may provide pump action in conjunction with bore 362 to distribute lubricating fluid to various portions of compressor 310.
  • Drive shaft 338 may have a pre- bent configuration, as discussed below.
  • Compression mechanism 318 may generally include an orbiting scroll 364 and a non-orbiting scroll 366.
  • Orbiting scroll 364 may include an end plate 368 having a spiral vane or wrap 370 on the upper surface thereof and an annular flat thrust surface 372 on the lower surface.
  • Thrust surface 372 may interface with an annular flat thrust bearing surface 374 on an upper surface of main bearing housing 320.
  • a cylindrical hub 376 may project downwardly from thrust surface 372 and may include a journal bearing 378 having a drive bushing 380 rotatively disposed therein.
  • Drive bushing 380 may include an inner bore in which crank pin 348 is drivingly disposed.
  • Crank pin flat 349 may drivingly engage a flat surface in a portion of the inner bore of drive bushing 380 to provide a radially compliant driving arrangement, such as shown in Assignee's aforesaid U.S. Pat. No. 4,877,382.
  • Non-orbiting scroll 366 may include an end plate 382 having a non-orbiting spiral wrap 384 on lower surface 386 thereof.
  • Non-orbiting spiral wrap 384 may form a meshing engagement with wrap 370 of orbiting scroll 364, thereby creating an inlet pocket 388, intermediate pockets 390, 392, 394, 396, and outlet pocket 398.
  • Non-orbiting scroll 366 may have a centrally disposed discharge passageway 400 in communication with outlet pocket 398 and upwardly open recess 402 which may be in fluid communication via an opening 403 in partition 329 with a discharge muffler chamber 404 defined by end cap 328 and partition 329.
  • Non-orbiting scroll 366 has in the upper surface thereof an annular recess 405 having parallel coaxial side walls in which is sealingly disposed for relative axial movement an annular floating seal 407 which serves to isolate the bottom of recess 405 from the presence of gas under suction and discharge pressure so that it can be placed in fluid communication with a source of intermediate fluid pressure by means of a passageway 409.
  • a spring 411 may urge floating seal 407 upward to maintain a sealing engagement.
  • Non- orbiting scroll 366 is thus axially biased against orbiting scroll member 350 by the forces created by discharge pressure acting on the central portion of non- orbiting scroll 366 and those created by intermediate fluid pressure acting on the bottom of recess 405.
  • This axial pressure biasing, as well as various techniques for supporting non-orbiting scroll 366 for limited axial movement, are disclosed in much greater detail in Assignee's aforesaid U.S. Pat. No. 4,877,382.
  • Compressor 310 may use a dual pressure balancing scheme to axially balance non-orbiting scroll 366 with floating seal 407 being used to separate the discharge gas pressure from the suction gas pressure.
  • a solenoid valve 413 may be used to open and close a passageway 415 located within non-orbiting scroll 366. Passageway 415 extends from the bottom of recess 405 which is at intermediate pressure during operation of compressor 310 to the area of compressor 310 which contains suction gas at suction gas pressure.
  • an Oldham coupling which may generally include a ring 408 having a first pair of keys 410 (one of which is shown) slidably disposed in diametrically opposed slots 412 (one of which is shown) in non-orbiting scroll 366 and a second pair of keys (not shown) slidably disposed in diametrically opposed slots in orbiting scroll 364.
  • FIG. 3 a typical generally linear drive shaft 138 is shown housed in first and second bearings 54, 56.
  • the curvature of drive shaft 138 is exaggerated in Figure 3 to depict the deflection of drive shaft 138 during compressor operation.
  • Figure 3 depicts deflection of drive shaft 138 under a maximum load and illustrates a maximum tilt angle ⁇ , which is defined as the angle between a tangent line 118 and a rotational axis 116.
  • Drive shaft 138 may include a centerline 114 which may intersect rotational axis 116 at both the first and second bearings 54, 56.
  • Tangent line 118 is defined relative to centerline 114, and may be formed at the intersection between centerline 114 and rotational axis 116 in first bearing 54.
  • First bearing portion 153 may be generally disposed within first bearing 54 at an angle that generally approximates maximum tilt angle ⁇ relative to first bearing wall 120.
  • first radial side 122 of drive shaft 138 may always be under tension and a second radial side 124 of drive shaft 138 may always be under compression during operation of compressor 10.
  • First radial side 122 may be generally opposite second radial side 124.
  • first radial side 122 may be the side that crank pin flat 149 is disposed on.
  • drive shaft 38 may have a pre-bent configuration to compensate for the deflection occurring during compressor operation.
  • Figure 4 shows drive shaft 38 in an exaggerated form for illustrative purposes.
  • Drive shaft 38 may have a pre- bent nonlinear structure to account for some of the deflection that may occur mentioned above and shown in Figure 3.
  • Drive shaft 38 may have a continuous curvature along its entire length or merely a portion thereof. Additionally, a portion of drive shaft 38 may be linear, such as first bearing portion 53, and another portion may be nonlinear (or curved). The nonlinear portion may be centrally disposed along the length of drive shaft 38 (creating a central locus of curvature) or may be biased toward an end thereof (creating a non-central locus of curvature). [0038] As described above regarding drive shaft 138 in Figure 3, drive shaft 38 may include a centerline 214 and a rotational axis 216. Rotational axis 216 may be generally similar to rotational axis 116 in drive shaft 138.
  • Centerline 214 and rotational axis 216 may intersect at both the first and second bearings 54, 56.
  • a tangent line 218 to centerline 214 may be formed at the intersection between centerline 214 and rotational axis 216 in first bearing 54.
  • Angle ⁇ may be defined as the angle between tangent line 218 and rotational axis 216.
  • Drive shaft 38 may include a generally continuous curved body. More specifically, centerline 214 may form a generally continuous curve having first and second linear portions 226, 228 extending through first and second bearing portions 53, 55 and connected to one another by a generally smooth curved portion extending therebetween. Second linear portion 228 may extend along a portion of drive shaft 38 that rotor 42 is in a press fit engagement with.
  • drive shaft 38 may be bent in a direction generally opposite the direction of deflection during operation. Specifically, drive shaft 38 may be bent in such a manner that first bearing portion 53 may be disposed at an angle that generally approximates angle ⁇ relative to first bearing wall 120 when compressor 10 is in a non- operating state. Angle ⁇ may generally be between - ⁇ /4 and - ⁇ degrees. More specifically, angle ⁇ may generally be equal to approximately - ⁇ /2 degrees. While described in terms of -a, angle ⁇ may also be described in terms of + ⁇ , with the understanding that angle ⁇ may extend generally opposite angle ⁇ .
  • the pre-bent structure of drive shaft 38 may provide for a reduced diameter of drive shaft 38 relative to a typical linear drive shaft.
  • This reduced diameter may result in a reduced compressor bearing diameter, such as the diameter of first bearing 54.
  • This bearing diameter reduction may be characterized by an increase in the ratio of the distance between bearings (L) and bearing inner diameter (d). More specifically, the ratio (Ud) may generally be greater than or equal to 10.
  • An increased LVd ratio may provide for the use of additional lamination material for a given motor diameter, resulting in a more efficient motor.
  • first radial side 222 may be the side that crank pin flat 49 is disposed on.
  • first radial side 222 on drive shaft 38 may generally correspond to first radial side 122 on drive shaft 138 and second radial side 224 on drive shaft 38 may generally correspond to second radial side 124 on drive shaft 138.
  • maximum tilt angle ⁇ may be determined in a number of ways including advanced methods such as Finite Element Analysis (FEA). Once maximum tilt angle ⁇ has been determined, or at least approximated, angle ⁇ may be determined.
  • FEA Finite Element Analysis
  • Angle ⁇ may generally be between 0.06 and 0.28 degrees, depending on compressor operation. As such, angle ⁇ may generally be between -0.03 and -0.14 degrees when ⁇ is approximately equal to - ⁇ /2. Angle ⁇ may be more or less depending on the application, as loads may vary depending on the compressor application. For example, angle ⁇ may generally be less than or equal to -0.05 degrees (or greater than or equal to 0.05 degrees if expressed as a positive angle, as discussed above), or more specifically, less than or equal to -0.10 degrees (or greater than or equal to 0.10 degrees if expressed as a positive angle, as discussed above).
  • drive shaft 38 has been described in a scroll compressor environment, the application of a pre-bent drive shaft extends to other areas as well.
  • a pre-bent drive shaft may be beneficial for use in a vane- type compressor, various turbine machines, or any other apparatus having loads rotating together with a drive shaft.
  • Pre-bent drive shaft 38 may be formed from a variety of materials including carbon steel (including low carbon steel and case hardened steel), as well as ductile iron.
  • the pre-bent structure of drive shaft 38 may provide for use of materials with a lower modulus of elasticity than carbon steel, such as ductile iron.
  • Pre-bent drive shaft 38 may be formed in a variety of ways.
  • pre-bent drive shaft 38 may be a carbon steel shaft having a bending moment applied thereto.
  • a shaft bending apparatus 510 is shown engaged with drive shaft 38.
  • Figure 5 shows shaft bending apparatus 510 and drive shaft 38 before a bending moment is applied to drive shaft 38.
  • Figure 6 is a schematic illustration of shaft bending apparatus 510 applying a bending moment to drive shaft 38.
  • Shaft bending apparatus 510 may include a support member
  • Support member 512 may include first and second supports 516, 518 and load applying mechanism 514 may include a load control mechanism 520 and a hydraulic press head 522 having an adapter 524 fixed to an end thereof.
  • Drive shaft 38 may be supported at first and second ends by first and second supports 516, 518. More specifically, first and second bearing portions 53, 55 may be supported on first and second supports 516, 518.
  • Hydraulic press head 522 may be used to apply the bending moment, or load, through adapter 524.
  • Adapter 524 may be engaged with a central portion of drive shaft 38 between first and second supports 516, 518 and may localize load application for consistency.
  • Load control mechanism 520 may meter and control the load magnitude, and therefore the magnitude of the deformation of drive shaft 38.
  • a displacement transducer 526 may additionally be used to monitor deformation of drive shaft 38.
  • Displacement transducer 526 may be a linear variational displacement transducer (LVDT) and may be placed under drive shaft 38 to measure displacement thereof.
  • LVDT 526 measures displacement of drive shaft 38 iteratively until a desired permanent deformation is achieved. Accordingly, the minimum load required for permanent deformation is applied and released before permanent displacement is determined. Thus, if drive shaft 38 is determined to be under-deformed, the bending process is repeated by increasing the magnitude of the load applied to drive shaft 38 until the measured permanent deformation meets the desired permanent deformation.
  • LVDT linear variational displacement transducer
  • Drive shaft 38 may initially be in the form of a linear member as shown in Figure 5. Application of the bending moment is illustrated in Figure 6. When a bending moment is applied by load applying mechanism 514, as discussed above, the bending moment may increase linearly from the first and second supports 516, 518, where the bending moment is generally zero, to the location where adapter 524 is engaged with drive shaft 38, where the bending moment is at a maximum. The magnitude of the maximum bending moment applied to drive shaft 38 is selected such that a yield point of drive shaft 38 is exceeded and drive shaft 38 is permanently deformed around the location where adapter 524 is engaged therewith.
  • drive shaft 38 has a very low bending moment applied around supports 516, 518, there is no permanent deformation around first and second bearing portions 53, 55, resulting in first and second bearing portions 53, 55 and therefore first and second linear portions 226, 228 of centerline 214 maintaining their linearity while the central portion of drive shaft 38 is permanently deformed.
  • An alternate shaft bending apparatus 610 is shown in Figure 7.
  • Shaft bending apparatus 610 may be generally simitar to shaft bending apparatus 510 shown in Figures 5 and 6 with the exception of the location of the support ' s and load application, discussed below.
  • Shaft bending apparatus 610 may include first and second supports 616, 618 supporting drive shaft 38 and a load applying mechanism 614 engaged with drive shaft 38.
  • First support 616 may provide a bending location for drive shaft 38 and may be disposed between second support 618 and a load applying mechanism 614.
  • Load applying mechanism 614 may apply a load to an end of drive shaft 38 near first bearing portion 53.
  • the shaft bending apparatus of Figure 7 may be used to generate a pre-bent drive shaft 38 similar to that created by shaft bending apparatus 510. However, due to the arrangement of supports 616, 618 and load applying mechanism 614, a reduced load magnitude relative to that required by shaft bending apparatus 510 may be used to generate the same amount of permanent deformation of drive shaft 38.

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

Abstract

L'invention concerne un arbre d'entraînement pour compresseur ; il comprend une première partie de palier, une seconde partie de palier et une partie intermédiaire disposée entre les deux. La partie intermédiaire comprend un axe central, non linéaire, continu dans un état déchargé.
PCT/US2007/007625 2006-03-28 2007-03-28 Arbre d'entraînement pour compresseur Ceased WO2007123635A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2007800109568A CN101410621B (zh) 2006-03-28 2007-03-28 压缩机的驱动轴

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US11/390,964 2006-03-28
US11/390,964 US20070231170A1 (en) 2006-03-28 2006-03-28 Drive shaft for a compressor
US11/728,596 US7661939B2 (en) 2006-03-28 2007-03-26 Drive shaft for a compressor
US11/728,596 2007-03-26

Publications (1)

Publication Number Publication Date
WO2007123635A1 true WO2007123635A1 (fr) 2007-11-01

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PCT/US2007/007625 Ceased WO2007123635A1 (fr) 2006-03-28 2007-03-28 Arbre d'entraînement pour compresseur

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104747449A (zh) * 2013-12-30 2015-07-01 上海日立电器有限公司 一种制造装配双支撑压缩机的方法
WO2015149146A1 (fr) * 2014-04-01 2015-10-08 Whirlpool S.A. Agencement de palier radial dans un compresseur de réfrigération

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02153289A (ja) * 1988-12-05 1990-06-12 Hitachi Ltd ロータリ圧縮機
JPH07301177A (ja) * 1994-05-02 1995-11-14 Toyota Autom Loom Works Ltd 両頭斜板式圧縮機
US5983738A (en) * 1996-03-22 1999-11-16 Mouvex Eccentric sealed rotary drive device, particularly for a positive displacement pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02153289A (ja) * 1988-12-05 1990-06-12 Hitachi Ltd ロータリ圧縮機
JPH07301177A (ja) * 1994-05-02 1995-11-14 Toyota Autom Loom Works Ltd 両頭斜板式圧縮機
US5983738A (en) * 1996-03-22 1999-11-16 Mouvex Eccentric sealed rotary drive device, particularly for a positive displacement pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104747449A (zh) * 2013-12-30 2015-07-01 上海日立电器有限公司 一种制造装配双支撑压缩机的方法
WO2015149146A1 (fr) * 2014-04-01 2015-10-08 Whirlpool S.A. Agencement de palier radial dans un compresseur de réfrigération

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