EP0329199A1 - Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter - Google Patents

Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter Download PDF

Info

Publication number
EP0329199A1
EP0329199A1 EP89106280A EP89106280A EP0329199A1 EP 0329199 A1 EP0329199 A1 EP 0329199A1 EP 89106280 A EP89106280 A EP 89106280A EP 89106280 A EP89106280 A EP 89106280A EP 0329199 A1 EP0329199 A1 EP 0329199A1
Authority
EP
European Patent Office
Prior art keywords
compressor
steam
liquid
heat
heat pump
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.)
Withdrawn
Application number
EP89106280A
Other languages
English (en)
French (fr)
Inventor
Hajime Endou
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.)
Mitsui Engineering and Shipbuilding Co Ltd
Original Assignee
Mitsui Engineering and Shipbuilding Co Ltd
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 JP6475086A external-priority patent/JPS62223579A/ja
Priority claimed from JP12468286A external-priority patent/JPS62284154A/ja
Application filed by Mitsui Engineering and Shipbuilding Co Ltd filed Critical Mitsui Engineering and Shipbuilding Co Ltd
Priority to EP89106280A priority Critical patent/EP0329199A1/de
Publication of EP0329199A1 publication Critical patent/EP0329199A1/de
Withdrawn legal-status Critical Current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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a method of curtailing the power required for driving a compressor in a heat pump and to a compressor operating according to such a method.
  • Compression-type heat pumps comprise an evaporator which absorbs heat energy from a lower temperature heat source, a compressor which adiabatically compresses the working fluid vapor evaporated by the evaporator, a condenser which provides heat energy to a higher temperature heat sink by condensation of heat medium vapor having a temperature and a pressure raised by the compressor, and an expansion valve which flashes and expands the heat medium condensate formed in the condenser, wherein an arrangement is made such that from the expansion valve, the working fluid is sent back to the evaporator.
  • Displacement compressors are simple in structure and, in addition, can provide a constant pressure ratio even under partial loading conditions by changing the number of rotation, so that they are suitably useful in or for heat pumps or heat pump systems.
  • the volume of fluid that they can deal with is relatively limited and also their volume efficiency tends to lower under partial loading conditions, whereby it has been difficult to realize a scale-up of heat pumps with use of a displacement compressor.
  • centrifugal-type compressors characteristically have a large capacity of fluid compression in spite of their being relatively limited in size.
  • the power required for driving the compressor becomes greater and the coefficient of performance (the transferred heat/the power input for the driving of the compressor - hereinafter referred to as COP -) becomes lowered.
  • the present invention reduces the power required for the driving of the compressor.
  • the present invention atomizes and injects cooling liquid from an injection valve into superheated vapor which is in a compression process, and evaporates the cooling liquid. In this manner, isothermal compression or a compression approximate to it can be effected due to the cooling effect by evaporation, and the power necessary for driving the compressor can be reduced.
  • this method can be applied most optimally to a compressor of the reciprocating type, it can be applied also to a compressor of the screw type and the vane type and further to turbo compressors.
  • This method can directly atomize the cooling liquid in a quantity matching with the existing state of the vapor during the compression process, and can control the temperature of the vapor during the compression by evaporation of cooling liquid.
  • the present invention further proposes to make use of water for the working medium, and although in the following description of the invention water is termed to mean the working fluid, liquid or medium and steam is termed to represent vapor, it will be appreciated that this is not in any sense to limit the scope of the invention, which is to be understood to cover broadly the use of any other suitable working medium or fluid.
  • this compression heat pump comprises an evaporator 11 for absorbing heat energy from a low temperature heat source, a compressor 17 for adiabatically compressing a heat medium steam from the evaporator 11, a condenser 19 for providing the heat energy to a higher temperature heat sink from the heat medium whose temperature and pressure are elevated by the compressor 17, and an expansion valve 22 for flushing and expanding the heat medium liquefied in the condenser 19.
  • the heat medium is returned from the expansion valve 22 to the evaporator 11.
  • Fig. 2 is a diagram of a heat pump including the present invention.
  • the heat medium supplied from a piping arrangement 12 to an evaporator 11 absorbs heat from a low temperature heat source 13 and evaporates and turns into steam S1, which is introduced into a foreside stage compressor 15 through another piping arrangement 14.
  • the steam S1 is compressed into an intermediate pressure steam S2 by the compressor 15 and is introduced to another compressor 17 through a piping 16.
  • the steam is compressed by the compressor 17 to a high temperature and high pressure steam S3, which is supplied to a desuperheater 37 disposed at an intermediate portion of a piping 18.
  • the desuperheater 37 has a nozzle 38, and the superheated steam S3 makes direct heat exchange with a liquid heat medium atomized from this nozzle 38, and is cooled near to saturation and is changed to a substantially saturated steam S4.
  • This saturated steam S4 is supplied to a condenser 19 through the piping 18. Since the heat medium atomized from the nozzle 38 evaporates and turns into a steam, too, the quantity of steam introduced into the condenser 19 increases.
  • the heat medium is atomized and sprayed into the compressor 17 through a pipe 36.
  • the foreside stage compressor 15 is connected to a later-appearing expansion turbine 28 by a shaft 26, thereby forming a steam supercharger 25.
  • the heat energy of the saturated steam S4 is supplied to the high temperature heat sink 20 and is condensed.
  • the heat medium liquid L condensed in the condenser 19 makes indirect heat exchange with a later-appearing steam S5 in a superheater 41 disposed at an intermediate portion of the piping 21 and is then expanded by the expansion valve 22. Thereafter, the heat medium liquid L is separated into a liquid L1 and a steam S5 by a vapor-liquid separator 23.
  • the steam S5 is introduced into the superheater 41 through a piping 24, makes heat exchange with the heat medium liquid L derived from the condenser 19 and is heated to a superheated steam S6.
  • This superheated steam S6 is introduced into the expansion turbine 28 for driving the foreside stage compressor 15 through a conduit 27.
  • the steam S6 is expanded to a pressure below that of the evaporator and preferably, to vacuum, and a steam S7 derived therefrom is sent to a condenser 30 through a piping arrangement 29, where it is condensed to a low temperature liquid L2.
  • the heat medium liquid atomized from m of the compressor 17 and n of the desuperheater 37 it is possible to use the heat medium liquid recirculated from the piping 12 to the evaporator 11 of this system or the heat medium liquid L derived from the condenser 19 or the heat medium liquid L1 derived from the vapor-liquid separator 23, but it is recommended to use the heat medium liquid L1 in the present invention.
  • the pressure of the heat liquid medium is raised by the pump 35 disposed at the intermediate portion of the piping 36 branched from the piping 34 and the heat medium liquid is then atomized and injected into the compressor 17 from a nozzle (not shown) at the tip of the pipe 36.
  • the heat medium liquid is atomized and injected from the nozzle 38 of the desuperheater 37 from the piping 39 branched from the piping 36.
  • the reference numeral 40 represents a motor and 46 a pressure control valve.
  • Fig. 3 is a Morrie diagram of the heat pump system shown in Fig. 2.
  • Fig. 4 shows a fundamental system for converting the internal energy of the condensate in the condenser 19 to the power.
  • the condensate is flashed by the expansion valve 22 and the resulting steam is supplied to the steam expansion turbine 28.
  • the resulting power is used as part of the driving force for the compressor 17.
  • Some conventional expansion turbines assembled in the heat pump are based upon the concept of expanding the steam to the evaporation pressure of the evaporator such as a total flow expander but they supply the resulting steam as such to the compressor.
  • the resulting steam is expanded to a pressure below the evaporation pressure and preferably, to vacuum, and sufficiently great power is recovered. It is necessary to condense the expanded steam by the condenser 30 and to raise its pressure to the evaporation pressure by the pump 32, but the power necessary therefor can be neglected.
  • the compressor 17 and the expansion turbine 28 are directly connected by the shaft 47.
  • Fig. 5 is a Morrie diagram which explains the operation of Fig. 4 and symbols a, b, c, e, f, f′, f ⁇ , g and h correspond to the respective positions in Fig. 5.
  • Fig. 6 is a diagram of a system accomplishing the concept of Fig. 4 as an actual system, wherein the compressor 17 is a displacement compressor.
  • the expansion turbine 28 is a steam turbine which is a turbo machine and the compressor 15 to be driven by the steam turbine is a turbo compressor which is also a turbo machine, and they are directly connected by the shaft 26, thereby forming a steam turbocharger 25. Since the turbo machine rotates at a high speed, it is small in size and since it supercharges the displacement compressor, the latter can be made compact in size. Therefore, the cost of production can be reduced.
  • the condensed hot water moves from e to e′ and in this instance, emits the heat and heats the flashed steam. Therefore, the steam shifts from the saturated state f ⁇ to the superheated state F′′′. Since the steam is introduced into the turbine 28 in this superheated state, a greater expansion ratio can be secured without causing an excessive drop of the quality (dryness) of the steam at the turbine outlet.
  • Fig. 8 is a Morrie diagram of the heat pump system shown in Fig. 7.
  • the positions represented by symbols, a, b, b′, c, e, e′, f, f′, f ⁇ , f′′′, g and h represent the same positions as those in Fig. 7.
  • Fig. 10 is a system flow diagram when the recovered power of the present invention exceeds the power necessary for compressing the steam. In such a case, some start means are necessary and the heat pump operates without external power. In case of system performance at a condensation temperature of 300° C as shown in Fig. 11, the system shown in Fig. 10 can be operated at an evaporation temperature of above 250° C and since there is no external power in this case, the COP becomes indefinite.
  • the superheated steam S3 having a high temperature and a high pressure which is compressed by the compressor 17 is supplied to the desuperheater 37 disposed at an intermediate portion of the piping 18.
  • This desuperheater 37 has the nozzle 38, and the liquid heat medium atomized from this nozzle 38 cools the superheated steam S3 into saturation.
  • the saturated steam S4 is supplied to the condenser 19 through the piping 18.
  • the heat medium atomized from the nozzle 38 turns into the steam, too, and is therefore supplied to the condenser 19, where the quantity of steam thus increases.
  • the flash steam quantity increases and contributes to the increase in the output of the expansion turbine 28. Since the output of the expansion turbine 28 is thus increased, the compression ratio of the foreside stage compressor 15 increases so that the power necessary for driving the motor 40 for driving the compressor 17 can be reduced.
  • Fig. 13 is a Morrie diagram of the heat pump system shown in Fig. 12 and symbols a, b, c, d, e, f, f′, f ⁇ , g and h represent the same conditions at the positions represented by the same reference numerals in Fig. 12.
  • Fig. 14 shows a case where intermediate cooling is effected in order to reduce the compressor power.
  • the flash liquid L1 is injected into the cooler 50 disposed at the intermediate portion between the compressors 17a and 17b in order to reduce the temperature by direct heat exchange and evaporation. Since the flash steam quantity increases for the same reason as shown in Fig. 12, the recovered power increases and the COP increases, too.
  • Fig. 15 is a Morrie diagram in the compression stroke when intermediate cooling is effected.
  • the present invention uses a displacement compressor as the compressor 17, injects the liquid into the steam during its compression stroke, controls the compression temperature by the evaporation of the steam and brings the compression close to isothermal compression.
  • the liquid-atomizing type steam compressor 1 includes a piston 3 which reciprocates inside a cylinder 2 and a suction valve 5, a delivery valve 6 and a liquid atomizing valve 4 that are disposed at a cylinder head 2a.
  • the liquid atomizing valve 4 is specifically disposed in order to practise the present invention. Its operation timing is regulated so that when the piston 3 moves to the right and compresses the steam, the valve 4 atomizes the cooling liquid into the cylinder 2.
  • the opening and closing timing of the liquid atomizing valve 4 is regulated so that it stops atomization of the cooling liquid when the pressure inside the cylinder 2 reaches a predetermined value.
  • liquid injection into a compressor has been known in the past, but the present invention is characterized in that the temperature control is effected while the steam is in the superheated state, makes direct heat exchange with the liquid and evaporates.
  • the curve M represents the increase of enthalpy of the steam with respect to the piston stroke x in the conventional steam compression method by adiabatic compression while the curve N represents that of the liquid atomizing system according to the present invention.
  • curve A - B represents a saturated liquid line while curve C - D represents a saturated steam line.
  • a saturated steam H (60° C, 0.203 ata) is compressed to a steam I (110° C, 0.28 ata) and turned into a superheated steam.
  • the cooling liquid W exchanges heat with the superheated steam from a point (85° C, 0.28 ata) on the curve A - B and evaporates, thereby cooling the steam S.
  • the curve I - J and the curve C - D have the temperature difference of 25° C for the same pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP89106280A 1986-03-25 1986-10-10 Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter Withdrawn EP0329199A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP89106280A EP0329199A1 (de) 1986-03-25 1986-10-10 Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP64750/86 1986-03-25
JP6475086A JPS62223579A (ja) 1986-03-25 1986-03-25 ヒ−トポンプシステム
JP12468286A JPS62284154A (ja) 1986-05-31 1986-05-31 ヒ−トポンプシステム
JP124682/86 1986-05-31
EP89106280A EP0329199A1 (de) 1986-03-25 1986-10-10 Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP86201755.5 Division 1986-10-10

Publications (1)

Publication Number Publication Date
EP0329199A1 true EP0329199A1 (de) 1989-08-23

Family

ID=27232354

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89106280A Withdrawn EP0329199A1 (de) 1986-03-25 1986-10-10 Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter

Country Status (1)

Country Link
EP (1) EP0329199A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0423976A1 (de) * 1989-10-17 1991-04-24 Copeland Corporation Kompressorkälteanlage mit Bedarfskühlung
EP3280892A4 (de) * 2015-04-07 2018-03-21 Conoco Phillips Company System zum abschrecken eines kältekreislaufs einer erdgasverflüssigungsanlage mit und verfahren zum abschrecken

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE645746C (de) * 1936-06-17 1937-06-03 Georges Loeffler Verfahren zum Betriebe von Kaelteverdichtern
US3105633A (en) * 1961-09-20 1963-10-01 Gen Electric Rotary compressor injection cooling arrangement
US3210958A (en) * 1964-09-10 1965-10-12 Gen Electric Heat pump comprising rotary compressor including injection cooling arrangement
FR2075310A5 (de) * 1970-01-19 1971-10-08 Thomas Sabroe Et Co As
US3945220A (en) * 1975-04-07 1976-03-23 Fedders Corporation Injection cooling arrangement for rotary compressor
US4049410A (en) * 1974-07-29 1977-09-20 Allan Sinclair Miller Gas compressors
USRE30499E (en) * 1974-11-19 1981-02-03 Dunham-Bush, Inc. Injection cooling of screw compressors

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE645746C (de) * 1936-06-17 1937-06-03 Georges Loeffler Verfahren zum Betriebe von Kaelteverdichtern
US3105633A (en) * 1961-09-20 1963-10-01 Gen Electric Rotary compressor injection cooling arrangement
US3210958A (en) * 1964-09-10 1965-10-12 Gen Electric Heat pump comprising rotary compressor including injection cooling arrangement
FR2075310A5 (de) * 1970-01-19 1971-10-08 Thomas Sabroe Et Co As
US4049410A (en) * 1974-07-29 1977-09-20 Allan Sinclair Miller Gas compressors
USRE30499E (en) * 1974-11-19 1981-02-03 Dunham-Bush, Inc. Injection cooling of screw compressors
US3945220A (en) * 1975-04-07 1976-03-23 Fedders Corporation Injection cooling arrangement for rotary compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0423976A1 (de) * 1989-10-17 1991-04-24 Copeland Corporation Kompressorkälteanlage mit Bedarfskühlung
EP3280892A4 (de) * 2015-04-07 2018-03-21 Conoco Phillips Company System zum abschrecken eines kältekreislaufs einer erdgasverflüssigungsanlage mit und verfahren zum abschrecken

Similar Documents

Publication Publication Date Title
US4896515A (en) Heat pump, energy recovery method and method of curtailing power for driving compressor in the heat pump
CN108005743B (zh) 一种带压缩制冷增效的无泵有机朗肯循环发电系统
CN109737639A (zh) 太阳能辅助的喷射-蒸气压缩混合制冷系统及其工作过程
CN108106048A (zh) 一种喷射器膨胀自复叠制冷循环系统及工作过程
CN105241115B (zh) 蒸汽压缩‑喷射耦合制冷循环装置及方法
CN101939599A (zh) 制冷装置
CN105509359B (zh) 一种相变波转子自复叠制冷系统及其工作方法
CN103206802B (zh) 一种脉管膨胀机
JP2011503507A (ja) 蒸気圧縮および膨張空調装置
US5216899A (en) Rotating single cycle two-phase thermally activated heat pump
CN208653032U (zh) 一种节能型制冷设备
CN104501449B (zh) 一种液体中间增压的蒸汽压缩-喷射耦合制冷系统
EP0329199A1 (de) Verfahren zur Beschränkung der Antriebskraft für einen Verdichter einer Wärmepumpe und nach diesem Verfahren arbeitender Verdichter
CN102600704B (zh) 一种机械蒸汽再压缩低温空气干燥装置及方法
CN112041542B (zh) 一种工质循环做功的新型蒸汽机
CN1419089A (zh) 二氧化碳跨临界制冷循环转子式膨胀节能器
CN1175663A (zh) 利用低温工质制冷发电的方法及制冷发电站
CN106969537A (zh) 环境能动力汽车
CN111219310B (zh) 膨胀压缩机
CN207963226U (zh) 一种喷射器膨胀自复叠制冷循环系统
CN113007915A (zh) 一种利用蒸汽压改变状态的热力学方法和装置
CN1138952C (zh) 一种超临界回热加热热力驱动热泵装置
CN200982768Y (zh) 循环射流膨胀蒸汽喷射式制冷装置
JPH0379970A (ja) ランキンサイクルエンジン駆動圧縮冷凍機
CN116222009A (zh) 一种太阳能辅助的两相喷射器膨胀补气增焓热泵系统及控制方法

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

AC Divisional application: reference to earlier application

Ref document number: 239680

Country of ref document: EP

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19900226