US20080210317A1 - Dynamically Controlled Compressors - Google Patents

Dynamically Controlled Compressors Download PDF

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Publication number
US20080210317A1
US20080210317A1 US11/658,811 US65881105A US2008210317A1 US 20080210317 A1 US20080210317 A1 US 20080210317A1 US 65881105 A US65881105 A US 65881105A US 2008210317 A1 US2008210317 A1 US 2008210317A1
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US
United States
Prior art keywords
compressors
inertia
pressure side
vessel
predetermined size
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.)
Abandoned
Application number
US11/658,811
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English (en)
Inventor
Ronald David Conry
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.)
Danfoss AS
Danfoss AS
Original Assignee
Turbocor 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
Application filed by Turbocor Inc filed Critical Turbocor Inc
Priority to US11/658,811 priority Critical patent/US20080210317A1/en
Assigned to TURBOCOR INC. reassignment TURBOCOR INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CONRY, RONALD DAVID
Publication of US20080210317A1 publication Critical patent/US20080210317A1/en
Assigned to DANFOSS A/S reassignment DANFOSS A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DANFOSS TURBOCOR COMPRESSORS B.V.
Abandoned 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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85978—With pump
    • Y10T137/86131—Plural
    • Y10T137/86163—Parallel

Definitions

  • the present invention relates to compressors. More specifically, the present invention is concerned with a dynamically controlled compressor system and method.
  • centrifugal compressors have an operating envelope, referred to as the compressor map, which is limited by a condition called choke and another condition called surge.
  • centrifugal compressors pump gas when operating within the surge and choke points. If a centrifugal compressor is left operating in a surge condition for any length of time, impellers thereof can overheat and damage the whole machine. Compressor manufacturers go to length at trying to protect the compressor from operating in these damaging conditions with a variety of surge detection devices, which, when they detect a surge, shut the machine down to prevent damage.
  • centrifugal compressors In order to conserve energy, some more recent centrifugal compressors have added speed control to increase its operating range and in these cases the compressors control system has become dynamic. While up until this point, the compressors were either on or off, they have thus become more intelligent and the dynamic nature of the controls causes the compressors to react to changes in the condition. In a most recent version now available on the marketplace, by the present applicant, the centrifugal compressors may have totally dynamic controls and continually optimizes their speed and the positions of their inlet guide vanes to maximize their efficiency.
  • centrifugal compressors have been mainly single compressor systems, and in more recent years, when two compressors have been applied to the one machine, have run in parallel and the loading and unloading has been through the use of the (IGV) alone and have been controlled from the one controller and therefore load and unload at the same rate and at the same time.
  • compressors have a compressor map programmed into a control unit thereof, to adjust their speed and when necessary also operate their inlet guide vanes in order to maximize their performance.
  • Such dynamic control system provides that the compressors adapt their operating parameters as the conditions in the system change and as the load in the system varies.
  • FIG. 1 illustrating a first compressor comp 1 and a second compressor comp 2 in parallel between a low pressure side (suction line) and a high pressure side (discharge line)
  • operating conditions of the first compressor may be directly effected by a change in pumping capacity of the second compressor.
  • a multiple compressor system comprising at least a first and a second compressors in parallel between a low pressure side and a high pressure side; at least one inertia vessel connected to one of suction lines and discharge lines of the at least first and second compressors; wherein the at least one inertia vessel acts as a means of dampening changes of operation condition of the at least first and second compressors.
  • a method for controlling a compressor system including at least two compressors arranged in parallel between a low pressure side and a high pressure side, comprising the step of connecting at least one inertia vessel to at least one of: a suction line and: a discharge line of at least one of the at least two compressors.
  • FIG. 1 labelled as Prior Art, illustrates a piping configuration of multiple compressors piped up in parallel, as known in the art
  • FIG. 2 illustrates a system according to an embodiment of the present invention
  • FIG. 3 illustrates a system according to an other embodiment of the present invention
  • FIG. 4 illustrates a system according to a further embodiment of the present invention
  • FIGS. 5 illustrate alternatives to the embodiment of FIG. 4 ;
  • FIG. 6 illustrates a system according to still a further embodiment of the present invention.
  • FIG. 7 illustrates an alternative to the embodiment of FIG. 6 .
  • FIG. 8 illustrates a system comprising multiple compressors piped in parallel to and from a common vessel, i.e. condenser and evaporator, which most likely does not require inertia tanks.
  • the load of the compressor varies as a function of time as well as the temperatures, and therefore pressures. These variations have impacts on the compressor operation and the compressor, in response, adjusts its speed and inlet guide vane.
  • Such a dynamic control system may be applied to conventional system using other types of positive displacement compressors such as reciprocating, scroll or screw compressors for example.
  • the compressor may thus respond as the load demand changes in the process in which it is being applied, such as a manufacturing process.
  • the present invention provides an adequately sized vessel or tank in either or both the suction line or the discharge line of multiple compressors, in such a fashion that if the conditions of the first compressor change, it does not have an immediate effect on the other compressors, the vessel acting as a means of dampening the change.
  • FIG. 2 illustrates a parallel piping system comprising a header arrangement to reduce the impact of a first compressor changes in operation on a second compressor: a common low pressure tank 12 is connected to the suction line and a high pressure tank 14 is connected to the discharge line of the compressors Comp 1 and Comp 2 .
  • an expansion tank is installed in the discharge 14 a, 14 b and in the suction 12 a, 12 b lines of each compressors Comp 1 and Comp 2 to reduce the impact of the change in the first compressor operation on the second compressor.
  • FIG. 4 illustrates a system of hermetic or semi-hermetic compressors wherein a compressor housing, such as in a hermetic or semi-hermetic compressor, is provided, which is adequately sized to act as an inertia tank thus eliminating the need for external inertia tanks.
  • FIGS. 5 illustrate a system comprising two compressors sharing a same housing adequately sized to act as an inertia tank thus eliminating the need for an external inertia tank.
  • This type of system may have one or more exit and entry ports (see FIGS. 5a and 5b ).
  • FIG. 6 illustrates an alternative embodiment where a low and high pressure inertia tanks are provided, these inertia tanks being modular in design and connected by flanged connections or connections as provided by Victualic Inc. for example, the inlet and outlet pipes being connected at either end.
  • the inlet and outlet pipes to the inertia tanks may be connected into any part of the inertia tanks.
  • the inlet and outlet connections may be installed into the middle of the stack in order to balance the distribution of the gas and reduce the size of the individual inertia tanks.
  • refrigerant may enter and exit the system from any of at least one ports.
  • the present invention may be used in applications where multiple dynamically controlled compressors are used to replace one large compressor and where the suction and discharge lines have to be connected to a heat exchanger through either or both the one entry and one exit points.
  • An example of this would be a water chiller where there is one entry to the condenser and one exit from the evaporator. If the compressor only required one compressor, then there would be no problem, however where two or more compressors are needed to obtain a required capacity, then simply piping the compressors as is usually done in the art is inefficient. The connecting point of the pipe work needs to be of adequate size as to not have an immediate effect on the other compressors operating in the system.
  • the present invention may be applied to systems comprising more than two compressors.
  • the systems of FIGS. 2-8 may be expanded by adding additional compressors either when the systems are first installed or at a later date as required.
  • Each of the systems may also have the capability to be piped up with single or multiple suction and discharge pipes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US11/658,811 2004-07-27 2005-07-21 Dynamically Controlled Compressors Abandoned US20080210317A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/658,811 US20080210317A1 (en) 2004-07-27 2005-07-21 Dynamically Controlled Compressors

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US59108204P 2004-07-27 2004-07-27
PCT/CA2005/001149 WO2006010251A1 (en) 2004-07-27 2005-07-21 Dynamically controlled compressors
US11/658,811 US20080210317A1 (en) 2004-07-27 2005-07-21 Dynamically Controlled Compressors

Publications (1)

Publication Number Publication Date
US20080210317A1 true US20080210317A1 (en) 2008-09-04

Family

ID=35785869

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/658,811 Abandoned US20080210317A1 (en) 2004-07-27 2005-07-21 Dynamically Controlled Compressors

Country Status (9)

Country Link
US (1) US20080210317A1 (ko)
EP (1) EP1781949A4 (ko)
JP (1) JP2008507659A (ko)
KR (1) KR20070045266A (ko)
CN (1) CN101002025A (ko)
AU (1) AU2005266792A1 (ko)
BR (1) BRPI0513578A (ko)
CA (1) CA2574879C (ko)
WO (1) WO2006010251A1 (ko)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10760840B2 (en) 2015-11-09 2020-09-01 Carrier Corporation Dual-compressor refrigeration unit
US11408418B2 (en) * 2019-08-13 2022-08-09 Rockwell Automation Technologies, Inc. Industrial control system for distributed compressors

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009016392A1 (de) 2009-04-07 2010-10-14 Man Turbo Ag Verdichteranordnung
US20240111314A1 (en) * 2022-09-29 2024-04-04 Opticool Solutions, LLC Automatic dual pump system with three-way valve

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2548472A (en) * 1947-12-19 1951-04-10 Standard Oil Dev Co Compressor pulsation dampener
US3859820A (en) * 1972-07-17 1975-01-14 Applied Air Cond Equip Compressor, condenser, evaporator structure
US4326387A (en) * 1978-04-03 1982-04-27 Hussmann Refrigerator Co. Fluidic time delay system
US4465090A (en) * 1982-05-07 1984-08-14 Menco Manufacturing, Inc. Air relay
US4989924A (en) * 1988-03-31 1991-02-05 Aisin Seiki Kabushiki Kaisha Fluid pressure circuit
US5875637A (en) * 1997-07-25 1999-03-02 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US6082408A (en) * 1998-09-22 2000-07-04 Navistar International Transportation Corp Modular air tank assembly
US6478560B1 (en) * 2000-07-14 2002-11-12 Ingersoll-Rand Company Parallel module rotary screw compressor and method
US20030012659A1 (en) * 2000-10-16 2003-01-16 Seibel Stephen M. Dual volume-ratio scroll machine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191305865A (en) * 1912-03-18 1913-12-04 Cyrus Howard Hapgood Improvements in Refrigerating Apparatus.
US1719807A (en) * 1923-06-04 1929-07-02 Westinghouse Electric & Mfg Co Refrigerator
US4646530A (en) * 1986-07-02 1987-03-03 Carrier Corporation Automatic anti-surge control for dual centrifugal compressor system
JPH0610562B2 (ja) * 1987-08-31 1994-02-09 三菱電機株式会社 ヒートポンプ式冷暖房装置
JP2911228B2 (ja) * 1990-12-13 1999-06-23 三洋電機株式会社 冷凍サイクルの制御装置
US5222370A (en) * 1992-01-17 1993-06-29 Carrier Corporation Automatic chiller stopping sequence
JP3649548B2 (ja) * 1997-03-25 2005-05-18 三菱重工業株式会社 冷凍サイクル
JP4774171B2 (ja) * 2001-08-20 2011-09-14 社団法人エルピーガス協会 空気調和装置
CA2373905A1 (en) * 2002-02-28 2003-08-28 Ronald David Conry Twin centrifugal compressor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2548472A (en) * 1947-12-19 1951-04-10 Standard Oil Dev Co Compressor pulsation dampener
US3859820A (en) * 1972-07-17 1975-01-14 Applied Air Cond Equip Compressor, condenser, evaporator structure
US4326387A (en) * 1978-04-03 1982-04-27 Hussmann Refrigerator Co. Fluidic time delay system
US4465090A (en) * 1982-05-07 1984-08-14 Menco Manufacturing, Inc. Air relay
US4989924A (en) * 1988-03-31 1991-02-05 Aisin Seiki Kabushiki Kaisha Fluid pressure circuit
US5875637A (en) * 1997-07-25 1999-03-02 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US6082408A (en) * 1998-09-22 2000-07-04 Navistar International Transportation Corp Modular air tank assembly
US6478560B1 (en) * 2000-07-14 2002-11-12 Ingersoll-Rand Company Parallel module rotary screw compressor and method
US20030012659A1 (en) * 2000-10-16 2003-01-16 Seibel Stephen M. Dual volume-ratio scroll machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10760840B2 (en) 2015-11-09 2020-09-01 Carrier Corporation Dual-compressor refrigeration unit
US11408418B2 (en) * 2019-08-13 2022-08-09 Rockwell Automation Technologies, Inc. Industrial control system for distributed compressors

Also Published As

Publication number Publication date
CA2574879C (en) 2010-04-27
EP1781949A1 (en) 2007-05-09
WO2006010251A1 (en) 2006-02-02
JP2008507659A (ja) 2008-03-13
EP1781949A4 (en) 2010-06-09
KR20070045266A (ko) 2007-05-02
AU2005266792A1 (en) 2006-02-02
CN101002025A (zh) 2007-07-18
BRPI0513578A (pt) 2008-05-06
CA2574879A1 (en) 2006-02-02

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AS Assignment

Owner name: TURBOCOR INC., CANADA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CONRY, RONALD DAVID;REEL/FRAME:019446/0664

Effective date: 20070123

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION

AS Assignment

Owner name: DANFOSS A/S, DENMARK

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DANFOSS TURBOCOR COMPRESSORS B.V.;REEL/FRAME:035813/0680

Effective date: 20140922