US3096630A - Refrigeration machine including compressor, condenser and evaporator - Google Patents

Refrigeration machine including compressor, condenser and evaporator Download PDF

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Publication number
US3096630A
US3096630A US18607A US1860760A US3096630A US 3096630 A US3096630 A US 3096630A US 18607 A US18607 A US 18607A US 1860760 A US1860760 A US 1860760A US 3096630 A US3096630 A US 3096630A
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United States
Prior art keywords
condenser
evaporator
refrigerant
shell
compressor
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 - Lifetime
Application number
US18607A
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English (en)
Inventor
Weller Peter Anthony
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.)
American Radiator and Standard Sanitary Corp
Original Assignee
American Radiator and Standard Sanitary Corp
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Filing date
Publication date
Application filed by American Radiator and Standard Sanitary Corp filed Critical American Radiator and Standard Sanitary Corp
Priority to US18607A priority Critical patent/US3096630A/en
Priority to CH350361A priority patent/CH391748A/fr
Priority to BE601693A priority patent/BE601693A/fr
Application granted granted Critical
Publication of US3096630A publication Critical patent/US3096630A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/23—Separators

Definitions

  • a further object of the invention is to provide a re frigerant system which can be installed as a single selfcontained package structure, complete with evaporator, compressor and condenser.
  • An additional object of the invention is to provide a unitary refrigerant machine having improved iiow of refrigerant, the improvement particularly residing in an arrangement wherein relatively short flow ⁇ ducts are utilized between the operative components of the system and wherein natural tendencies of the refrigerant in its different states (liquid and gaseous) are taken advantage of in promoting a satisfactory refrigerant circulation.
  • a still further object of the invention is to provide a compressor-condenser arrangement wherein compressed refrigerant is fed from the compressor into extensive and diverse areas of the condenser so as to promote a rapid, high rate condensing action.
  • a further object of the invention is to provide a refrigerant system devoid of constricted flow areas such as would retard the proper flow of refrigerant and such as would interfere with proper operation of the system after prolonged service life, as by reason of clogging, plugging or the like.
  • Another object of the invention is to provide a refrigerant system having an eliminator or condensate collection member arranged to receive evaporated refrigerant from the evaporator and trap condensed refrigerant against entrance into the compressor, the construction and arrangement being such that the eliminator presents an extensive surface area to the evaporated refrigerant, whereby the vapor velocities are maintained relatively low so as to reduce the tendency for liquid entrainment.
  • FIGURE 1 is a sectional View of one embodiment of the invention taken substantially on line 1--1 in FIG. 2;
  • FIG. 2 is a sectional view taken substantially on line 2--2 in FIG. l;
  • FIG. 3 is a top plan view of a portion of the FIG. l embodiment taken on a reduced scale
  • IFIG. 4 is a reduced scale sectional view taken substantially on line 4-4 in FIG. l.
  • a refrigerant system including a compressor section identified generally by numeral 10, a condenser section identified generally by numeral 12, and an evaporator section identified generally by numeral 14. It will be noted from FIGS. 1 and 2 that the refrigerant takes a path such that evaporated refrigerant -from the evaporator section 14 travels upwardly through a central tube ⁇ or passageway 68 and into the inlet of the compressor section 10. The compressed refrigerant is directed generally laterally in two different directions before being discharged in a generally downward direction at two longitudinally spaced points within the condenser section 12.
  • the condensed refrigerant drains downwardly on the sloping surfaces 18 and 20, and thence into the channels 24 which lead to the receiver or trap chamber 26.
  • the collected refrigerant in receiver 26 is drawn upwardly through a conduit 28 and thence into the spray means indicated generally by numeral 30, from whence it is discharged downwardly onto the bundle of tubes 45 extending within the evaporator section 14.
  • the evaporated refrigerant is then drawn upwardly by the compressor as previously explained so as to repeat the cycle.
  • the drawings show the refrigerant distributing means as comprising the spray pipes 102 and 104 acting to discharge refrigerant downwardly onto the evaporator tubes.
  • Such a downward Vdischarge is desirable because it promotes dispersion of the refrigerant into fine droplets and provides satisfactory efficiencies.
  • ⁇ It is however possible within the broader aspects of the invention to provide -a distribution means acting to discharge the refrigerant as an upwardly directed spray from adjacent the lower portion of the evaporator.
  • the distribution system might take the form of an axially elongated plate or baffle perforated along its length and receiving refrigerant from the trap chamber to discharge same as -a fine upwardly directed spray.
  • the illustrated arrangement comprises generally a horizontally elongated shell or tube 32 of generally cylindrical cross section. At its opposite ends the shell is provided with the vertical partitions 34 and 36 which serve to mount the end'portions of various heat transfer tubes extending within evaporator section 14 and condenser section 12.
  • the space between the right end of shell 32 and the adjacent vertical partition 34 is subdivided by a horizontal partition 42 and vertical partition 44 to form inlet and outlet chambers for circulating heat exchange fluid such as water through the heat transfer tubes 45 in evaporator section 14.
  • Circulation through tubes 45 is further facilitated by a horizontal partition 47, the arrangement being such that water is pumped through certain of the tubes 45 in the arrow 49 direction from inlet 50 so as to give up some of its heat to the refrigerant in the evaporator section 14. The water is thus directed into a chamber ⁇ 52 at the left end of the shell structure 32 and is returned to the right end of the shell structure through the remaining tubes 45 so as to extract additional heat from the refrigerant surrounding the tubes.
  • Condenser section 12 is provided with tubes 51 and 53 communicating with the spaces on opposite sides of the vertical partition 55, the arrangement being such that the fluid travels in tubes 51 in the arrow 57 direction from inlet 58 to chamber 60 and thence in a reverse direction through tubes 53 for discharge. During its travel through tubes 51 and 53V the heat transfer fluid extracts heat from the refrigerant in condenser section 12 to effect the condensing operations.
  • the shell structure 32 is provided with an elongated partition 64 extending the full distance between vertical partitions 34 and 36 so as to form the aforementioned condenser section 12 and evaporator section 14.
  • the longitudinal partition is provided with two oppositely sloping or slanting sections as shown in FIGS. 2 and 4, so as to form the aforementioned sloping surfaces at 18 and 20 for directing condensate from the condenser section 12.
  • partition 64 is constructed as a double wall structure with thermal insulation 66 in the spaces between the two walls, the purpose in this arrangement being to thermally insulate the condenser section 12 from the evaporator section 14 so as to improve the heat transfer characteristics of the two sections.
  • Partition 64 is connected with an upwardly extending duct or passageway 68 which extends centrally through an intermediate portion of the condenser section 12 so as to communicate with the inlet opening 70 of the compressor 10.
  • the compressor is of the centrifugal type and is provided with a power source in the form of an electric motor 72 having the shaft thereof connected with the varied impeller 74.
  • the varies of the compressor direct refrigerant into the scroll structures generally indicated by numerals 78 and 79.
  • the scroll structures take fluid from the varies 76 at two diametrically spaced points and direct it in two separate streams longitudinally along the upper surface of the shell structure 32, and thence over to respective ones of the inlet openings 86 for the condenser section 12.
  • the two inlet openings 86 are located at widely spaced points along the length of the condenser section, and that the compressed refrigerant from compressor is thereby caused to be given a wide circulation through the condenser.
  • the compressed refrigerant enters the condenser at only one point, in which case some portions of the condenser become relatively ineffective for heat transfer operations.
  • substantially all portions of the condenser become effective as heat transfer areas, and the device can therefore be constructed as a relatively small structure per given refrigeration capacity requirement.
  • the condensed refrigerant drains along the sloping surfaces 18 and 20 into the channels 24 which extend along the outer surfaces of the shell 32.
  • the drawings show four channels 2.4 extending from the condenser section at points spaced along its length. However it will be appreciated that additional channels could be employed if desired, the number and size thereof depending on the capacity of the system.
  • Pipe 28 connects with a spray means 30 as previously explained.
  • This spray means can of course take difyferent forms depending on the type of spraying mechanisms available to the manufacturer and the different :manufacturing facilities utilized in his plant operations.
  • the spray means may consist simply of a cross pipe 100 ⁇ having connection with the pipe 28 and communicating at its ends with the longitudinally extending pipes 102 and 104.
  • Pipes y102 and 104 may be provided with suitable orifices at spaced points therealong to direct liquefied refrigerant in a spray form onto the heat transfer pipes 45 in the evaporator section 14.
  • the partition ⁇ 64 is so arranged with respect to eliminator 108 that, while space is held to a minimum, yet adequate space is available above the surface of the eliminator such that refrigerant can flow unrestricted through the low side of the system without tendency to clog the system after prolonged service.
  • the illustrated system provides features of compact construction which enable the evaporator and condenser to be mounted vwithin a single shell structure with high heat transfer efficiency and performance.
  • the connections between the evaporator, compressor, and condenser are of relatively short length so that the refrigerant is being operated on effectively during a substantial portion of its travel through the system.
  • the system components are arranged so that natural forces are utilized effectively in combination with the force of the compressor to provide an improved circulation of refrigerant through the system.
  • the evaporator section 14 is located directly below the condenser section such that evaporated refrigerant passes through the condenser section during its travel to the compressor.
  • the arrangement lof the evaporator and condenser within a single shell is of further advantage in that increased space is made available for the tubes.
  • the tubes can thereby he arranged so as to dispose a lesser number of tubes in each vertical row.
  • each refrigerant particle traverses a iesser number of tubes and there is lessened tendency for all of the heat transfer to take place at the upper tubes (i.e., before reaching the lower tubes).
  • the refrigerant condenses before it Vreaches the lower tubes, and hence the lower tubes tend to become coated with a condensed refrigerant film which acts as an insulator to reduce heat transfer.
  • the heat transfer action is better distributed or spread out so as to provide an improved overall operating efiiciency or capacity.
  • the cylindrical ,character of the illustrated shell is of material advantage in that the shell acts as a true pressure vessel, thereby permitting construction of the shell with thinner and less costly material than might otherwise he necessary.
  • a self-contained recirculating refrigeration machine having a lower evaporator unit, a medially located condenser unit, and a compressor unit receiving gaseous refrigerant from the evaporator unit, the compressor unit surmounting the condenser and discharging compressed refrigerant thereinto; a horizontally disposed cylindrical shell completely enclosing the condenser unit and the evaporator unit and having at its axial ends heat exchange passages joined -by heat exchange tubes lying parallel to the axis of the shell to completely traverse the condenser and evaporator units, respectively, an axially extending wall element separating the condenser and evaporator units, the lower surfaces of said wall element defining therebetween a flow path for vapor from the lower evaporator to the upper condenser and the upper surfaces of said wall element defining separate partial liquid return passages from the condenser to a lowermost evaporator sump, and axially spaced external iiow passages
  • a horizontally disposed elongated hollow shell a refrigerant evaporator positioned in the lower part of said shell, a refrigerant condenser positioned in the upper part of said shell, la compressor surmounting said shell at a median point thereon, a longitudinally extending wall isolating said evaporator from said condenser and defining a substantial vapor space above said evaporator, a horizontally disposed fluid baffle extending between said evaporator and condenser in a median portion of said vapor space, a gaseous refrigerant conduit extending through said wall and connecting said compressor in intake relation to said vapor space, said compressor being exhaust connected to said condenser -by two generally axially extending scroll structures superimposed on top of said shell and each having the inner end connected with said compressor and the outer end connected with spaced portions of the condenser at either side of the compressor ifor uniform distribution of compressed ref
  • a horizontally disposed, hollow shell divided by a longitudinal, interior wall into an upper condenser compartment, a :lower evaporator compartment and defining a vapor space above the evaporator compartment,
  • a horizontally disposed and elongated uid baffle extending the length of said shell and positioned in a median section of said vapor space
  • a compressor mounted at the top of said shell and intake fluid connected to the evaporator by a passage extending through said llongitudinal interior wall
  • said wall sloping downwardly and outwardly interiorly of said shell to dene a central substantially axially extending vapor passage communicating with said evaporator compartment and isolated from said condenser compartment and forming the bottom wall of said condenser compartment to catch liquid refrigerant pro-duced in said condenser compartment,
  • conduit means extending from said sump into the upper portion of said evaporator compartment to form a downward spray therein.
  • a horizontally disposed and elongated hollow shell divided by an axially extending interior wall into an Kaxially extending evaporator compartment and an axially extending condenser compartment with a vapor space above the evaporator compartment,
  • said shell having -at its ends heat-exchange passages joined by axially extending heat-exchange tubes,
  • a compressor mounted on top of said shell and uid connected to said evaporator compartment by a passage extending through said shell,
  • conduit means connecting said compressor in fluid How relation to said condenser compartment
  • conduit means to conduit liquid refrigerant from said condenser compartment into said evaporator compartment.

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  • 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)
US18607A 1960-03-30 1960-03-30 Refrigeration machine including compressor, condenser and evaporator Expired - Lifetime US3096630A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18607A US3096630A (en) 1960-03-30 1960-03-30 Refrigeration machine including compressor, condenser and evaporator
CH350361A CH391748A (fr) 1960-03-30 1961-03-23 Machine à froid
BE601693A BE601693A (fr) 1960-03-30 1961-03-23 Machine frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US18607A US3096630A (en) 1960-03-30 1960-03-30 Refrigeration machine including compressor, condenser and evaporator

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US3096630A true US3096630A (en) 1963-07-09

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US (1) US3096630A (fr)
BE (1) BE601693A (fr)
CH (1) CH391748A (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3453809A (en) * 1968-05-27 1969-07-08 Joseph H Henderson Air drying unit
US4972683A (en) * 1989-09-01 1990-11-27 Blackstone Corporation Condenser with receiver/subcooler
US6481242B2 (en) * 2000-06-07 2002-11-19 Mitsubishi Heavy Industries, Ltd. Condenser and freezer
US20090049861A1 (en) * 2007-08-21 2009-02-26 Wolverine Tube, Inc. Heat Exchanger with Sloped Baffles
US20090173087A1 (en) * 2008-01-04 2009-07-09 Parata Systems, Llc Device and Method for Evaporating Water from a Compressor
US20110220100A1 (en) * 2008-09-18 2011-09-15 Tongaat Hulett Limited Continuous vacuum pan and internal insulation arrangement thereof
EP2641036A4 (fr) * 2010-11-16 2016-08-17 Zahid Hussain Ayub Évaporateur à couche mince
CN106705500A (zh) * 2015-11-12 2017-05-24 浙江万享科技股份有限公司 蒸发器
US20170191714A1 (en) * 2016-01-06 2017-07-06 Johnson Controls Technology Company Vapor compression system
US20180306519A1 (en) * 2015-10-21 2018-10-25 Technip France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1575818A (en) * 1921-04-05 1926-03-09 Carrier Engineering Corp Refrigerating system and method of refrigeration
CH158939A (de) * 1930-08-11 1932-12-15 Bbc Brown Boveri & Cie Stopfbüchsenlose, vollständig gekapselte Kompressions-Kältemaschine.
FR739288A (fr) * 1931-11-23 1933-01-09 Brown Calorifugeage intérieur pour machines frigorifiques blindées dont l'évaporateur etle condenseur sont disposés côte à côte
US2059725A (en) * 1934-03-09 1936-11-03 Carrier Engineering Corp Shell and tube evaporator
US2266107A (en) * 1938-09-30 1941-12-16 Buensod Stacey Air Conditionin Centrifugal refrigerating apparatus
US2277647A (en) * 1940-08-01 1942-03-24 Carrier Corp Refrigeration
US2724246A (en) * 1954-04-01 1955-11-22 Charles E Lowe Method and means for improving the utilization of volatile refrigerants in heat exchangers
US2992543A (en) * 1958-03-21 1961-07-18 Trane Co Refrigeration machine with capacity control means

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1575818A (en) * 1921-04-05 1926-03-09 Carrier Engineering Corp Refrigerating system and method of refrigeration
CH158939A (de) * 1930-08-11 1932-12-15 Bbc Brown Boveri & Cie Stopfbüchsenlose, vollständig gekapselte Kompressions-Kältemaschine.
FR739288A (fr) * 1931-11-23 1933-01-09 Brown Calorifugeage intérieur pour machines frigorifiques blindées dont l'évaporateur etle condenseur sont disposés côte à côte
US2059725A (en) * 1934-03-09 1936-11-03 Carrier Engineering Corp Shell and tube evaporator
US2266107A (en) * 1938-09-30 1941-12-16 Buensod Stacey Air Conditionin Centrifugal refrigerating apparatus
US2277647A (en) * 1940-08-01 1942-03-24 Carrier Corp Refrigeration
US2724246A (en) * 1954-04-01 1955-11-22 Charles E Lowe Method and means for improving the utilization of volatile refrigerants in heat exchangers
US2992543A (en) * 1958-03-21 1961-07-18 Trane Co Refrigeration machine with capacity control means

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3453809A (en) * 1968-05-27 1969-07-08 Joseph H Henderson Air drying unit
US4972683A (en) * 1989-09-01 1990-11-27 Blackstone Corporation Condenser with receiver/subcooler
WO1991003692A1 (fr) * 1989-09-01 1991-03-21 Blackstone Corporation Condenseur avec recepteur/sous-refroidisseur
US6481242B2 (en) * 2000-06-07 2002-11-19 Mitsubishi Heavy Industries, Ltd. Condenser and freezer
US20090049861A1 (en) * 2007-08-21 2009-02-26 Wolverine Tube, Inc. Heat Exchanger with Sloped Baffles
US8220658B2 (en) 2008-01-04 2012-07-17 Parata Systems, Llc Device and method for evaporating water from a compressor
US8113492B2 (en) * 2008-01-04 2012-02-14 Parata Systems, Llc Device and method for evaporating water from a compressor
US20090173087A1 (en) * 2008-01-04 2009-07-09 Parata Systems, Llc Device and Method for Evaporating Water from a Compressor
US20110220100A1 (en) * 2008-09-18 2011-09-15 Tongaat Hulett Limited Continuous vacuum pan and internal insulation arrangement thereof
US8277562B2 (en) * 2008-09-18 2012-10-02 Tongaat Hulett Limited Continuous vacuum pan and internal insulation arrangement thereof
EP2641036A4 (fr) * 2010-11-16 2016-08-17 Zahid Hussain Ayub Évaporateur à couche mince
US20180306519A1 (en) * 2015-10-21 2018-10-25 Technip France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method
US11686531B2 (en) * 2015-10-21 2023-06-27 Technip Energies France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method
CN106705500A (zh) * 2015-11-12 2017-05-24 浙江万享科技股份有限公司 蒸发器
US20170191714A1 (en) * 2016-01-06 2017-07-06 Johnson Controls Technology Company Vapor compression system
US10458687B2 (en) * 2016-01-06 2019-10-29 Johnson Controls Technology Company Vapor compression system

Also Published As

Publication number Publication date
BE601693A (fr) 1961-09-25
CH391748A (fr) 1965-05-15

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