EP0012895B1 - Centrifugal vapor compressor and a diffuser control therefor - Google Patents

Centrifugal vapor compressor and a diffuser control therefor Download PDF

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Publication number
EP0012895B1
EP0012895B1 EP79104971A EP79104971A EP0012895B1 EP 0012895 B1 EP0012895 B1 EP 0012895B1 EP 79104971 A EP79104971 A EP 79104971A EP 79104971 A EP79104971 A EP 79104971A EP 0012895 B1 EP0012895 B1 EP 0012895B1
Authority
EP
European Patent Office
Prior art keywords
throttle
annular recess
throttling
housing
maintaining
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.)
Expired
Application number
EP79104971A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0012895A1 (en
Inventor
Phiroze Bandukwalla
Howard W. Kirtland
Gordon L. Mount
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 US05/973,404 external-priority patent/US4257733A/en
Priority claimed from US05/973,405 external-priority patent/US4219305A/en
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP0012895A1 publication Critical patent/EP0012895A1/en
Application granted granted Critical
Publication of EP0012895B1 publication Critical patent/EP0012895B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
    • 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
    • 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
    • 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
    • F05D2250/51—Inlet
    • 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

  • This invention relates to centrifugal vapor compressors, and more particularly to a diffuser control for controlling vapor flow through a diffuser passage of a centrifugal vapor compressor.
  • the compressor enters what is known as surge, wherein there are periodic complete flow reversals in the diffuser passage, destroying the efficiency of the machine and endangering the integrity of the machine elements.
  • surge wherein there are periodic complete flow reversals in the diffuser passage, destroying the efficiency of the machine and endangering the integrity of the machine elements.
  • One of the most accepted and successful modifications has been the addition of guide vanes in the inlet of the compressor to vary the flow direction and quantity of entering vapor.
  • Another widely known modification has been to vary diffuser configuration in response to the load on the compressor. Commonly, this is done by means of a diffuser control ring which moves laterally across the diffuser passage to throttle vapor flow therethrough (see, for example, US-A-3 426 964).
  • Prior art variable diffuser control rings have been generally controlled by a mechanism arranged to locate and hold the control ring at any position between a full opened and a full closed position.
  • Such control mechanisms are typically relatively expensive, often involving fairly complex mechanical and/or pneumatic components. Further, because of the complex components, the manufacture and installation of the diffuser ring control mechanisms are often difficult and time consuming tasks requiring expensive skilled manual labor.
  • continuously variable diffuser control rings often provide excellent results, it has been learned that very satisfactory results can be achieved with a diffuser control ring which has a limited number of discrete, spaced throttling positions. While obtaining these very satisfactory results, a discretely variable diffuser control, in accordance with the present invention, is, at the same time, much simpler than prior art diffuser controls. This simplicity facilitates and reduces the cost of construction, installation, and maintenance of the diffuser control and improves the reliability thereof.
  • a diffuser control for controlling vapor flow through a diffuser passage comprising an annular recess defined by a housing of the diffuser passage and in communication therewith; a throttle supported for movement within the recess and the diffuser passage between maximum and minimum throttling positions, and including a front, radially and annularly extending surface, an outside axial surface extending rearward from an outside radial edge of the front surface and spaced from the housing to facilitate movement of the throttle and an inside axial surface extending rearward from an inside radial edge of the front surface and spaced from the housing to facilitate movement of the throttle; a spring means supported by the housing and urging the throttle toward the maximum throttling position; a low pressure conduit for connecting the annular recess to a low pressure source; a seal for retarding vapor flow from a higher pressure side of the throttle to a lower pressure side thereof when the throttle is in the minimum throttling position; and a valve for regulating vapor flow through the low pressure conduit and including
  • a centrifugal vapor compressor comprising a housing defining an inlet passage and a diffuser passage, an impeller rotatably mounted in the housing between the inlet and diffuser, an annular recess defined by the housing and in communication with the diffuser, a throttle supported for movement within the annular recess and the diffuser passage between maximum and minimum throttling positions, and including a front, radially and annularly extending surface, an outside axial surface extending rearward from an outside radial edge of the front surface and spaced from the housing to facilitate movement of the throttle, and an inside axial surface extending rearward from an inside radial edge of the front surface and spaced from the housing to facilitate movement of the throttle, spring means supported by the housing and urging the throttle toward the maximum throttling position, a low pressure conduit for connecting the annular recess to a low pressure source, a seal for retarding vapor flow from a higher pressure side of the throttle to a lower pressure side thereof when the
  • a diffuser control for controlling vapor flow through a diffuser passage comprising an annular recess defined by a housing of the diffuser passage and in communication therewith, a throttle supported for movement within the recess and the diffuser passage between minimum and maximum throttling positions, first spring means supported by the housing for urging the throttle toward the maximum throttling position, a conduit for connecting the annular recess to a low pressure source, a first seal for retarding vapor flow from a higher pressure side of the throttle to a lower pressure side thereof when the throttle is in the minimum throttling position, and a valve for regulating vapor flow through the conduit and including a first position for maintaining a low pressure in the annular recess and a first pressure difference across the throttle for maintaining the throttle in the minimum throttling position, and a second position for maintaining a high pressure in the annular recess wherein the first spring means maintains the throttle in the maximum throttling position, characterized in that the throttle has
  • a centrifual vapor compressor comprising a housing defining an inlet passage and a diffuser passage, an impeller rotatably mounted in the housing between said inlet and diffuser, an annular recess defined by the housing and in communication with the diffuser, a throttle supported for movement within the annular recess and the diffuser passage between minimum and maximum throttling positions, first spring means supported by the housing for urging the throttle toward the maximum throttling position, a conduit for connecting the annular recess to a low pressure source, a first seal for retarding vapor flow from a higher pressure side of the throttle to a lower pressure side thereof when the throttle is in the minimum throttling position, and a valve for regulating the vapor flow through the conduit including a first position for maintaining a low pressure in the annular recess and a pressure difference across the throttle for maintaining the throttle in the minimum throttling position, and a second position for maintaining a high pressure in the annular recess wherein
  • compressor 10 constructed according to a first embodiment of the present invention.
  • compressor 10 is of the well-known centrifugal type wherein vapor to be compressed is induced to flow in an axial direction into a vaned impeller connected to a suitable driver for imparting rotary motion thereto.
  • vapor to be compressed is induced to flow in an axial direction into a vaned impeller connected to a suitable driver for imparting rotary motion thereto.
  • compressor 10 includes housing 12 with inlet passage 14 and diffuser passage 16 formed therein. Only portions of housing 12 are shown, it being understood that such a construction is conventional in equipment of the kind under consideration.
  • Impeller 18 affixed to shaft 20 by nut 22 is provided in housing 12 between inlet passage 14 and diffuser passage 16.
  • Inlet guide vanes 24 journaled for rotation in housing 12 are positioned about inlet passage 14 to control the direction and quantity of vapor flow therethrough.
  • Diffuser control, referenced generally as 26, is provided for controlling vapor flow through diffuser passage 16.
  • Diffuser control 26 comprises, generally, annular recess 28 defined by housing 12 and in communication with diffuser passage 16, and diffuser restriction means such as annular control ring 30.
  • Control ring 30 is supported for movement within annular recess 28 and diffuser passage 16 between an open position, shown in full lines in Figure 1, and a throttling position, shown in broken lines in Figure 1. In the throttling position, control ring 30 throttles vapor flow through diffuser passage 16; and, preferably, in the open position, the control ring allows an unrestricted flow of vapor through the diffuser passage.
  • Urging means 32 is provided for urging control ring 30 toward the throttling position.
  • the urging means includes resilient means such as a plurality of springs 32 positioned within recess 28.
  • Springs 32 are preferably equally spaced about the circumference of control ring 30, forming a ring of springs with a radius equal to the radius of the control ring.
  • Stop means 34 limits movement of the control ring at the throttling position for preventing the control ring from completely restricting vapor flow through diffuser passage 16.
  • stop means 34 includes a surface of housing 12. More specifically, as control ring 30 moves forward, from left to right as viewed in Figure 1, and reaches the throttling position, flange 36 of the control ring abuttingly engages surface 34 and this abutting contact prevents further forward movement of the control ring.
  • Diffuser control 26 further comprises conduit means 37 and valve means 39.
  • Conduit means 37 connects annular recess 28 to a pressure source having a pressure less than the pressure in diffuser passage 16, and valve means 39 regulates vapor flow through the conduit means.
  • conduit means 37 includes low pressure conduit 38 which connects annular recess 28 to, for example, an inlet line of compressor 10
  • valve means 39 includes valve 40 located in the low pressure conduit.
  • valve 40 includes a first position for maintaining control ring 30 in the open position and a second position for maintaining the control ring in the throttling position.
  • conduit 38 when valve 40 is in the first position, conduit 38 is fully open, maintaining a low pressure in annular recess 28 and a pressure difference across control ring 30 for maintaining the control ring in the open position. That is, the low pressure source is chosen so that the forces on control ring 30 resulting from the pressure differential thereacross, explained in greater detail below, when conduit 38 is open are greater than the forces on the control ring due to springs 32, wherein the vapor pressure forces maintain the control ring in the open position.
  • valve 40 when valve 40 is in the second position, preferably low pressure conduit 38 is fully closed thereby, and vapor passes into annular recess 28 from diffuser passage 16 for maintaining a high pressure in the annular recess wherein springs 32 maintain control ring 30 in the throttling position.
  • Valve 40 is operated by positioning means 41, which may be of any appropriate type such as electric, pneumatic, or hydraulic positioners. Positioning means 41 is responsive to an operating condition of compressor 10 or its associated equipment which is indicative of the load on the compressor. Thus, if compressor 10 were to be used in a refrigeration machine, then the positioning means could be responsive to the temperature of the chilled water leaving the machine, this temperature being related to the quantity of refrigerant being lifted from the low side to the high side of the machine by the compressor. If compressor 10 were being used to compress air, then the positioning means could be responsive to ambient temperature, since this is an indication of the air density and therefore the quantity of air being compressed. Preferably, though, the position of valve 40 is determined by the position of guide vanes 24, sensed by sensing means 43.
  • Sensing means 43 may include, for example, a limit switch (not shown) which is actuated by a guide vane or a control linkage thereof in response to movement of the guide vane to a predetermined position, indicative of a restricted flow of vapor through compressor 10.
  • Compressor 10 functions as follows. With valve 40 in the first position wherein conduit 38 is open, annular recess 28 is in communication, via conduit 38, with the low pressure source, and the pressure in the recess is approximately equal to that of the low pressure source. Vapor pressure in annular recess 28 is less than vapor pressure in diffuser passage 16 and a pressure difference exists across control ring 30, urging the control ring rearward, to the left as viewed in Figure 1. As mentioned above, the low pressure source is chosen so that the forces on control ring 30 resulting from the pressure differential thereacross when conduit 38 is open are greater than the forces on the control ring due to springs 32. Thus, control ring 30 is moved to and maintained in the open position, allowing maximum vapor flow through diffuser passage 16.
  • Second stop means 42 may be provided to limit rearward movement of control ring 30, and preferably the second stop means includes a surface of housing 12. More specifically, as control ring 30 moves rearward and reaches the open position, flange 44 of the control ring abuttingly engages surface 42 and this abutting engagement prevents further rearward movement of the control ring. With this arrangement, flange 44 and surface 42, when abuttingly engaged as described above, also function as sealing means for retarding vapor flow from the higher pressure, right side of control ring 30 to the lower pressure, left side thereof.
  • valve 40 is moved to the second position, preferably wherein conduit 38 is fully closed by the valve. This may be done, as mentioned above, in response to any one of a number of conditions indicative of a restricted flow rate through compressor 10 such as the position of guide vanes 24. With conduit 38 closed, annular recess 28 is isolated from the low pressure source. Vapor passes into annular recess 28 from diffuser passage 16 through the interface between surface 42 and flange 44, equalizing the pressure in the annular recess and the diffuser passage. The vapor pressure forces on control ring 30 equalize.
  • control ring 30 throttles refrigerant passing into diffuser passage 16, maintaining stable vapor flow therethrough at the relatively lower flow rate.
  • FIG. 2 through 4 there is illustrated a second embodiment of the present invention.
  • Diffuser control ring 30 of the embodiment shown in Figures 2, 3 and 4 include three stable positions; an open position shown in Figure 2, an intermediate throttling position shown in Figure 3, and a full throttling position shown in Figure 4.
  • the embodiment shown in Figures 2 through 4 includes, in addition to those elements discussed above with reference to Figure 1, second urging means 50 for urging control ring 30 toward the intermediate throttling position.
  • conduit means 37 preferably includes low pressure conduit 38 and intermediate pressure conduit 58; and valve means 39 includes valves 40 and 62, with the former valve located in conduit 38 and the latter valve located in conduit 58.
  • the second urging means includes second resilient means such as a plurality of second springs 50 positioned within recess 28.
  • Second springs 50 are preferably equally spaced about the circumference of control ring 30, forming a second ring of springs with a radius also equal to that of the control ring.
  • first and second springs 32 and 50 have a generally cylindrical shape, with each second spring 50 concentrically encircling a first spring 32.
  • Force limiting means referenced generally as 52, limits the force exerted by second springs 50 on control ring 30 at the intermediate throttling position.
  • force limiting means 52 includes movable rings 54 and stop means such as stationary rings 56 which are secured to housing 12 and extend into annular recess 28. Rings 54 are slidably supported within recess 28 between second springs 50 and fingers 57 of control ring 30. Second springs 50 abuttingly engage rings 54, and this abutting contact maintains second springs 50 to the left of the rings. First springs 32, however, are slidable within rings 54, and rings 54 do not interfere with movement of first springs 32.
  • Intermediate pressure conduit 58 connects annular recess 28 with an intermediate pressure source.
  • the intermediate pressure source may be an intermediate stage thereof.
  • valves 40 and 62 cooperatively define a first position for maintaining a low pressure in annular recess 28, a second position for maintaining an intermediate pressure therein, and a third position for maintaining a high pressure in the annular recess.
  • the low pressure is sufficiently lower than the pressure in diffuser passage 16 so that, when the low pressure is maintained in annular recess 28, the pressure force on control ring 30 due to the pressure difference between the annular recess and the diffuser passage is greater than the forces on the control ring due to springs 32 and 50, and this first pressure force maintains the control ring in the open position.
  • the pressure force on control ring 30 is less than the combined forces on the control ring due to 32 and 50 but more than the forces on the control ring due solely to springs 32. This second pressure force maintains control ring 30 in the intermediate position.
  • valves 40 and 62 when valves 40 and 62 are in the third position and the high pressure is maintained in annular recess 28, the force on control ring 30 due to the pressure difference, if any, between the annular recess and diffuser passage 16 is less than the force on the control ring due to first springs 32, wherein springs 32 maintain the control ring in the full throttling position.
  • low pressure conduit 38 is open and intermediate pressure conduit 58 is closed by valve 62.
  • conduit 38 When valves 40 and 62 are in the second position, conduit 38 is closed by valve 40 but conduit 58 is open, and when valves 40 and 62 are in the third position, the valves close conduits 38 and 58 respectively.
  • second valve 62 may be operated by second positioning means 66 which, like first positioning means 41, may be of any appropriate type such as electric, pneumatic, or hydraulic positioners. Also like first positioning means 41, second positioning means 66 is responsive to an operating condition of compressor 10 or its associated equipment which is indicative of the load on the compressor. Preferably, positioning means 66 is responsive to the position of guide vanes 24 as sensed by sensor 43.
  • compressor 10 functions as follows. With valves 40 and 62 in the first position wherein low pressure conduit 38 is open and intermediate pressure conduit 58 is closed by valve 62, annular recess 28 is in communication with the low pressure source via conduit 38, and the pressure in the recess is approximately equal to that of the low pressure source. Vapor pressure in annular recess 28 is less than vapor pressure in diffuser passage 16 and a pressure difference exists across control ring 30, urging the control ring rearward, to the left as viewed in the drawings.
  • the low pressure source is chosen so that the forces on control ring 30 resulting from the pressure differential thereacross when valve 40 is open and valve 62 is closed are greater than the forces on the control ring due to springs 32 and 50. Thus, the vapor pressure forces dominate and control ring 30 is moved to and maintained in the open position, allowing maximum vapor flow through diffuser passage 16.
  • Second stop means 64 may be provided to limit rearward movement of control ring 30, and preferably the second stop means includes a surface of stationary ring 56. More specifically, as control ring 30 moves rearward and reaches the open position, flange 70 of the control ring abuttingly engages surface 64 and this abutting engagement prevents further rearward movement of the control ring. With this arrangement, flange 70 and surface 64, when abuttingly engaged as described above, also function as sealing means for retarding vapor flow from the higher pressure, right side of control ring 30 to the lower pressure, left side thereof.
  • control ring 30 To move control ring 30 to the intermediate throttling position, shown in Figure 3, low pressure conduit 38 is closed by valve 40 and intermediate pressure conduit 58 is opened. This may be done, for example, in response to guide vanes 24 moving to a predetermined position wherein vapor flow through compressor 10 is restricted. Annular recess 28 is in communication with the intermediate pressure chamber via conduit 58. The pressure in recess 28 is increased to approximately that of the intermediate pressure source, and the pressure difference across control ring 30 is decreased.
  • the intermediate pressure source is chosen so that the vapor pressure forces on control ring 30 when valve 40 is closed and valve 62 is open are less than the combined forces on the control ring due to springs 32 and 50. Thus, control ring 30 moves from the open position toward the intermediate throttling position.
  • control ring 30 When control ring 30 reaches the intermediate throttling position, shown in Figure 3, movable ring 54 abuttingly engages stationary ring 56, preventing further forward movement of the movable ring and second spring 50. Thus, second springs 50 do not urge control ring 30 further to the right. First springs 32 continue to urge control ring 30 further to the right.
  • the intermediate pressure source is chosen so that the vapor pressure forces on control ring 30 resulting from the pressure differential thereacross when valve 40 is closed and valve 62 is open are greater than the forces on the control ring due solely to second springs 50.
  • control ring 30 is maintained in the intermediate throttling position. In this position, control ring 30 throttles the vapor flowing through diffuser passage 16, providing a stable vapor flow therethrough at the reduced flow rate.
  • control ring 30 when control ring 30 is in the intermediate throttling position, movable ring 54 abuttingly engages both stationary ring 56 and fingers 57 of the control ring, and rings 54 and 56 and fingers 57 function as sealing means for retarding vapor flow from the higher pressure, right side of the control ring to the lower pressure, left side thereof.
  • control ring 30 To move control ring 30 to the full throttling position, shown in Figure 4, low and intermediate pressure conduits 38 and 58 are closed by valves 40 and 62 respectively. This may be done, as an example, in response to guide vanes 24 moving to a second predetermined position further restricting vapor flow through compressor 10. Vapor passes into annular recess 28 from diffuser passage 16 via the interface between fingers 57 and movable rings 54, and vapor pressures in the annular recess and the diffuser passage equalize, equalizing the vapor pressure forces on control ring 30. Forces from springs 32 dominate the push control ring 30 into diffuser passage 16 to the full throttling position, wherein abutting contact between flange 36 and surface 34 prevents further forward movement of the control ring. Control ring 30 further throttles vapor passing through diffuser passage 16, maintaining stable vapor flow therethrough even at the further restricted rate of flow through compressor 10.
  • the above-described preferred embodiments of the present invention provide stable vapor flow through diffuser passage 16 over a wide range of compressor loads.
  • the simplicity of diffuser controls 26, particularly the absence of any complicated mechanical linking arrangement connecting the control with, for example, guide vanes 24, makes the diffuser controls well suited for use on a retrofit basis.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
EP79104971A 1978-12-26 1979-12-06 Centrifugal vapor compressor and a diffuser control therefor Expired EP0012895B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US05/973,404 US4257733A (en) 1978-12-26 1978-12-26 Diffuser control
US05/973,405 US4219305A (en) 1978-12-26 1978-12-26 Diffuser control
US973405 1978-12-26
US973404 1978-12-26

Publications (2)

Publication Number Publication Date
EP0012895A1 EP0012895A1 (en) 1980-07-09
EP0012895B1 true EP0012895B1 (en) 1983-09-07

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ID=27130568

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Application Number Title Priority Date Filing Date
EP79104971A Expired EP0012895B1 (en) 1978-12-26 1979-12-06 Centrifugal vapor compressor and a diffuser control therefor

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EP (1) EP0012895B1 (cs)
JP (1) JPS5921100U (cs)
CA (1) CA1119140A (cs)
DE (1) DE2966146D1 (cs)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH677956A5 (cs) * 1986-07-02 1991-07-15 Carrier Corp
NZ220367A (en) * 1986-09-25 1991-05-28 Superstill Technology Inc Liquid seal for pump shaft: liquid is steam condensed from pump chamber
JP2751418B2 (ja) * 1989-06-13 1998-05-18 ダイキン工業株式会社 ターボ圧縮機のディフューザ
GB9711892D0 (en) * 1997-06-10 1997-08-06 Holset Engineering Co Variable geometry turbine
CN104632712B (zh) * 2013-11-21 2017-02-08 珠海格力电器股份有限公司 叶轮机械及其扩压器
EP3325816B1 (en) 2015-07-22 2019-08-28 Carrier Corporation Diffuser restriction ring
CN114651131A (zh) * 2019-11-13 2022-06-21 丹佛斯公司 用于混合流压缩机的主动卸载装置

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL224304A (cs) * 1957-12-23
DE1503580A1 (de) * 1965-04-12 1970-06-11 Mannesmann Meer Ag Radial-Kreiselmaschine mit optimal anpassbaren Stroemungsquerschnitten im feststehenden Teil
US3426964A (en) * 1966-10-11 1969-02-11 Dresser Ind Compressor apparatus
JPS5229441B2 (cs) * 1973-06-25 1977-08-02
JPS5092508A (cs) * 1973-12-21 1975-07-24
JPS5115807A (ja) * 1974-07-30 1976-02-07 Mitsubishi Heavy Ind Ltd Enshinatsushukuki

Also Published As

Publication number Publication date
DE2966146D1 (en) 1983-10-13
EP0012895A1 (en) 1980-07-09
JPS5921100U (ja) 1984-02-08
JPS6218719Y2 (cs) 1987-05-13
CA1119140A (en) 1982-03-02

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