US3859820A - Compressor, condenser, evaporator structure - Google Patents

Compressor, condenser, evaporator structure Download PDF

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Publication number
US3859820A
US3859820A US378719A US37871973A US3859820A US 3859820 A US3859820 A US 3859820A US 378719 A US378719 A US 378719A US 37871973 A US37871973 A US 37871973A US 3859820 A US3859820 A US 3859820A
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United States
Prior art keywords
condenser
compartment
evaporator
machine
separate
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Expired - Lifetime
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US378719A
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English (en)
Inventor
William Edwin Dobney
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 Air Conditioning Pty Ltd
APPLIED AIR CONDITIONING EQUIPMENT Pty Ltd
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APPLIED AIR CONDITIONING EQUIPMENT Pty Ltd
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Assigned to LUKE LIMITED reassignment LUKE LIMITED CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: K.G. LUKE GROUP INDUSTRIES LIMITED
Assigned to K.G. LUKE GROUP INDUSTRIES LIMITED reassignment K.G. LUKE GROUP INDUSTRIES LIMITED REGISTRATON OF BUSINESS NAME Assignors: APPLIED AIR CONDITIONING EQUIPMENT
Assigned to CARRIER AIR CONDITIONING PTY. LTD. reassignment CARRIER AIR CONDITIONING PTY. LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LUKE LIMITED
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements

Definitions

  • ABSTRACT A refrigeration machine comprising an evaporator and condenser, the condenser being divided into at least two condenser chambers, a separate compressor for each condenser chamber, the inputs of the compressors being in communication with the evaporator and the output of each being in communication with its associated condenser chamber, the divisionof the condenser affording the advantages of a two condenser machine without the cost of a separate condenser construction.
  • Tube-shell type machines are those wherein the evaporator and condenser compartments are constructed in the form of elongated hollow shell structures with heat transfer tubes extending longitudinally therethrough.
  • the evaporator and condenser compartments may comprise separate shell structures or alternatively the evaporator and condenser compartments may be defined by an insulated dividing wall within a single shell structure.
  • the use of two compressors enables controlled load sharing of the compressors to provide for more stable and efficient operation of the machines.
  • the proportion of load is low, it is preferable to use a single compressor operating at a relatively high level of load than to use both compressors operating at relatively low load levels because the characteristics of the compressors are poorer at low load levels.
  • the compressors which are normally used in this type of refrigeration machine are centrifugal compressors which are normally fitted with automatic control means to reduce the gas flow therethrough so that the overall performance of the refrigeration machine may be controlled to meet the load requirements of the machine. It is clear that where the refrigeration machine is used for airconditioning purposes the load requirements will vary according to the prevailing climatic conditions. Therefore in normal use considerable variation in load is to be expected. Unfortunately, the performance curves of the centrifugal compressors is such that when the gas flow is reduced below about 90 percent of the maximum, there is a tendency for the pressure head available from the compressor to be reduced.
  • the main object of this invention is to provide a refrigeration machine of the type referred to having the advantages of two compressors, the construction being such that problem of surge is substantially reduced, and yet the need for separate condenser structures is avoided. 7
  • a refrigeration machine comprising an evaporator and condenser, the condenser being divided into at least two condenser chambers, a separate compressor for each condenser chamber, the inputs of the compressors being in communication with the evaporatorand the output of each being in communication with its associated condenser chamber.
  • a separate compressor for each condenser chamber, the inputs of the compressors being in communication with the evaporatorand the output of each being in communication with its associated condenser chamber.
  • the evaporator and condenser may comprise separate structures, or alternatively comprise a single divided structure, the latter being preferred because of its cheaper construction.
  • the condenser is preferably divided into separate condenser chambers by a baffle or baffles which extend transversely of heat transfer tubes which pass through the condenser.
  • the condenser may be divided by a baffle or baffles which extend in the direction of the heat transfer tubes but in most cases the former arrangement is preferred because normally a two-pass arrangement of tubes is employed and tends to give more equal average temperatures inthe condenser chambers and thus more even loading of the compressors when operating in parallel.
  • a similar temperature averaging effect can be achieved in the arrangement where the condenser is divided by a baffle extending in the direction of the heat transfer tubes by having both passes of the two pass tubes within one of I the condenser chambers.
  • the elongated hollow structure is substantially elliptical in cross-section, and in normal use of the machine, a major axis'of the ellipse will be vertical.
  • the evaporator and condenser compartments may be defined by a pair of spaced plates which are located near and parallel to the minor axis of the ellipse at any cross-.
  • the two compressors are mounted on the hollow structure and are spaced longitudinally thereon.
  • the compressors may have impellers which rotate about horizontal axes, the inputs of which are in communication with the evaporator compartment through input ports provided in the upper part of the hollow structure, and the first heat transfer tubes are located near the lower part of the evaporator compartment.
  • the outputs of the compressors are preferably in communication with the separate chambers through outlet ports provided in the side of thehollow structure, and the second heat transfer tubes are located in the upper part of the separatechambers.
  • FIG. 1 is a fragmentary elevation view of a refrigeration machine in accordance with the present invention
  • I FIG. 2 is a fragmentary cross-sectional view taken along the line 2-2 in FIG. 1.
  • the refrigeration machine shown generally by the reference numeral 2, comprises an elongated hollow shell structure 4 and two centrifugal compressors 6 and 8 mounted on the shell structure 4.
  • the shell structure 4 is formed from steel plate and is substantially elliptical in cross-section with the major axis vertical.
  • the shell structure 4 is divided longitudinally by a pair of spaced parallel plates 12 and 14 to define evaporator and condenser compartments 16 and 18, respectively.
  • the spacing between the plates 12 and 14 provides thermal insulation between the evaporator and condenser compartments 16 and 18.
  • An insulating jacket not shown in the drawings would normally be provided around part of the outer periphery of the shell structure 4 to provide thermal insulation for the evaporator compartment 16.
  • the evaporator compartment 16 is located above the condenser compartment 18 but this is not'absolutely necessary.
  • a plurality of spaced, parallel heat transfer tubes 20 extend through the evaporator compartment 16 in a regular array but are located near the lower part of the evaporator compartment 16.
  • the tubes comprise finned or unfinned copper tubing supported at the end walls 22 and 24 of the structure 4.
  • the heat transfer tubes 20 When the refrigeration machine 2 is installed, the heat transfer tubes 20 would form part of a primary heat transfer circuit in -which a heat transfer fluid (normally water) is used as to return the rest of the primary heat transfer circuit.
  • a heat transfer fluid normally water
  • tubes 20 when filled with water are quite heavy and additional support may 4 be required at intermediate portions along their length.
  • additional support is provided by a pair of perforated plates 30 and 30a which are mounted upon the plate 14.
  • the tubes 20 pass through an array of perforations provided in the plates 30 and 30a.
  • the heat transfer fluid in the tubes 20 is arranged to be cooled by the agency of evaporating and expanding refrigerant fluid which issues from a plurality of nozzles 32.
  • the nozzles 32 extend longitudinally in three rows along the evaporator compartment 16 adjacent to the plate 16.
  • the refrigerant fluid in liquid form, is supplied to the nozzles 32 by a supply channel 34 located centrally of and between the plates 12 and 14.
  • One row of nozzles is directly above the supply channel 34 and the other rows are disposed to either side and are supplied with liquid refrigerant by a plurality of tubes 36 which extend laterally from the supply channel 34.
  • the nozzles 32 are arranged to issue the evaporating and expanding refrigerant fluid in a direction generally parallel to the plate 14 to provide better circulation of the refrigerant gas about the heat transfer tubes 20 so that heat can be extracted-more effectively from the heat transfer liquid therein. It will be appreciated that a greater volume flow of evaporating and expanding refrigerant fluid in the evaporator compartment will mean that a greater amount of heat will be extracted from the heat transfer fluid in the tubes 20. Therefore the output capacity of the machine can be controlled by controlling the flow of refrigerant fluid to meet the capacity required by the compressors. As mentioned previously, undesirable modes of operation would be encountered if the flow of refrigerant fluid were to be controlled by adjusting the two compressors 6 and 8 independently without the incorporation of a special feature into the condenser compartment to be described later.
  • the evaporated refrigerant fluid is collected from the evaporator compartment 16 by means of input ducts 38 and 40 to the centrifugal compressors 6 and 8 respectively.
  • an array of eliminator plates 42 is provided to ensure that only refrigerant fluid in the gaseous state and not droplets of refrigerant fluid is allowed to reach the compressor input.
  • the refrigerant fluid leaving the centrifugal compressors 6 and 8 is discharged into the compressor compartment 18 by means of discharge ducts 44 and 46.
  • the partition 48 is provided with an array of perforations which'correspond with an array of heat conducting tubes 54 which pass through the perforations and are sealed at their peripheries to the partition 48.
  • the discharge ducts 44 and 46 are in communication with the chambers 50 and 52 of the condenser compartment 18 respectively.
  • the heat conducting tubes 54 are provided in the upper part of the condenser chamber compartment 18 and extend between the end walls 22 and 24 of the shell structure 4.
  • the tubes 54 form part of a secondary heat transfer conduit in which the heat transfer medium is arranged to enterthe tubes 54 through an inlet manifold 56 located adjacent the end wall 22 and leave via per tubing supported along their lengths by the end wall 22, a pair of perforated support plates 60, 60a, the partition 48, and the end wall 24.
  • the discharge ducts. 44 and 46 are in communication with the respective chambers 50 and 52 of the condenser 18 by means of openings 62 and 64 in the side of the shell structure 4.
  • the refrigerant fluid discharged from the discharge'ducts 44 and 46 is at a relatively higher temperature because of the compression process and is arranged to circulate about the tubes 54 so that the heat transfer fluid in the secondary circuit absorbs heat from the refrigerant gas.
  • secondary circuit usually includes an atmospheric heat sink for dissipating unwanted heat.
  • the refrigerant fluid after losing sufficient heat, will then condense on the tubes 54 or on the inside of the peripheral walls of the chambers 50 and 52.
  • the condensed refrigerant fluid is then allowed to drain into refrigerant sumps 66 and 68.
  • Supply tubes 70 and 72 are provided to allow liquid refrigerant fluid to pass therethrough from the sumps to the supply channel 34 from where it is free to issue from the rows of nozzles 32.
  • the flow of refrigerant through the supply tubes 70, 72 is controlled respectively by float valves 74, 76, the operation of which is controlled by the level of refrigerant fluid in the sumps.
  • the partition 48 affords an absolutely gas tight seal between the two chambers 50 and 52.
  • the seal between the compartments 50 and 52 is imperfect, and compressors 6 and 8 are operating under different load conditions, then it is quite probable that the pressure in the chambers 50 and 52 will differ and consequently there will be some flow of refrigerant fluid between the chambers.
  • the amount of refrigerant fluid flow between the two chambers will, in practice, be insignificant compared to the two compressors 6 and 8 are set to operate to share equally the load, the existence of a small refrigerant fluid flow from one chamber to the other can be considered advantageous because this will have a tendency to more evenly distribute the loading between the two condensers.
  • baffle 48 to divide the condenser compartment 18 into two separate chambers is that the pressure in one chamber is essentially independent from the pressure inthe other chamber, and therefore operation of one compressor is substantially independent from the operation of the other. Thus, the likelihood of one of the compressors stalling is substantially reduced.
  • a machine according to claim 1 including an elongated structure having a hollow interior, and means for dividing the hollow interior longitudinally to define evaporator and condenser compartments within the hollow structure.
  • hollow structure is substantially elliptical in cross-section with the major axis vertical, the means for dividing the hollow structure being in a horizontal plane which includes the minor axis of the hollow structure.
  • a machine as claimed in claim 4 including spaced apart, generally parallel upper and lower longitudinal plates for dividing the hollow structure into the evaporator and condenser compartments, the space above the upper plate being the evaporator compartment and the space beneath the lower plate being the condenser compartment, the area between the upper and lower plates being a hollow space for serving as a duct for condensed refrigerant fluid being returned to the evaporator compartment. by the return means.
  • a machine as claimed in claim '5 including separate means to return condensed refrigerant fluid from the separate condenser chambers to the evaporator compartment.
  • each baffle means extends through a medial plane of the condenser compartment, whereby the two separate condenser chambers are substantiallyequal in volume, and including an equal number of second heat transfer tubes extending through each of the two separate condenser chambers.
  • baffle means divides the condenser compartment into condenser chambers of substantially equal size.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
US378719A 1972-07-17 1973-07-12 Compressor, condenser, evaporator structure Expired - Lifetime US3859820A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AUPA973572 1972-07-17

Publications (1)

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US3859820A true US3859820A (en) 1975-01-14

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Country Status (4)

Country Link
US (1) US3859820A (enExample)
JP (1) JPS4992643A (enExample)
DE (1) DE2336151A1 (enExample)
GB (1) GB1388244A (enExample)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5450852U (enExample) * 1977-09-16 1979-04-09
JPS5463253U (enExample) * 1977-10-13 1979-05-04
WO1999005463A1 (en) * 1997-07-25 1999-02-04 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US6481242B2 (en) * 2000-06-07 2002-11-19 Mitsubishi Heavy Industries, Ltd. Condenser and freezer
WO2006010251A1 (en) * 2004-07-27 2006-02-02 Turbocor Inc. Dynamically controlled compressors
WO2009004422A3 (en) * 2007-07-03 2009-02-26 Wtk S R L 'improved tube-bundle heat exchanger'.
WO2011008375A1 (en) * 2009-06-29 2011-01-20 Johnson Controls Technology Company System for limiting pressure differences in dual compressor chillers
CN105758032A (zh) * 2016-04-25 2016-07-13 张家港市华昌新材料科技有限公司 一种乙二醇冷冻机组节能方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZA858943B (en) * 1984-11-22 1986-08-27 Hitachi Ltd Compression refrigerating machine with vapor-liquid separator
JP6304220B2 (ja) 2015-12-08 2018-04-04 トヨタ自動車株式会社 運転支援装置
US10088208B2 (en) 2016-01-06 2018-10-02 Johnson Controls Technology Company Vapor compression system

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118290A (en) * 1964-01-21 Refrigeration machine including evaporator condenser structure
US3122003A (en) * 1962-03-13 1964-02-25 American Radiator & Standard Sequence changer

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118290A (en) * 1964-01-21 Refrigeration machine including evaporator condenser structure
US3122003A (en) * 1962-03-13 1964-02-25 American Radiator & Standard Sequence changer

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5450852U (enExample) * 1977-09-16 1979-04-09
JPS5463253U (enExample) * 1977-10-13 1979-05-04
WO1999005463A1 (en) * 1997-07-25 1999-02-04 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US5875637A (en) * 1997-07-25 1999-03-02 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US6481242B2 (en) * 2000-06-07 2002-11-19 Mitsubishi Heavy Industries, Ltd. Condenser and freezer
WO2006010251A1 (en) * 2004-07-27 2006-02-02 Turbocor Inc. Dynamically controlled compressors
US20080210317A1 (en) * 2004-07-27 2008-09-04 Turbocor Inc Dynamically Controlled Compressors
WO2009004422A3 (en) * 2007-07-03 2009-02-26 Wtk S R L 'improved tube-bundle heat exchanger'.
US20100132927A1 (en) * 2007-07-03 2010-06-03 Wtk S.R.L. Tube-Bundle Heat Exchanger
WO2011008375A1 (en) * 2009-06-29 2011-01-20 Johnson Controls Technology Company System for limiting pressure differences in dual compressor chillers
US8739562B2 (en) 2009-06-29 2014-06-03 Johnson Controls Technology Company System for limiting pressure differences in dual compressor chillers
CN105758032A (zh) * 2016-04-25 2016-07-13 张家港市华昌新材料科技有限公司 一种乙二醇冷冻机组节能方法

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Publication number Publication date
JPS4992643A (enExample) 1974-09-04
DE2336151A1 (de) 1974-02-07
GB1388244A (en) 1975-03-26

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Date Code Title Description
AS Assignment

Owner name: CARRIER AIR CONDITIONING PTY. LTD., AUSTRALIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LUKE LIMITED;REEL/FRAME:006548/0094

Effective date: 19900928

Owner name: LUKE LIMITED, AUSTRALIA

Free format text: CHANGE OF NAME;ASSIGNOR:K.G. LUKE GROUP INDUSTRIES LIMITED;REEL/FRAME:006547/0547

Effective date: 19761216

Owner name: K.G. LUKE GROUP INDUSTRIES LIMITED, AUSTRALIA

Free format text: REGISTRATON OF BUSINESS NAME;ASSIGNOR:APPLIED AIR CONDITIONING EQUIPMENT;REEL/FRAME:006548/0099

Effective date: 19751017