EP0026400A2 - Verfahren und Apparat zum Erfüllen des Wärme- und Kältebedarfs - Google Patents

Verfahren und Apparat zum Erfüllen des Wärme- und Kältebedarfs Download PDF

Info

Publication number
EP0026400A2
EP0026400A2 EP80105577A EP80105577A EP0026400A2 EP 0026400 A2 EP0026400 A2 EP 0026400A2 EP 80105577 A EP80105577 A EP 80105577A EP 80105577 A EP80105577 A EP 80105577A EP 0026400 A2 EP0026400 A2 EP 0026400A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure side
high pressure
refrigeration unit
vapor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP80105577A
Other languages
English (en)
French (fr)
Other versions
EP0026400B1 (de
EP0026400A3 (en
Inventor
Gary S. Leonard
Raymond L. Eckman
Thomas M. Zinsmeyer
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 US06/078,877 external-priority patent/US4254631A/en
Priority claimed from US06/078,878 external-priority patent/US4254632A/en
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP0026400A2 publication Critical patent/EP0026400A2/de
Publication of EP0026400A3 publication Critical patent/EP0026400A3/en
Application granted granted Critical
Publication of EP0026400B1 publication Critical patent/EP0026400B1/de
Expired legal-status Critical Current

Links

Images

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
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements

Definitions

  • This invention relates generally to methods and apparatus for simultaneously satisfying heating and cooling demands.
  • Refrigeration apparatus or machines are frequently employed to cool a fluid such as water which is circulated through various rooms or enclosures of a building to cool these areas. Often, the refrigerant of such machines rejects a relatively large amount of heat at the condenser of the machine. This rejected heat is commonly dissipated to the atmosphere, either directly or via a cooling fluid that circulates between the condenser and a cooling tower. Over a period of time, the rejected heat represents a substantial loss of energy, and much attention has been recently directed to reclaiming or recovering this heat to satisfy a heating load or demand.
  • One general approach to reclaiming this heat is to employ a booster compressor to draw and further compress refrigerant from the condenser of the refrigeration machine. This further compressed vapor is then passed through a separate, heat reclaiming condenser. A heat transfer fluid is circulated through the heat reclaiming condenser in heat transfer relation with the refrigerant passing therethrough. Heat is transferred from the refrigerant to the heat transfer fluid, heating the fluid and condensing the refrigerant. The heated heat transfer fluid may then be used to satisfy a present heating load or the fluid may be stored for later use, and the condensed refrigerant is returned to the cooling circuit for further use therein.
  • the refrigerant flow a rate through the heating circuit is relatively large and a relatively large portion of the refrigerant discharged from the compressor of the cooling circuit is drawn into the booster compressor and passed through the heating circuit.
  • the refrigerant flow rate through the booster compressor may temporarily exceed the rate at which refrigerant is discharged from the compressor of the cooling circuit.
  • the mass of refrigerant vapor in the condenser of the cooling circuit decreases, decreasing the pressure therein. This, in turn, decreases the pressure at the inlet of the booster compressor.
  • the temperature of the vapor discharged from the booster compressor may become undesirably high, or the booster compressor may enter what is known as surge conditions wherein there are periodic complete flow reversals in the compressor, destroying the efficiency of the compressor and endangering the integrity of the elements thereof.
  • the present invention relates to apparatus for satisfying heating and cooling demands comprising a cooling circuit including a mechanical refrigeration unit having a low pressure side and a high pressure side, a heating circuit including a booster compressor for drawing and further compressing refrigerant from the high pressure side of the refrigeration unit, and a heat reclaiming condenser for passing the further compressed refrigerant vapor in heat transfer relation with a heat transfer fluid to heat the fluid and condense the refrigerant vapor.
  • the apparatus also comprises a control for reducing the vapor flow rate through the booster compressor when the pressure in the high pressure side of the refrigeration unit falls below a predetermined value.
  • Machine 10 includes, generally, cooling circuit 12 and heating circuit 14.
  • Cooling circuit 12 includes primary compressor means such as first stage 16 of two stage compressor 18, primary condenser 20, primary expansion means 22, and evaporator 24.
  • Heating circuit 14 includes booster compressor means such as second stage 26 of compressor 18, heat reclaiming condenser 30, and auxiliary expansion means 32.
  • Inlet guide vanes 34 are provided to control the vapor flow through first stage 16 of compressor 18 and, thus, through cooling circuit 12, while valve 36 is utilized to regulate the vapor flow through second stage 26 of compressor 18 and, hence, through heating circuit 14.
  • Pressure sensor means 38 preferably including two pressure switches 40 and 42, is in vapor communication with primary condenser 20 to control valve 36 in a manner more fully discussed below.
  • Motor or drive means (not shown) is employed in a manner which will be apparent to those skilled in the art to simultaneously drive first and second stages 16 and 26 of compressor 18.
  • first stage 16 of compressor 18 discharges hot, compressed refrigerant vapor into primary condenser 20 via line 44.
  • Refrigerant passes through primary condenser 20, rejects heat to an external heat exchange medium such as water circulating through heat exchange coil 46 located therein, and condenses.
  • the condensed refrigerant flows through primary expansion means 22, reducing the temperature and pressure of the refrigerant.
  • the expanded refrigerant enters and passes through evaporator 24 and absorbs heat from an external heat transfer medium such as water passing through heat exchange coil 50 which is positioned within the evaporator.
  • the heat transfer medium is thus cooled and the refrigerant is evaporated.
  • the cooled heat transfer medium may then be used to satisfy a cooling load, and the evaporated refrigerant is drawn from evaporator 24 into line 52 leading back to first stage 16 of compressor 18.
  • first stage 16 of compressor 18 and primary expansion means 22 separate cooling circuit 12 into high pressure side 54 and low pressure side 56, and booster inlet line 58 is provided for transmitting refrigerant vapor from the high pressure side of the cooling circuit to second stage 26 of compressor 18.
  • inlet line 58 is connected to primary condenser 20 and transmits a portion of the refrigerant vapors passing therethrough to second stage 26 of compressor 18.
  • line 58 could be connected to discharge line 44.
  • Second stage 26 of compressor 18 further compresses the vapor transmitted thereto, further raising the temperature and pressure of the vapor. This further compressed vapor is discharged into line 60, leading to heat reclaiming condenser 30.
  • the refrigerant vapor enters and passes through heat reclaiming condenser 30 in heat transfer relation with a heat transfer fluid such as water passing through heat exchange coil 62 disposed within the heat reclaiming condenser. Heat is transferred from the refrigerant vapor to the fluid passing through coil 62, heating the fluid and condensing the refrigerant. The heated heat transfer fluid may then be employed to satisfy a heating load.
  • Refrigerant condensed in heat reclaiming condenser 30 passes therefrom back to cooling circuit 12 via return means including auxiliary expansion means such as orifice 32 and refrigerant lines 64 and 66.
  • condensed refrigerant from heat reclaiming condenser 30 flows through orifice 32 via line 64, reducing the pressure and temperature of the refrigerant.
  • Refrigerant line 66 transmits refrigerant from orifice 32 back to cooling circuit 12, specifically primary expansion means 22 thereof, for further use in the cooling circuit.
  • Guide vanes 34 may be controlled in response to any one or more of a number of factors indicative of changes in the load on cooling circuit 12 to vary the capacity thereof. For example, guide vanes 34 may be controlled in response to the temperature of the fluid leaving heat exchanger 50 of evaporator 24. As the cooling load increases or decreases, guide vanes 34 move between minimum and maximum vapor flow positions to increase or decrease, respectively, the vapor flow rate through first stage 16 of compressor 18 and, thus, cooling circuit 12. Similarly, valve 36 may be controlled in response to any one or more factors indicating changes in the load on heating circuit 14 to vary the capacity thereof. For example, valve 36 may be controlled in response to the temperature of the fluid discharged from heat exchanger 62 of heat reclaiming condenser 30.
  • positioning means 68 moves valve 36 between minimum and maximum vapor flow positions to increase or decrease, respectively, the vapor flow rate through second stage 26 of compressor 18 and, hence, through heating circuit 14.
  • Positioning means 68 may be of any suitable type, for example an electric, hydraulic or pneumatic device.
  • positioning means 68 includes a reversible electric motor that is selectively connected to a source of electrical energy to move valve 36.
  • machine 10 includes control means for reducing the vapor flow rate through second stage 26 of compressor 18 when the pressure in the high pressure side 54 of cooling circuit 12 falls below a first predetermined value or set point. More specifically, the above-mentioned reducing means includes pressure sensor 38 and positioning means 68. Positioning means 68 is connected to sensor 38 and, as mentioned above, to valve 36.
  • Positioning means 68 and sensor 38 cooperate for moving valve 36 toward its minimum flow position to decrease the vapor flow rate through second stage 26 of compressor 18 when the pressure of vapor in primary condenser 20 falls below the first predetermined value.
  • positioning means 68 continues to move valve 36 toward its minimum flow position if the pressure in primary condenser 20 remains below the first predetermined value, further reducing the vapor flow rate through heating circuit 14.
  • the rate at which vapor is drawn from primary condenser 20 by heating circuit 14 is reduced until that vapor flow rate matches or becomes less than the rate at which vapor enters the primary condenser via primary compressor 16. This tends to maintain the mass of refrigerant vapor in primary condenser 20 at or above a stable value.
  • the pressure in primary condenser 20 may be maintained at or above a level sufficient to prevent second stage 26 of compressor 18 from entering surge conditions or from discharging vapor at an excessively high temperature.
  • sensor 38 ceases to cause positioning means 68 to move valve 36 toward its minimum flow position.
  • valve 36 may still be moved toward its minimum flow position for other reasons such as a decrease in the load on heating circuit 14.
  • sensor 38 also senses when the pressure in primary condenser 20 falls below a second predetermined level or set point, greater than the above-discussed first predetermined level. When this event is sensed, positioning means 68 is prevented from moving valve 36 toward its maximum flow position. This tends to prevent the rate at which vapor is drawn from primary condenser 20 by heating circuit 14 from increasing due to, for example, an increase in the load on heating circuit 14. This, in turn, tends to prevent the pressure in the primary condenser from further decreasing.
  • pressure sensor 38 may be of any suitable type such as an electric, hydraulic, or pneumatic device. Since positioning means 68 preferably includes a reversible electric motor, pressure sensor 38 preferably includes first and second pressure switches 40 and 42. Switch 40 senses when the pressure in primary condenser 20 falls below the second set point to disconnect the electric motor from the source of electrical energy to disable the motor from opening valve 36, while switch 42 senses when the pressure in primary condenser 20 falls below the first set point to connect the electric motor to the electrical energy source for closing valve 36. As shown in the drawing, switches 40 and 42 are disposed in chamber 70 which is in vapor communication with primary condenser 20 via tap-off line 72.
  • Refrigeration machine 10 incorporating teachings of the present invention may be effectively employed to prevent the booster compressor from entering surge conditions or from discharging vapor at undesirably high temperatures when the_ machine is called upon to simultaneously satisfy a low cooling load and a high heating load. Moreover, as may be understood from a review of the above discussion, these beneficial results may be achieved in a very reliable and inexpensive manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP80105577A 1979-09-26 1980-09-17 Verfahren und Apparat zum Erfüllen des Wärme- und Kältebedarfs Expired EP0026400B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US06/078,877 US4254631A (en) 1979-09-26 1979-09-26 Method and apparatus for satisfying heating and cooling demands and control therefor
US78878 1979-09-26
US06/078,878 US4254632A (en) 1979-09-26 1979-09-26 Method and apparatus for satisfying heating and cooling demands and control therefor
US78877 1979-09-26

Publications (3)

Publication Number Publication Date
EP0026400A2 true EP0026400A2 (de) 1981-04-08
EP0026400A3 EP0026400A3 (en) 1981-08-26
EP0026400B1 EP0026400B1 (de) 1984-11-28

Family

ID=26761047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80105577A Expired EP0026400B1 (de) 1979-09-26 1980-09-17 Verfahren und Apparat zum Erfüllen des Wärme- und Kältebedarfs

Country Status (9)

Country Link
EP (1) EP0026400B1 (de)
AR (1) AR228040A1 (de)
AU (1) AU534650B2 (de)
BR (1) BR8006153A (de)
CA (1) CA1122024A (de)
DE (1) DE3069715D1 (de)
ES (2) ES8200466A1 (de)
MX (1) MX153394A (de)
NZ (1) NZ195051A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN121083385A (zh) * 2025-11-12 2025-12-09 山东辰榜数控装备有限公司 一种用于机床冷却系统的冷却液散热装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH129380A (de) * 1927-10-01 1928-12-17 Escher Wyss Maschf Ag Zwischenbehälter von Kälteanlagen mit mehrstufigem Verdichter.
CH234063A (de) * 1941-11-19 1944-09-15 Sulzer Ag Wärmepumpenanlage mit mindestens zwei Verdichterstufen.
CH241603A (de) * 1944-07-01 1946-03-31 Bbc Brown Boveri & Cie Wärmepumpenanlage mit Turboverdichtern, die bei ihrem Lauf mit gleichbleibender Drehzahl angetrieben werden.
US2921445A (en) * 1956-02-17 1960-01-19 Carrier Corp Centrifugal refrigeration machines
US2921446A (en) * 1956-11-02 1960-01-19 Carrier Corp Refrigeration machine
DE1051878B (de) * 1957-03-02 1959-03-05 Licencia Talalmanyokat Verfahren fuer den kombinierten Betrieb von Kaeltemaschine und Waermepumpe sowie Einrichtung zum Ausueben des Verfahrens
US3011322A (en) * 1958-08-12 1961-12-05 Dresser Operations Inc Stabilization of refrigeration centrifugal compressor
US3303664A (en) * 1965-04-30 1967-02-14 Refrigerating Specialties Comp Refrigeration system having a back pressure valve
US3668883A (en) * 1970-06-12 1972-06-13 John D Ruff Centrifugal heat pump with overload protection
US3635041A (en) * 1970-07-13 1972-01-18 Carrier Corp Heating and cooling refrigeration apparatus
US3665724A (en) * 1970-07-13 1972-05-30 Carrier Corp Heating and cooling refrigeration apparatus
DE2837695A1 (de) * 1977-08-29 1979-03-15 Carrier Corp Verfahren und vorrichtung zur wirkungsgradverbesserung in einer kuehlanlage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN121083385A (zh) * 2025-11-12 2025-12-09 山东辰榜数控装备有限公司 一种用于机床冷却系统的冷却液散热装置

Also Published As

Publication number Publication date
AU534650B2 (en) 1984-02-09
ES8206003A1 (es) 1982-07-01
ES499019A0 (es) 1982-07-01
AR228040A1 (es) 1983-01-14
NZ195051A (en) 1984-05-31
DE3069715D1 (en) 1985-01-10
EP0026400B1 (de) 1984-11-28
CA1122024A (en) 1982-04-20
AU6267080A (en) 1981-04-09
ES495325A0 (es) 1981-10-16
ES8200466A1 (es) 1981-10-16
BR8006153A (pt) 1981-04-07
EP0026400A3 (en) 1981-08-26
MX153394A (es) 1986-10-07

Similar Documents

Publication Publication Date Title
US4527399A (en) High-low superheat protection for a refrigeration system compressor
US5050394A (en) Controllable variable speed heat pump for combined water heating and space cooling
KR890003630B1 (ko) 냉동 시스템의 냉동팽창밸브 제어장치 및 방법
US4538422A (en) Method and control system for limiting compressor capacity in a refrigeration system upon a recycle start
US4230470A (en) Air conditioning system
US4535607A (en) Method and control system for limiting the load placed on a refrigeration system upon a recycle start
CA1121803A (en) Heat reclaiming method and apparatus
US4974420A (en) Control method and apparatus for refrigeration system
US4025326A (en) Heat reclaiming system
US4254631A (en) Method and apparatus for satisfying heating and cooling demands and control therefor
US4254632A (en) Method and apparatus for satisfying heating and cooling demands and control therefor
CA1122024A (en) Method and apparatus for satisfying heating and cooling demands and control therefor
US4309876A (en) Method and apparatus for satisfying heating and cooling demands and control therefor
US4534181A (en) Cooling system
EP0042434A1 (de) Verfahren zum verstärken von wärme
US4262488A (en) System and method for controlling the discharge temperature of a high pressure stage of a multi-stage centrifugal compression refrigeration unit
CA1129219A (en) Method and apparatus for satisfying heating and cooling demands and control therefor
US3133426A (en) Refrigeration apparatus for operation under low head pressures
US3362188A (en) Refrigeration system including high pressure protection
GB2035529A (en) Providing cooled air in an outside broadcast vehicle
JPS6383556A (ja) 冷凍サイクル
JPS5838369Y2 (ja) クウキチヨウワキ
JPS61208472A (ja) 太陽熱利用温水装置
JPS5822054Y2 (ja) クウキチヨウワキ
JPH0141907B2 (de)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19820108

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 3069715

Country of ref document: DE

Date of ref document: 19850110

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19910906

Year of fee payment: 12

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19910930

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19930528

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19930602

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19930907

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19940917

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19940917