EP1321679A1 - Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable - Google Patents

Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable Download PDF

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Publication number
EP1321679A1
EP1321679A1 EP03004927A EP03004927A EP1321679A1 EP 1321679 A1 EP1321679 A1 EP 1321679A1 EP 03004927 A EP03004927 A EP 03004927A EP 03004927 A EP03004927 A EP 03004927A EP 1321679 A1 EP1321679 A1 EP 1321679A1
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EP
European Patent Office
Prior art keywords
housing
centerline
diffuser
backlash
rack gear
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.)
Granted
Application number
EP03004927A
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German (de)
English (en)
Other versions
EP1321679B1 (fr
Inventor
Edward G. Gallagher
Vishnu M. Sishtla
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
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 US08/907,319 external-priority patent/US5895204A/en
Priority claimed from US08/907,288 external-priority patent/US5988977A/en
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP1321679A1 publication Critical patent/EP1321679A1/fr
Application granted granted Critical
Publication of EP1321679B1 publication Critical patent/EP1321679B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/002—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to centrifugal compressors in general and in particular to a drive positioning mechanism and a backlash adjustment mechanism for a variable pipe diffuser for a centrifugal compressor.
  • variable width diffuser in conjunction with fixed diffuser guide vanes.
  • variable width vaned diffusers wherein the diffuser vanes are securely affixed, as by bolting to one of the diffuser walls.
  • the vanes are adapted to pass through openings formed in the other wall thus permitting the geometry of the diffuser to be changed in response to changing load conditions.
  • variable geometry pipe diffuser which may also be termed a split-ring pipe diffuser
  • split-ring pipe diffuser splits the diffuser into a first, inner ring and a second outer ring.
  • the inner and outer rings have complementary inlet flow channel sections formed therein. That is, each inlet flow channel section of the inner ring has a complementary inlet flow channel section formed in the outer ring.
  • the inner ring and outer ring are rotatable respective one another. The rings are rotated to improve efficiency for varying pressure levels between a fully open position and a partially closed position. In the partially closed position the misalignment of the exit pipes of the diffuser causes an increase in noise. Rotation of the rings past an optimum design point results in excessive noise and efficiency degradation.
  • split ring diffusers Another problem with split ring diffusers is premature part wear. Lubricants are generally not used within the gas flow regions of centrifugal compressors to preclude contamination of the gases. The dynamic loads imposed upon the split ring diffuser by the gas flow exiting the impeller cause wear in the components of the diffuser to be accelerated by the absence of lubricating oil.
  • the drive system for accurately positioning the rings relative to one another must, among other things, be rigid to avoid any fretting of components. Because of circumferential loading on the rings there is a propensity for the inner ring to oscillate relative to the outer ring which could cause compressor instability, part wear and could adversely affect efficiency. This causes several problems that need to be overcome.
  • a drive system is needed that is capable of preventing the relative movement between the inner and outer rings.
  • a bearing concept is also needed which would allow for the relative rotation of the two rings and also be capable of withstanding the circumferential and thrust loads while maintaining tight geometric tolerances between the rings. There is also a need to provide a positioning system that includes positive minimum and maximum stops to avoid unnecessary noise and efficiency degradation as well as simple field retrofit. In addition, there is a need for the drive and bearing systems have a long operating life and be easy to install and adjust properly.
  • the present invention relates to a variable geometry pipe diffuser for a centrifugal compressor. More specifically the present invention relates to a drive positioning mechanism and an associated backlash adjustment mechanism for use in a variable geometry pipe diffuser for a centrifugal compressor.
  • a rack gear is attached to the inner ring of a variable pipe diffuser of the present invention.
  • a pinion gear is attached to a rotation drive means mounted to the casing of a centrifugal compressor in meshing arrangement with the rack gear.
  • the rotational drive means is operated to rotate the inner ring relative to the outer ring between a position where the diffuser pipes are fully open and a position where the diffuser pipes are partially closed.
  • the drive means is capable of aligning the pipes of the diffuser to a plurality of positions between the fully open and partially closed positions.
  • a travel limiter is also provided to positively limit the travel of the inner ring at the fully open and the partially closed positions.
  • the backlash adjustment mechanism has a housing concentric about a first centerline and a bore therethrough concentric about a second centerline.
  • the pinion gear is mounted to a drive shaft passing through the bore.
  • the housing is rotatably mounted to the casing.
  • the housing of the present invention is rotatably operable about the second centerline to adjust
  • a centrifugal compressor 10 as part of an HVAC system (not shown) having an impeller 12 for accelerating refrigerant vapor to a high velocity, a diffuser 14 for decelerating the refrigerant to a low velocity while converting kinetic energy to pressure energy, and a discharge plenum in the form of a collector 16 to collect the discharge vapor for subsequent flow to a condenser.
  • Power to the impeller 12 is provided by an electric motor (not shown) which is hermetically sealed in the other end of the compressor and which operates to rotate a high speed shaft 19.
  • the refrigerant enters the inlet opening 29 of the suction housing 31, passes through the blade ring assembly 32 and the guide vanes 33, and then enters the compression suction area 23 which leads to the compression area defined on its inner side by the impeller 12 and on its outer side by the housing 34. After compression, the refrigerant then flows into the diffuser 14, the collector 16 and the discharge line (not shown).
  • a variable geometry pipe diffuser 14 includes a first, inner ring 40 and a second outer ring 42, a ring support mechanism 35, and a positioning drive mechanism 121.
  • the inner and outer rings have complementary flow channel sections 44 and 46 formed therein. That is, each flow channel section 44 of the inner ring 40 has a complementary channel section 46 formed in outer ring 42.
  • Inner ring 40 and outer ring 42 are rotatable with respect to one another. In a preferred embodiment, inner ring 40 rotates circumferentially within a stationary outer ring 42.
  • Rings 40 and 42 are adjustable between a first fully open position, as illustrated in Fig. 3, wherein complementary channel sections are aligned and a maximum amount of fluid passes through inner and outer rings 40 and 42, and a second, partially closed position, as illustrated in Fig. 4, wherein complementary channels are misaligned and flow through the channel sections 44 and 46 is restricted.
  • a ring support mechanism 35 according to an embodiment of the present invention is shown.
  • the embodiment shown illustrated the use of three such mechanisms spaced circumferentially equidistant about the diffuser.
  • the ring support mechanism of the present invention includes an inner bearing slot 41 and a cutout 43 disposed in inner ring 40, a roller assembly 54, a roller axle assembly 36 and an outer bearing slot 45 disposed in the outer ring.
  • the roller assembly as shown in Fig. 8 includes a roller 55 having an outer bearing surface 56, and a pair of thrust bearing surfaces 57.
  • the axle assembly as shown in Figs. 6 - 7 includes an axle 37 and an axle bolt 39.
  • axle 37 includes a hex head 38 and an axle body 47, an axle body centerline 48, an axle bore 49 and an axle bore centerline 50.
  • the axle 39 includes a pair of shoulders 73, 74 concentric with axle bore centerline 50.
  • split ring diffusers Another problem with split ring diffusers is premature part wear.
  • Lubricants are generally not used within the gas flow regions of centrifugal compressors to preclude contamination of the gases.
  • the dynamic loads imposed upon the split ring diffuser by the gas flow exiting the impeller cause wear in the components of the diffuser to be accelerated by the absence of lubricating oil. Due to the non-availability of lubricating oils in most compressors it is usually necessary to take steps to minimize friction and fretting wear. Accordingly, in certain embodiments of the present invention and as described herein below, component interfaces are hard coated, parts are manufactured from ultra high molecular weight plastic materials, the ring assemblies are preloaded and backlash is eliminated from the gears of the positioning drive system.
  • the outer ring 42 is stationary with respect to the suction housing and three sets of ring support mechanisms 35 are installed into the outer ring by positioning the roller assembly 54 within the bearing slot 45 of the outer ring, passing the axle through the mounting hole 58 and the roller assembly and then installing the axle bolt 39 through the axle and loosely threading the axle bolt 39 into threaded holes 59 in the outer ring.
  • the inner ring 40 is installed inside of the outer ring with the cutouts 43 of the inner ring circumferentially aligned with the bearing slot 45 and the roller assemblies 35 and then rotating the inner ring clockwise as shown in Fig. 7 to position the roller assemblies within the bearing slot 41.
  • the ring support mechanisms are employed to properly center and position the inner ring by rotating the axle through the use of a wrench placed on the hex head 38.
  • the axle body centerline 48, on which the roller 55 is mounted is offset from axle bore centerline 50, which is concentric with the shoulders 73, 74, by .021 inches.
  • the rotation of hex head 38 causes the roller assembly to rotate about the shoulders within the outer ring and causes the roller assembly to be radially displaced relative to the outer ring.
  • the hex head is further rotated to preload the outer bearing surface 56 of the roller assemblies against the inner ring.
  • the axle bolt 39 is then tightened.
  • the preload conditioned is preferred because it prevents the inner ring from movement due to tangential and circumferential loads.
  • the roller 55 and the inner ring 40 are aluminum and both the outer bearing surface 56 and the inner bearing slot 41 are hardened to prevent wear.
  • the roller assemblies restrain movement of the rings in the axial direction due to thrust loads by positioning the thrust bearing surfaces 57 within the hardened inner bearing slot 41 and the relatively soft outer bearing slot 45.
  • the thrust bearing surface 57 of the roller assembly must allow for the rotation of the inner and outer rings and at the same time withstand the thrust loads produced by the compressor.
  • the thrust bearing surface 57 is manufactured from ultra high molecular weight plastic having a low coefficient of friction of 0.16 and a hardness of 64 on the Shore D scale.
  • the plastic thrust bearing surfaces prevent contact between the hardened roller and the soft outer bearing slot and are utilized to carry the thrust loads of the compressor and to adjust axial tolerances of the inner ring.
  • FIG. 16 Another embodiment of the present invention for limiting and precluding axial movement of the inner ring relative to the outer ring is shown in Fig. 16.
  • an axial restraint system 90 comprising a threaded shaft 91, a threaded mounting hole 92, a bearing pad 93, a lock nut 94, a hex head 95, and a recess 96.
  • the axial restraint mechanism 90 is installed such that the bearing pad 93 is positioned in the recess 96.
  • the bearing pad positioned within the recess allows clearance for the shroud 34 to be mounted to outer ring 42 without accidental contact of the bearing pads with the inner ring..
  • the threaded shaft 91 is rotated to bring the bearing pad in contact with the inner ring.
  • the mechanism is releasably fastened by tightening lock nut 94.
  • the bearing pad is manufacture from an ultra high molecular weight plastic material.
  • An embodiment of the present invention includes six such axial restraint mechanisms positioned circumferentially equally spaced about the inner ring.
  • a positioning drive mechanism 121 for rotating inner ring 40 circumferentially within outer ring 42 is described with reference Fig. 10.
  • Outer ring 42 has fixedly attached thereto rack gear 123 which extends radially outwardly from outer ring 42.
  • rack gear 123 In gearing relation with rack gear 123 is pinion gear 124 which is driven via pinion axle 126 by actuator 128.
  • Actuator 128 is selected and controlled to effect movement of inner ring 40 in relation to outer ring 42 between a first fully open position and a second partially closed position and any number of intermediate positions therebetween.
  • Axle 126 is housed in a containment housing 130 which hermetically seals axle 126 from compressor interior 132 and which prevents leakage of fluid out of compressor 10 through containment housing 130.
  • the tangential and circumferential loading on the rings by the refrigerant flow within the diffuser causes the inner ring to have the propensity to chatter back and forth within the outer ring. Excess movement or chattering of the inner ring would cause the rack gear 123 and the pinion gear 124 to fret and also cause other parts to wear. Preloading the inner ring via the roller assemblies as discussed herein earlier prevents movement of the inner ring as well as chattering under normal operating conditions. In cases of abnormal conditions, such as operating in a surge, a secondary mechanism is needed to prevent motion of the inner ring.
  • the present invention provides for a drive mounting system to prohibit adverse movement and chattering of the inner ring by preventing the backlash between the segment gear and the pinion gear via adjustment of the relative center positions of the pinion gear and the rack gear utilizing the axle containment housing 130.
  • the axle housing outer surface 125 is concentric about housing centerline 127 and housing bore 129 is concentric about housing bore centerline 131.
  • the housing centerline 127 and the housing bore centerline 129 are offset by .060 inches. Referring to Fig. 11 there is shown wrench flats 135 and adjustment slots 134 of the positioning drive mechanism.
  • the backlash between the rack gear 123 and the pinion gear 124 is removed by rotating the drive positioning mechanism by placing a wrench (not shown) across wrench flats 135. Once minimal backlash is achieved the positioning drive mechanism is fixed in place by the tightening of cap screws 133. Once the backlash is eliminated the tendency for the inner ring to move is discharged directly by the actuator through the gear system.
  • the flow of fluid through diffuser 14 in a second partially closed position in relation to the fully open position flow rate is determined by the ratio of the minimum cross-sectional area of a flow channel of a diffuser in a partially closed position to the minimum cross-sectional area of a flow channel (defined by complementary channel sections 44 and 46) in a fully open position.
  • This minimum flow channel area known as the "throat area” will generally be determined by the smallest diameter of the flow passage 52 of the inner ring channel 44 when diffuser 14 is in a fully open position, and will be controlled by the width 53 at the interface between the inner and outer rings 40 and 42 when diffuser 14 is in a second partially closed position. For example, if a diffuser channel has a minimum area (throat area) of 1/8 sq. in.
  • the volumetric flow rate of fluid through a diffuser in the partially closed position will be about 50% of the flow rate as in the fully open position.
  • the flow rate of fluid through compressor 10 when diffuser 14 is in a second, partially closed position will generally be between about 10% and 100% of the flow rate of fluid through compressor 10 when diffuser is in the first fully open position.
  • a second partially closed position (Fig. 4) at least about 10% the volume of flow as in the fully open position should flow through diffuser 14 so as to prevent excessive thermodynamic heating, excessive noise and a degradation in the efficiency of the compressor.
  • the amount of relative rotation between the two ring sections should be limited to an amount of rotation necessary to effect a second partially closed position.
  • the rings should not be adjustable to completely close off a flow of fluid therebetween. The degree of allowable rotation between the two rings is determined by the desired flow between the rings in a fully closed position, and the number and volume of inlet flow channel sections 44, 46 in the ring sections 40 and 42 in relation to the volume of the ring sections 40 and 42.
  • R 2 defines the radius of the impeller tip
  • R 3 defines the outside radius of inner ring 40
  • R 4 defines the outside radius of outer ring.
  • FIG. 5 and 12 an embodiment of the present invention is shown having a mechanism to provide positive positioning of the inner ring corresponding to a first fully open position and a second partially closed position.
  • Cavity 137 is machined in outer ring 42 to accommodate rack gear 123.
  • Rack gear 123 is accurately mounted to inner ring 40 in a tongue and groove fashion wherein the rack gear is provided with a circumferential groove 143 adapted to receive tongue section 139 of inner ring 40.
  • To determine the fully opened position the inner ring is positioned within the outer ring and the rings are rotated relative to one another until flow passages 52 are fully aligned with outer flow channels 46.
  • the rack gear is mounted to the inner ring with gear face 145 in contact with full open stop 140 of cavity 137.
  • Bolts (not shown) are then installed through gear mounting holes 142 and securely and tightened into threaded holes 138 in the inner ring.
  • the rack gear and the cavity are sized to provide for a predetermined amount of closure of the pipe diffuser.
  • a is sized such that difference between the rack gear angular width and the cavity provide for a 10% open position. In this example the required travel of the rack gear is 10 degrees, the rack gear angular width is 35 degrees and the corresponding cavity angular width is 45 degrees.
  • a positive stop is created between the rack gear and the cavity to accurately and repeatably position the rings at points corresponding to a fully open position and a partially closed position.
  • the positive stops also allow for field retrofit of actuator 128 without the need to adjust the position of the inner and outer rings.
  • FIG. 5 showing a performance diagram for a compressor having a variable pipe diffuser according to the invention integrated therein.
  • the performance diagram of Fig. 5 includes a plurality of performance plots 60, 62, 64, 66 and 68, each corresponding to a discreet positioning between inner and outer ring sections 40 and 42.
  • Each performance plot, e.g. 60 is characterized by a surge point, e.g. 70, which is the point of maximum available pressure. Operating a compressor at a flow rate at or below the surge point will likely result in a surge condition, as discussed in the Background of the Invention section herein.
  • plot 60 may correspond, for example, to a first, fully open position
  • plot 62 may correspond to an intermediate 2 degree partially closed position
  • plot 64 may correspond to an intermediate 4 degree partially closed position
  • plot 68 may correspond to a maximum 8 degree partially closed position.
  • adjusting ring sections 40 and 42 toward a closed position has the effect of adjusting the surge point e.g. 70, 72 in a performance plot for a compressor toward a lower flow rate.
  • a surge condition can be avoided during periods of low flow demand by adjusting diffuser rings 40 and 42 toward a closed position.
  • surge point pressure available from compressor 10 remains essentially stable when diffuser rings 40 and 42 are adjusted toward a closed position.
  • an operating condition requiring a low flow rate and high compressor pressure can be satisfied by adjusting diffuser rings 40 and 42 toward a closed position.
  • An operating condition requiring a low flow rate and a high pressure ratio relative to the full load operating pressure ratio (e.g. 90% of full load) is common in the case where there is a large difference (e.g. about 50° F or more) between the ambient air temperature and indoor temperature, but occasional light loading in a building being cooled.
  • a relatively high compressor pressure ratio (e.g. above about 2.5) is required by the refrigerant saturation pressures corresponding to the condenser, and evaporation temperatures, but only a reduced flow rate e.g. 25% of full load is needed to remove the heat generated within the building.
  • Fig. 7 shows a performance diagram for a compressor having both adjustable guide vanes and a variable pipe diffuser in accordance with the invention. It is seen that efficiency of a compressor can often be optimized by combining an adjustment of guide vanes 33 with an adjustment of diffuser rings 40 and 42.
  • dash curves 111, 112, 113, 114, 115, and 116 show performance plots for a compressor having a variable diffuser in a fully open position for various positioning of inlet guide vanes 33
  • solid curves 101, 102, 103, 104 and 105 show performance plots for a compressor having partially closed (here, there is about 40% of original flow rate in the closed position) diffuser rings at various guide vane positioning.
  • a compressor operates at optimum efficiency when operating at the "knee" (e.g. 81 at Fig. 6) of the performance plot characterizing performance of the compressor.
  • the operating condition requiring, for example, a pressure of about 0.7 maximum, and a flow rate of about 0.3 maximum would be most efficiently satisfied by a compressor operating in accordance with plot 104, realized by adjusting diffuser rings 40 and 42 to a closed position and by adjusting guide vanes 33 to a 10 degree position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Gears, Cams (AREA)
EP03004927A 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable Expired - Lifetime EP1321679B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US907319 1997-08-06
US08/907,319 US5895204A (en) 1997-08-06 1997-08-06 Drive positioning mechanism for a variable pipe diffuser
US907288 1997-08-06
US08/907,288 US5988977A (en) 1997-08-06 1997-08-06 Backlash adjustment mechanism for variable pipe diffuser
EP98630040A EP0896157B1 (fr) 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP98630040A Division EP0896157B1 (fr) 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable

Publications (2)

Publication Number Publication Date
EP1321679A1 true EP1321679A1 (fr) 2003-06-25
EP1321679B1 EP1321679B1 (fr) 2004-10-06

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EP03004927A Expired - Lifetime EP1321679B1 (fr) 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable
EP98630040A Expired - Lifetime EP0896157B1 (fr) 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable

Family Applications After (1)

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EP98630040A Expired - Lifetime EP0896157B1 (fr) 1997-08-06 1998-07-31 Mécanisme de positionnement avec réglage de jeu pour diffuseur tubulaire variable

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EP (2) EP1321679B1 (fr)
JP (1) JP3091179B2 (fr)
KR (1) KR100297572B1 (fr)
CN (1) CN1279300C (fr)
AU (1) AU737988B2 (fr)
BR (1) BR9803641A (fr)
DE (2) DE69818589T2 (fr)
ES (2) ES2203914T3 (fr)
MY (2) MY123718A (fr)
TW (1) TW402666B (fr)

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WO2005035992A3 (fr) * 2003-10-10 2005-11-24 York Int Corp Systeme et procede de commande de la stabilite dans un compresseur centrifuge
WO2009058975A1 (fr) * 2007-10-31 2009-05-07 Johnson Controls Technology Company Système de commande
US7905102B2 (en) 2003-10-10 2011-03-15 Johnson Controls Technology Company Control system
EP2505849A1 (fr) * 2011-03-28 2012-10-03 Siemens Aktiengesellschaft Procédé et système pour l'optimisation d'énergie d'un compresseur centrifuge

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JPH0683160U (ja) * 1993-04-30 1994-11-29 志 祥 侯 半田ワイヤ送給装置
JP2003106289A (ja) * 2001-10-01 2003-04-09 Kondo Kogyo Kk 多段式遠心ファン
FR2878912B1 (fr) * 2004-12-07 2008-08-15 Peugeot Citroen Automobiles Sa Ensemble de suralimentation pour moteur a combustion interne et vehicule correspondant
JP4952465B2 (ja) * 2007-09-13 2012-06-13 株式会社Ｉｈｉ パイプディフューザ式遠心圧縮機
US9353765B2 (en) 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
US8052384B2 (en) * 2008-06-17 2011-11-08 Hamilton Sundstrand Corporation Centrifugal pump with segmented diffuser
CN103158024B (zh) * 2011-12-19 2015-04-22 沈阳理工大学 一种调整齿轮齿条传动间隙的机构
AU2013376868B2 (en) 2013-01-31 2017-03-30 Danfoss A/S Centrifugal compressor with extended operating range
CN104421209B (zh) * 2013-08-26 2017-02-08 珠海格力电器股份有限公司 调节器结构及离心式压缩机
EP3325816B1 (fr) 2015-07-22 2019-08-28 Carrier Corporation Anneau de restriction de diffuseur
WO2017135949A1 (fr) 2016-02-04 2017-08-10 Danfoss A/S Régulation de pompage active dans des compresseurs centrifuges avec injection à microjet
KR102655373B1 (ko) 2017-09-25 2024-04-04 존슨 컨트롤스 테크놀러지 컴퍼니 원심 압축기용 2 부품 분할 스크롤
KR20210014450A (ko) * 2019-07-30 2021-02-09 현대자동차주식회사 가변 지오메트리 터보차저
CN112780612A (zh) * 2021-01-29 2021-05-11 安徽应流航空科技有限公司 一种扩压器定位固定结构

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WO2005035992A3 (fr) * 2003-10-10 2005-11-24 York Int Corp Systeme et procede de commande de la stabilite dans un compresseur centrifuge
US7356999B2 (en) 2003-10-10 2008-04-15 York International Corporation System and method for stability control in a centrifugal compressor
US7905102B2 (en) 2003-10-10 2011-03-15 Johnson Controls Technology Company Control system
WO2009058975A1 (fr) * 2007-10-31 2009-05-07 Johnson Controls Technology Company Système de commande
US8567207B2 (en) 2007-10-31 2013-10-29 Johnson Controls & Technology Company Compressor control system using a variable geometry diffuser
EP2505849A1 (fr) * 2011-03-28 2012-10-03 Siemens Aktiengesellschaft Procédé et système pour l'optimisation d'énergie d'un compresseur centrifuge

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AU737988B2 (en) 2001-09-06
CN1538072A (zh) 2004-10-20
EP0896157A1 (fr) 1999-02-10
DE69818589D1 (de) 2003-11-06
BR9803641A (pt) 1999-09-28
KR19990023377A (ko) 1999-03-25
DE69826901T2 (de) 2006-03-09
ES2225802T3 (es) 2005-03-16
AU7877598A (en) 1999-02-18
CN1279300C (zh) 2006-10-11
JPH11132197A (ja) 1999-05-18
EP1321679B1 (fr) 2004-10-06
MY121001A (en) 2005-12-30
MY123718A (en) 2006-05-31
KR100297572B1 (ko) 2001-10-27
ES2203914T3 (es) 2004-04-16
DE69818589T2 (de) 2004-08-05
DE69826901D1 (de) 2004-11-11
TW402666B (en) 2000-08-21
EP0896157B1 (fr) 2003-10-01
JP3091179B2 (ja) 2000-09-25

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