EP2035758B1 - Mécanisme de réfrigération - Google Patents

Mécanisme de réfrigération Download PDF

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Publication number
EP2035758B1
EP2035758B1 EP07786886A EP07786886A EP2035758B1 EP 2035758 B1 EP2035758 B1 EP 2035758B1 EP 07786886 A EP07786886 A EP 07786886A EP 07786886 A EP07786886 A EP 07786886A EP 2035758 B1 EP2035758 B1 EP 2035758B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
compressor
turbine
pump
cooling device
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.)
Not-in-force
Application number
EP07786886A
Other languages
German (de)
English (en)
Other versions
EP2035758A1 (fr
Inventor
Husnu Kerpicci
Tolga Kurtulus
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.)
Arcelik AS
Original Assignee
Arcelik AS
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Filing date
Publication date
Application filed by Arcelik AS filed Critical Arcelik AS
Publication of EP2035758A1 publication Critical patent/EP2035758A1/fr
Application granted granted Critical
Publication of EP2035758B1 publication Critical patent/EP2035758B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers
    • 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
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression

Definitions

  • the present invention relates to a cooling device wherein a high performance is provided by increasing the compressor inlet pressure of the refrigerant fluid.
  • the compression activity is achieved by a piston that moves to and fro by means of a crank mechanism in the cylinder, the refrigerant fluid aspirated into the cylinder is compressed by the piston and discharged out of the cylinder as the exhaust valve is opened.
  • the refrigerant having a certain pressure sucked into the compressor is pumped to be compressed to a greater pressure; the sucked and pumped gas pressure determines the compression rate.
  • the power consumed at the compressor is proportional to the compression rate.
  • the refrigerant fluid returning from the refrigerant cycle reaches the compressor with a reduced pressure and the suction of the low pressure refrigerant results in the increase of the power consumed for compression and decrease in the performance of the compressor.
  • the temperature of the refrigerant fluid must be kept as low as possible as the pressure thereof is increased while being sucked into the compressor casing. Failing that, the density of the refrigerant fluid is decreased thus adversely affecting the thermodynamic efficiency.
  • auxiliary charging units called turbo chargers or supercharging devices driven by the compressor motor are utilized in order to draw in more refrigerant fluid into the compressor from the refrigerant cycle. These units increase the inlet gas pressure, however driving of these units situated in the compressor casing directly by the compressor motor reduces the efficiency of the compressor and also the temperature of the refrigerant fluid at inlet of the compressor cannot be reduced.
  • a "supercharging device” in a hermetic compressor a "supercharging device" is utilized that provides to deliver a greater amount of the refrigerant fluid to the cylinder.
  • the movement of a driving pulley disposed on a lower end of a crankshaft is transmitted to another pulley in the suction chamber and to a fan connected to this pulley by means of transmitting means such as the belt or gears.
  • the refrigerant is delivered to the suction chamber wherein the fan operates by means of a suction pipe, one end of which is connected to the evaporator and thus the amount of the refrigerant drawn into the cylinder head is increased by the fan and from thereon is delivered to the refrigerant cycle.
  • Another type of supercharged cooling device is shown in document US-A-3 367 125 which is considered to represent the closest prior art.
  • the aim of the present invention according to claim 1, is the realization of a cooling device wherein a greater cooling performance is provided by increasing the inlet pressure of the refrigerant fluid into the compressor without increasing the temperature.
  • a supercharging device is utilized which is connected to the refrigerant line that connects the elements of the refrigerant cycle such as the evaporator, the condenser and the capillary tube wherein the refrigerant circulates, providing to increase the pressure of the refrigerant at the inlet of the compressor by transmitting the movement energy received from the pressurized refrigerant at the outlet of the compressor to the refrigerant at the inlet of the compressor.
  • the supercharging device comprises a turbine that moves by the effect of the high pressure refrigerant at the compressor outlet and a pump that is actuated by the drive of the turbine that provides to deliver the low pressure refrigerant received from the refrigerant line to the compressor after increasing the pressure thereof.
  • the supercharging device is disposed outside of the compressor casing and thus provides the refrigerant conveyed to the suction side of the compressor from the refrigerant line, to be delivered into the compressor casing without raising the temperature thereof and thus preventing expansion.
  • the power required to compress the refrigerant and the piston leaks that occur during compression are decreased by increasing the pressure of the refrigerant at the compressor inlet by means of the supercharging device, providing to increase the amount of the refrigerant pumped at the same stroke volume by the cylinder thus increasing capacity.
  • the supercharging device is preferably connected in between the compressor outlet pipe disposed at the outlet of the compressor and the compressor return pipe disposed at the side wherein the refrigerant enters the compressor.
  • the refrigerant in the compressor outlet pipe is delivered to the turbine via a turbine inlet pipe, and the refrigerant after activating the turbine is delivered to the refrigerant line by the turbine outlet pipe after leaving the turbine.
  • the low pressure refrigerant received from the evaporator is delivered to the pump via a pump inlet pipe and the refrigerant activated by the pump to increase the pressure is then delivered to the compressor return pipe by the pump outlet pipe.
  • the entry and exit of the refrigerant in the inlet and return pipes of the compressor into the supercharging device is controlled by automatic multi-way valves and one-way valves.
  • the turbine part of the supercharging device is connected between the condenser outlet and the evaporator inlet providing to expand the refrigerant to be delivered to the evaporator, thus the use of an additional expansion element for example the capillary tube is deemed unnecessary.
  • Figure 1 - is the schematic view of a cooling device wherein a supercharging device is used in the refrigerant cycle.
  • Figure 2 - is the schematic view of a cooling device wherein a supercharging device connected between the compressor inlet and return pipes is used.
  • Figure 3 - is the schematic view of a cooling device wherein a supercharging device connected between the condenser outlet and the evaporator inlet is used.
  • the cooling device (1) comprises a compressor (2) for activating the refrigerant, a condenser (3) that condenses the refrigerant and delivers to the outside surroundings, an evaporator (4) providing to cool the ambient environment by the circulating refrigerant within absorbing the heat, a refrigerant line (5) wherein the refrigerant circulates and that connects together the refrigerant cycle elements such as the compressor (2), condenser (3) and evaporator (4).
  • the cooling device (1) of the present invention comprises a supercharging device (6) connected to the refrigerant line (5) that provides to increase the pressure of the refrigerant entering the compressor (2), having a turbine (7) that moves by the effect of the refrigerant at the pump-out side of the compressor (2) and a pump (8) that is activated by the drive of the turbine (7) that provides the refrigerant delivered from the refrigerant line (5) to the suction side of the compressor (2) to be increased in pressure and sent to the compressor (2).
  • the supercharging device (6) transfers the movement energy received from the pressurized refrigerant on the pump-out side of the compressor (2) to the refrigerant on the suction side of the compressor (2) thus power from a separate motor or from the compressor (2) motor is not required to operate the supercharging device (6).
  • the supercharging device (6) is situated outside of the compressor (2) casing and thus provides the refrigerant delivered to the suction side of the compressor (2) from the refrigerant line (5) to be sent into the compressor (2) casing without increasing the temperature thereof hence preventing expansion.
  • the refrigerant pumped by the compressor (2) is directed towards the turbine (7) providing the turbine (7) to rotate.
  • the refrigerant upon leaving the turbine (7) reaches the condenser (3).
  • the turbine (7) transfers the movement to the pump (8) and the pressure of the refrigerant coming from the evaporator (4) outlet to the suction side of the compressor (2) is increased by the pump (8) ( Figures 1 , 2 ).
  • the cooling device (1) comprises a compressor outlet pipe (9) disposed on the pump-out side of the compressor (2), a compressor return pipe (10) disposed on the suction side of the compressor (2) and the supercharging device (6) is connected in between the compressor outlet pipe (9) and the compressor return pipe (10).
  • the refrigerant is directed from the compressor outlet pipe (9) to the turbine (7) part of the supercharging device (6), and the refrigerant activated by the pump (8) driven by the turbine (7) is directed to the compressor return pipe (10) ( Figure 2 ).
  • the cooling device (1) furthermore comprises a turbine inlet pipe (11) that delivers the refrigerant in the compressor outlet pipe (9) to the turbine (7), a turbine outlet pipe (12) that delivers the refrigerant activating the turbine (7) once again to the refrigerant line (5) after it leaves the turbine (7), a multi-way valve (13) having one inlet and two outlets, that provides the refrigerant in the compressor outlet pipe (9) to be directed partially or entirely to the turbine inlet pipe (11), a one-way valve (check valve) (14) that provides to direct the refrigerant that activates the turbine (7) to the condenser (3) after leaving the turbine (7), a pump inlet pipe (15) that delivers the refrigerant received from the evaporator (4) to the pump (8), a pump outlet pipe (16) for delivering the refrigerant activated by the pump (8) to the compressor return pipe (10), a multi-way valve (113) for directing the refrigerant received from the evaporator (4) outlet partially or entirely to
  • the refrigerant pumped out by the compressor (2) reaches the multi-way valve (13) passing through the compressor outlet pipe (9).
  • the multi-way valve (13) directs the refrigerant partially or entirely to the turbine (7) by means of the turbine inlet pipe (11) depending on the data received, providing to rotate the turbine (7).
  • the refrigerant upon leaving the turbine (7) reaches the one-way valve (14) through the turbine outlet pipe (12) and from there to the condenser (3).
  • the turbine (7) transfers the motion to the pump (8) and the pressure of the refrigerant at the outlet of the evaporator (4) that is directed to the pump (8) via the multi-way valve (113) is increased by means of the pump (8).
  • the refrigerant is then sent to the one-way valve (114) by means of the pump outlet pipe (16) and from there to the compressor return pipe (10).
  • the multi-way valve (13) at the compressor outlet pipe (9) and the multi-way valve (113) at the compressor return pipe (10) are controlled automatically, providing the supercharging device (6), when necessary, to be de-energized or the refrigerant to be sent partially to the supercharging device (6) depending on the data received from the pressure and temperature sensors disposed in the refrigerant line (5).
  • the turbine (7) part of the supercharging device (6) is connected between the condenser (3) outlet and the evaporator (4) inlet, since the required refrigerant expansion for inlet to the evaporator (4) is provided in the turbine (7), the necessity for an additional expansion element, for example the use of a capillary tube is no longer needed ( Figure 3 ).
  • the turbine inlet pipe (11) is connected to the condenser (3) outlet and the turbine outlet pipe (12) is connected to the evaporator (4) inlet.
  • the high pressure refrigerant leaving the condenser (3) is delivered to the turbine (7) via the turbine inlet pipe (11), and since the refrigerant now expanded and depressurized while activating the turbine (7) has attained the condition for entering the evaporator (4) and the expanded refrigerant is sent directly to the evaporator (4) inlet after leaving the turbine (7).
  • the pump (8) driven by the turbine (7) provides to increase the pressure of the refrigerant at the inlet of the compressor (2) as in the previous embodiment ( Figure 3 ).
  • the refrigerant that is pumped out by the compressor (2) is sent directly to the condenser (3) after leaving the compressor (2).
  • the refrigerant, after leaving the condenser (3) is delivered to the turbine via the turbine inlet pipe (11).
  • the refrigerant activating the turbine (7) leaves the turbine (7) with a lower pressure and is delivered to the evaporator (4) inlet via the turbine outlet pipe (12).
  • the cooling device (1) of the present invention by means of the supercharging device (6) disposed between the pump-out side of the compressor (2) and suction side of the compressor (2), the pressure of the refrigerant at the compressor (2) inlet is increased and the power required to be consumed for compression in the compressor (2) and the piston leaks during the compression are decreased. Capacity increase is provided by means of increasing the amount of refrigerant pumped in the same stroke volume in the cylinder.
  • the load of the condenser (3) is decreased by means of the refrigerant rotating the turbine (7) expanding by some amount at the outlet of the compressor (2) and thus a smaller size condenser (3) can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Separation Using Semi-Permeable Membranes (AREA)

Claims (8)

  1. Un dispositif de refroidissement (1) comprenant un compresseur (2), un condenseur (3), un évaporateur (4), tous étant reliés entre eux par une ligne de réfrigérant (5) dans lequel le réfrigérant circule et un dispositif de suralimentation (6) relié à la ligne de refrigérant (5), et caractérisée par le dispositif de suralimentation (6) assurant l'augmentation de la pression du réfrigérant dans le compresseur (2), comprenant
    - une turbine (7) qui se déplace par l'effet du réfrigérant sur le côté de vidange du compresseur (2) et
    - une pompe (8), qui est activée par le lecteur de la turbine (7) et qui fournit le refrigérant provenant de la ligne de réfrigérant (5) vers le côté d'aspiration du compresseur (2) en augmentant la pression du réfrigérant, et qui envoie le réfrigérant dans le compresseur (2).
  2. Un dispositif de refroidissement (1) selon la Revendication 1, caractérisé par le dispositif de suralimentation (6) disposé à l'extérieur du boîtier du compresseur (2).
  3. Un dispositif de refroidissement (1) selon la revendication 1 ou 2, caractérisé par un tuyau de sortie de compresseur (9) situé sur le côté de vidange du compresseur (2), un tuyau de retour de compresseur (10) situé sur le côté d'aspiration du compresseur (2) et le dispositif de suralimentation (6) relié entre le tuyau de sortie de compresseur (9) et le tuyau de retour de compresseur (10).
  4. Un dispositif de refroidissement (1) selon la revendication 3, caractérisé par un tuyau d'entrée de turbine (11) qui transmet le réfrigérant venant du tuyau de sortie de compresseur (9) à la turbine (7), un tuyau de sortie de turbine (12) qui transmet le réfrigérant activant la turbine (7) de nouveau à la ligne de réfrigérant (5) après qu'il sort de la turbine (7), un tuyau d'entrée de pompe (15) transmettant le réfrigérant reçu de l'évaporateur (4) à la pompe (8), et tuyau de sortie de pompe (16) pour transmettre le réfrigérant activé par la pompe (8) au tuyau de retour de compresseur (10).
  5. Un dispositif de refroidissement (1) selon la revendication 3 ou 4, caractérisé par une vanne multi-voies (13) comprenant une entrée et deux sorties, qui fournit le réfrigérant dans le tuyau de sortie de compresseur (9) à être dirigée en partie ou entièrement vers le tuyau d'entrée de turbine (11), un clapet anti-retour (clapet) (14) qui sert à diriger le réfrigérant activant la turbine (7) vers le condenseur (3) après qu'il sort de la turbine (7), une autre vanne multi-voies (113) pour diriger le réfrigérant reçu de la sortie de l'évaporateur (4) partiellement ou entièrement vers la pompe (8), et un clapet anti-retour (clapet) (114) qui dirige le réfrigérant provenant du tuyau de sortie de pompe (16) au tuyau de retour de compresseur (10).
  6. Un dispositif de refroidissement (1) selon la revendication 5, caractérisé par des capteurs de pression et de température disposés dans la ligne de réfrigérant (5) et des vannes multi-voies (13, 113) qui permettent au dispositif de suralimentation (6), le cas échéant, de se mettre en hors tension ou au réfrigérant d'être envoyé en partie au dispositif de suralimentation (6) en fonction des données reçues des capteurs de pression et de température.
  7. Un dispositif de refroidissement (1) selon la revendication 1 ou 2, caractérisé par le dispositif de suralimentation (6) comprenant la turbine (7) qui est connectée entre la sortie du condenseur (3) et l'entrée de l'évaporateur (4).
  8. Un dispositif de refroidissement (1) selon la revendication 7, caractérisé par le tuyau d'entrée de turbine (11) connecté à la sortie du condenseur (3), et un tuyau de sortie la turbine (12) connecté à l'entrée de l'évaporateur (4).
EP07786886A 2006-06-30 2007-06-28 Mécanisme de réfrigération Not-in-force EP2035758B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TR200603359 2006-06-30
PCT/EP2007/056487 WO2008000793A1 (fr) 2006-06-30 2007-06-28 Mécanisme de réfrigération

Publications (2)

Publication Number Publication Date
EP2035758A1 EP2035758A1 (fr) 2009-03-18
EP2035758B1 true EP2035758B1 (fr) 2010-07-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07786886A Not-in-force EP2035758B1 (fr) 2006-06-30 2007-06-28 Mécanisme de réfrigération

Country Status (4)

Country Link
EP (1) EP2035758B1 (fr)
AT (1) ATE475849T1 (fr)
DE (1) DE602007008099D1 (fr)
WO (1) WO2008000793A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220381496A1 (en) * 2020-07-10 2022-12-01 Energy Recovery, Inc. Refrigeration system with high speed rotary pressure exchanger
US12085324B2 (en) 2021-06-09 2024-09-10 Energy Recovery, Inc. Refrigeration and heat pump systems with pressure exchangers

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11397030B2 (en) * 2020-07-10 2022-07-26 Energy Recovery, Inc. Low energy consumption refrigeration system with a rotary pressure exchanger replacing the bulk flow compressor and the high pressure expansion valve
EP4441442A1 (fr) * 2021-12-03 2024-10-09 Energy Recovery, Inc. Systèmes de manipulation de fluide comprenant un compresseur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3371706A (en) * 1964-06-23 1968-03-05 Carrier Corp Heating and cooling system
US3367125A (en) * 1966-09-02 1968-02-06 Carrier Corp Refrigeration system
US4209992A (en) * 1977-11-04 1980-07-01 Chih Kang Shao Power generating method and apparatus
US4683725A (en) * 1984-07-31 1987-08-04 Diesel Kiki Co., Ltd. Air conditioner for automotive vehicles capable of cooling intake air supplied to an internal combustion engine
CN1161543C (zh) * 2000-11-10 2004-08-11 三星光州电子株式会社 封闭式压缩机的增压装置
KR100658420B1 (ko) * 2004-12-22 2006-12-19 삼성광주전자 주식회사 냉동사이클 및 이를 갖춘 냉온수기

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220381496A1 (en) * 2020-07-10 2022-12-01 Energy Recovery, Inc. Refrigeration system with high speed rotary pressure exchanger
US11982481B2 (en) * 2020-07-10 2024-05-14 Energy Recovery, Inc. Refrigeration system with high speed rotary pressure exchanger
US12085324B2 (en) 2021-06-09 2024-09-10 Energy Recovery, Inc. Refrigeration and heat pump systems with pressure exchangers

Also Published As

Publication number Publication date
WO2008000793A1 (fr) 2008-01-03
ATE475849T1 (de) 2010-08-15
EP2035758A1 (fr) 2009-03-18
DE602007008099D1 (de) 2010-09-09

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