EP2048457B1 - Kühlvorrichtung - Google Patents

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Publication number
EP2048457B1
EP2048457B1 EP07791431.5A EP07791431A EP2048457B1 EP 2048457 B1 EP2048457 B1 EP 2048457B1 EP 07791431 A EP07791431 A EP 07791431A EP 2048457 B1 EP2048457 B1 EP 2048457B1
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EP
European Patent Office
Prior art keywords
refrigerant
expander
muffler
expansion
pressure
Prior art date
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Active
Application number
EP07791431.5A
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English (en)
French (fr)
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EP2048457A1 (de
EP2048457A4 (de
Inventor
Satoshi Ishikawa
Kazutaka Hori
Eiji Kumakura
Katsumi Sakitani
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Publication of EP2048457A1 publication Critical patent/EP2048457A1/de
Publication of EP2048457A4 publication Critical patent/EP2048457A4/de
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Publication of EP2048457B1 publication Critical patent/EP2048457B1/de
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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound

Definitions

  • the present invention relates to a refrigerating apparatus performing a vapor compression refrigeration cycle by circulating carbon dioxide and particularly relates to a measure to reduce pressure pulsation of the refrigerant flowing in a refrigerant circuit and being compressed to over its critical pressure.
  • Patent Document 1 discloses a refrigerating apparatus using carbon dioxide as the refrigerant.
  • a compressor, a radiator, a positive displacement type expander, and an evaporator are connected to the refrigerant circuit of this refrigerating apparatus.
  • the compressor the refrigerant is compressed to over its critical pressure.
  • the refrigerant discharged from the compressor radiates heat in the radiator, and is expanded in the expander. Thereafter, the refrigerant is evaporated in the evaporator, and is then sucked into the compressor to be compressed again. For example, in a heating operation of this refrigerating apparatus, heat released from the radiator heats an indoor room.
  • a refrigerant expansion operation is performed in such a manner that the piston revolves to increase the volume of the expansion chamber.
  • the refrigerant on the inflow side and outflow side of the expander becomes comparatively high in density. Therefore, the expansion operation by the expander accompanies variation in pressure of the refrigerant on the inflow side and outflow side of the expander to cause large pressure pulsation of the refrigerant.
  • the pressure pulsation of the refrigerant may cause noise generation or malfunction of instruments connected to the refrigerant pipes.
  • Patent Document 2 proposes a refrigerating apparatus in which a pulsation absorbing accumulator is provided on the inflow side of the expander for reducing the pressure pulsation of the refrigerant.
  • This accumulator includes a sealed container housing a bag-shaped membrane. Inside the membrane, a high-pressure nitrogen gas is encapsulated. When the pressure of the refrigerant flowing, for example, on the inflow side of the expander is increased, the membrane contracts to increase the effective volume of the sealed container. As a result, the pressure of the refrigerant lowers to mitigate and absorb the pressure pulsation of the refrigerant.
  • Patent Document 2 necessitates the membrane to make the device configuration comparatively complicated, thereby shortening its lifetime and increasing its cost.
  • the present invention has been made in view of the foregoing, and its objective is to reduce, in a refrigerating apparatus performing a vapor compression refrigeration cycle, the pressure pulsation of refrigerant on the inflow side or outflow side of an expander by a comparatively simple device configuration.
  • a first aspect of the present invention is directed to a refrigerating apparatus according to claim 1.
  • a compressor (20) and a positive displacement type expander (22) are provided in a refrigerant circuit (10).
  • the refrigerant is compressed in the compressor (20), while being expanded in the expander (22), thereby performing the vapor compression refrigeration cycle.
  • the muffler (30, 40, 50) is provided on the inflow side of the expander (22). This muffler is of any one of expansion type, branch pipe type, and interference type. When the refrigerant flows in the muffler (30, 40, 50), the pressure variation of the refrigerant is suppressed to reduce the pressure pulsation of the refrigerant.
  • the refrigerant circuit (10) uses carbon dioxide as the refrigerant for performing the refrigeration cycle, in which the compressor (20) compresses the refrigerant to over its critical pressure.
  • the refrigerant flowing on the inflow side and outflow side of the expander (22) becomes comparatively low in sonic speed.
  • the refrigerant circuit (10) includes pressure reducing means (24) for allowing high-pressure refrigerant to be in a gas-liquid two-phase state by reducing its pressure, and the muffler (30, 40, 50) is provided between the outflow side of the pressure reducing means (24) and the inflow side of the expander (22).
  • the high-pressure refrigerant having been compressed in the compressor (20) is reduced in pressure to be in a gas-liquid two-phase state.
  • This refrigerant in the gas-liquid two-phase state flows into the muffler (30, 40, 50).
  • the refrigerant in the gas-liquid two-phase state flowing in the muffler (30, 40, 50) is further lower in sonic speed than, for example, refrigerant in a gas state.
  • the pressure pulsation of the refrigerant can be reduced further effectively, while size reduction of the muffler (30, 40, 50) can be contemplated.
  • the expander (22) alternatively allows high-pressure refrigerant to be in a gas-liquid two-phase state by reducing its pressure, and the muffler (30, 40, 50) is provided on the outflow side of the expander (22).
  • the refrigerant having been reduced in pressure in the expander (22) to be in the gas-liquid two-phase state flows into the muffler (30, 40, 50). Accordingly, in the present aspect, similarly to the case in the third aspect, the sonic speed of the refrigerant flowing in the muffler (30, 40, 50) becomes low to lead to size reduction of the muffler (30, 40, 50).
  • the refrigerating apparatus may further include: an expansion type muffler (30) including an expansion passage (32) including at the respective ends thereof opening parts to which refrigerant pipes are connected, the expansion passage (32) having a diameter larger than each of the refrigerant pipes, and a partition plate (60) including an opening (61) having a diameter smaller than an inner diameter of a refrigerant pipe at an opening part of the expansion passage (32) on the side of the expander (22).
  • the use of the expansion type muffler (30) may cause resonance of a pressure wave generated in the expander (22) to invite noise generation in a refrigerant pipe connecting the expander (22) and the muffler (30).
  • the refrigerant expansion operation by the expander (22) allows a traveling wave of sound to progress from the expander (22) toward the muffler (30), so that this pressure wave enters the expansion passage (32).
  • the traveling wave of the sound is readily reflected, which means that the reflected wave is liable to progress from the muffler (30) toward the expander (22).
  • the partition plate (60) is provided at the opening part of the expansion passage (32) on the side of the expander (22).
  • the partition plate (60) has the opening smaller in diameter than the refrigerant pipe to function as a generally-called orifice at the opening part of the expansion passage (32).
  • the partition plate (60) can prevent generation of the reflected wave from the expansion passage (32) toward the expander (22) to prevent resonance in the refrigerant pipe between the expander (22) and the muffler (30).
  • the refrigerating apparatus may further include: an expansion type muffler (30) including an expansion passage (32) including at the respective ends thereof opening parts to which refrigerant pipes are connected, the expansion passage (32) having a diameter larger than each of the refrigerant pipes, wherein the expansion passage (32) is formed in a spiral shape.
  • the muffler (30) can be reduced in size with the length of the expansion passage (32) sufficiently secured.
  • the muffler (30, 40, 50) of expansion type, branch pipe type, or interference type is provided on the inflow side of the expander (22) to reduce the pressure pulsation of the refrigerant.
  • the mufflers (30, 40, 50) of these types have a device configuration simpler than, for example, the accumulate in Patent Document 2, thereby enabling contemplation of a low cost muffler. Such the simple device configuration facilitates the maintenance of the muffler (30, 40, 50).
  • the muffler (30, 40, 50) is applied to a refrigerant circuit (10) in which carbon dioxide is compressed to over its critical pressure.
  • the refrigeration cycle in which the refrigerant is compressed to over its critical pressure lowers comparatively the sonic speed of the refrigerant flowing in the muffler (30, 40, 50), thereby leading to a compact design of the muffler (30, 40, 50).
  • the refrigerant in the gas-liquid two-phase state is allowed to flow into the muffler (30, 40, 50).
  • the flow rate of the refrigerant in the gas-liquid two-phase state flowing in the muffler (30, 40, 50) lowers further to lead to a further compact design of the muffler (30, 40, 50).
  • the partition plate (60) serving as an orifice may be provided at the opening part of the expansion passage (32) on the side of the expander (22) in the expansion type muffler (30). This prevents resonance from causing in the refrigerant pipe between the muffler (30) and the expander (22). As a result, noise generation caused due to the resonance can be suppressed.
  • expansion passage (32) may be formed in a spiral shape. This can lead to a further compact design of the muffler (30) with the channel length of the expansion passage (32) sufficiently secured.
  • Configuration 1 illustrates the basic configuration of a refrigerating apparatus which is not part of the the claimed invention.
  • a refrigerating apparatus in accordance with configuration 1 composes an air conditioner (1) for indoor air conditioning.
  • the refrigerating apparatus (1) includes a refrigerant circuit (10) performing a vapor compression refrigeration cycle by circulating refrigerant.
  • the refrigerant circuit (10) is filled with carbon dioxide as the refrigerant.
  • the refrigeration cycle in which the refrigerant is compressed to over its critical pressure is performed in the refrigerant circuit (10).
  • a compressor (20), a radiator (21), an expander (22), and an evaporator (23) are connected to one another by means of refrigerant pipes (11, 12, 10 13, 14).
  • a discharge pipe (11) is connected to the discharge side of the compressor (20.
  • the other end of the discharge pipe (11) is connected to one end of the radiator (21).
  • the other end of the radiator (21) is connected to one end of an inflow pipe (12).
  • the other end of the inflow pipe (12) is connected to the inflow side of the expander (22).
  • the outflow side of the expander (22) is connected to one end of an 15 outflow pipe (13).
  • the other end of the outflow pipe (13) is connected to one end of the evaporator (23).
  • the other end of the evaporator (23) is connected to one end of a suction pipe (14).
  • the other end of the suction pipe (14) is connected to the suction side of the compressor (20).
  • the compressor (20) is of positive displacement type.
  • the compressor (20) 20 accommodates in its casing a rotary compression mechanism.
  • the compression mechanism of the compressor (20) compresses gas refrigerant up to a pressure over its critical pressure.
  • the radiator (21) is disposed in an indoor space, for example, and is composed of a fin-and-tube type heat exchanger. In the radiator (21), heat is radiated from the high-temperature high-pressure refrigerant indoors.
  • the expander (22) is of 25 positive displacement type.
  • the expander (22) accommodates in its casing a rotary expansion mechanism.
  • the expansion mechanism of the expander (22) reduces the pressure of the high-pressure refrigerant to allow it to be in a gas-liquid two-phase state.
  • the evaporator (23) is disposed in an outdoor space, for example, and is composed of a fin-and-tube heat exchanger.
  • the low-pressure liquid refrigerant absorbs heat from the outdoor air to be evaporated.
  • An expansion type muffler (30) is provided in the refrigerant circuit (10).
  • the expansion type muffler (30) is mounted to the inflow pipe (12) on the inflow side of the expander (22).
  • the expansion type muffler (30) includes a hollow cylindrical casing (31), in which a cylindrical expansion passage (32) is formed.
  • the expansion passage (32) includes an opening part at one end thereof to which a refrigerant inflow pipe (12a) is connected, and an opening part at the other end thereof to which a refrigerant outflow pipe (12b) is connected.
  • Each inner diameter of the refrigerant inflow pipe (12a) and the refrigerant outflow pipe (12b) is set at approximately 10 mm, and the inner diameter of the casing (31) is set at approximately 30 mm. Namely, the inner diameter of the casing (31) is approximately three times as large as each inner diameter of the refrigerant pipes (12a, 12b) connected to the respective ends of the casing (31).
  • the channel length 1 of the expansion passage (32) is set at approximately 70 cm.
  • the channel length 1 of the expansion passage (32) may be designed according to the sonic speed of the refrigerant which can be obtained from the property and driving condition of the refrigerant flowing in the expansion passage (32) and the frequency of the pressure pulsation which can be obtained from the rotating speed of the expansion mechanism of the expander (22).
  • the expansion type muffler (30) includes a partition plate (60) at the opening part of the expansion passage (32) on the side of the expander (22).
  • the partition plate (60) has a circular opening (61) having a diameter smaller than the inner diameter of the refrigerant outflow pipe (12b), and is fitted in the refrigerant outflow pipe (12b).
  • the partition plate (60) functions as an orifice for preventing resonance of the pressure wave from the expander (22) accompanied by the operation of the expander (22).
  • the high-pressure refrigerant is reduced in pressure to be low-pressure refrigerant in a gas-liquid two-phase state.
  • the refrigerant having been reduced in pressure in the expander (22) flows out into the outflow pipe (13).
  • the refrigerant flowing in the outflow pipe (13) flows into the evaporator (23).
  • the refrigerant absorbs heat from the outdoor air to be evaporated.
  • the gas refrigerant having been evaporated in the evaporator (23) flows into the suction pipe (14), and is then sucked into the compressor (20).
  • the compression mechanism of the compressor (20) the refrigerant is compressed again to over its critical pressure.
  • refrigerant compression by the compressor (20) may accompany variation in pressure of the refrigerant flowing in the refrigerant circuit (10), which can cause pressure pulsation of the refrigerant in any of the refrigerant pipes (11, 12, 13, 14).
  • the expansion type muffler (30) is provided to minimize the pressure pulsation of the refrigerant on the inflow side of the expander (22).
  • the high-pressure refrigerant having radiated heat in the radiator (21) flows into the expansion type muffler (30).
  • the expansion passage (32) a wave by the pressure variation of the refrigerant receives interference to mitigate the pressure variation of the refrigerant.
  • the pressure pulsation of the refrigerant on the inflow side of the expander (22) is reduced.
  • a traveling wave of sound progresses from the inflow side of the expander (22) toward the expansion type muffler (30).
  • this traveling wave is reflected by the opening part of the expansion passage (32), and accordingly, the reflected wave from the expansion passage (32) toward the expander (22) is readily produced. Resonance of the traveling wave and the reflected wave may generate noise in the refrigerant outflow pipe (12b).
  • the partition plate (60) is provided at the opening part of the expansion passage (32) on the side of the expander (22) in the present embodiment. With the partition plate (60) provided, the reflected wave from the expansion type muffler (30) toward the expander (22) is not produced to suppress resonance in the refrigerant outflow pipe (12b).
  • the expansion type muffler (30) is provided on the inflow side of the expander (22). This can reduce the pressure pulsation of the refrigerant on the inflow side of the expander (22) effectively, while the muffler is simplified. In consequence, in the present invention, cost reduction of the muffler can be contemplated when compared with the conventional accumulator. Such the simplified configuration of the muffler can facilitate the maintenance of the muffler (30).
  • the carbon dioxide is compressed to over its critical pressure in the refrigerant circuit (10). This lowers the flow rate of the refrigerant flowing in the expansion type muffler (30). By this lowering, the channel length 1 of the expansion passage (32) can be shortened. Thus, the expansion type muffler (30) can be reduced in size.
  • the partition plate (60) serving as an orifice is provided at the opening part of the expansion passage (32) on the side of the expander (22). This can prevent resonance from causing in the refrigerant pipe between the expansion type muffler (30) and the expander (22) (refrigerant outflow pipe (12b)). Hence, noise generated due to the resonance can be avoided.
  • an air conditioner (1) in accordance with configuration 2 which is not part of the claimed invention, 10 as shown in FIG. 3 and FIG. 4 the same expansion type muffler (30) as that in configuration 1 provided to the outflow pipe (13) on the outflow side of the expander (22) (between a refrigerant inflow pipe (13a) and a refrigerant outflow pipe (13b)).
  • this refrigerant circuit (10) the high-pressure refrigerant at a pressure over its critical pressure is reduced in pressure in the expander (22) to be in a gas-liquid two-phase state. 15 Thereafter, the refrigerant in the gas-liquid two-phase state flows into the expansion type muffler (30). As a result, the pressure pulsation of the refrigerant on the outflow side of the expander (22) can be reduced.
  • the sonic speed of the refrigerant flowing in the expansion passage (32) can be reduced further when compared with, for example, that of gas refrigerant. Accordingly, the channel length 1 of the expansion passage (32) can be further shortened, thereby enabling contemplation of reduction in size of the expansion type muffler (30).
  • the partition plate (60) is provided at the opening part of the 25 expansion passage (32) on the side of the expander (22) (the refrigerant inflow pipe (13a)). This can prevent the aforementioned resonance from being caused in the refrigerant inflow pipe (13a).
  • an expansion valve (24) is provided between the radiator (21) and the expander (22).
  • the expansion valve (24) serves as pressure reducing means for allowing the high-pressure refrigerant having radiated heat in the radiator (21) to be in a gas-liquid two-phase state by reducing its pressure.
  • the same expansion type muffler (30) as that in above unclaimed configurations is provided between the outflow side of the pressure reducing valve (24) and the inflow side of the expander (22).
  • the refrigerant in the gas-liquid two-phase state is allowed to flow into the expansion type muffler (30). This lowers the flow rate of the refrigerant flowing in the expansion passage (32) to lead to shortening of the length of the expansion passage (32).
  • the expansion type muffler (30) is provided on the inflow side of the expander (22).
  • a branch pipe type muffler (40) shown in FIG. 6 or an interference type muffler (50) shown in FIG. 7 may be employed.
  • the branch type muffler (40) shown in FIG. 6 includes a branch pipe (41) branching from a refrigerant pipe (12, 13) on the inflow side or outflow side of the expander (22), and having a closed distal end.
  • the branch pipe type muffler (40) interference in pressure variation is allowed to be caused between the refrigerant flowing in the branch pipe (41) branching from the refrigerant pipe (12, 13) and the refrigerant having been reflected by the closed end of the branch pipe (41) to thus reduce the pressure pulsation of the refrigerant.
  • the interference type muffler (50) shown in FIG. 7 includes an interference pipe (51) branching from a refrigerant pipe (12, 13) on the inflow side of the expander (22), and interflowing again with refrigerant pipe (12, 13).
  • interference in pressure variation is allowed to be caused between the refrigerant flowing in the refrigerant pipe (12, 13) and the refrigerant flowing in the interference pipe (51) to reduce the pressure pulsation of the refrigerant.
  • Each of the mufflers (40, 50) has a device configuration simpler than the conventional accumulator, thereby enabling contemplation of cost reduction and maintenance facilitation of the muffler.
  • the expansion passage (32) may be formed in a spiral or coil shape, for example.
  • the spiral expansion passage (32) can lead to a compact design of the expansion type muffler (30) with the channel length of the expansion passage (32) secured to some extent.
  • a four-way switching valve (25) and a bridge circuit (26) including four check valves may be provided, as shown in FIG. 9 , to make the air conditioner (1) switchable between a cooling operation and a heating operation.
  • provision of any of the mufflers (30, 40, 50) on the inflow side of the expander (22) can reduce the pressure pulsation of the refrigerant on the inflow side or outflow side of the expander (22) during each operation.
  • carbon dioxide is used as the refrigerant in the refrigerant circuit (10) for performing the refrigeration cycle in which the carbon dioxide is compressed to over its critical pressure.
  • the compression mechanism of the compressor (20) and the expansion mechanism of the expander (22) may be connected to each other by means of a rotary shaft to compose a generally-called single shaft expander-compressor unit.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Pipe Accessories (AREA)

Claims (3)

  1. Kühlvorrichtung mit einem Kältemittelkreislauf (10), an den ein Kompressor (20) und eine positive Verdrängungsexpansionseinrichtung (22) angeschlossen sind, und der einen Kühlkreislauf durchführt, indem ein Kältemittel zirkuliert wird, umfassend:
    einen Expansions-Schalldämpfer (30), einen Abzweigrohr-Schalldämpfer (40) oder einen Interferenz-Schalldämpfer (50), wobei
    der Kältemittelkreislauf (10) Kohlendioxid als Kältemittel für die Durchführung des Kühlkreislaufs verwendet, in dem der Kompressor (20) das Kältemittel über seinen kritischen Druck hinaus komprimiert, dadurch gekennzeichnet,
    dass der Kältemittelkreislauf (10) Druckminderungsmittel (24) aufweist, um es einem Hochdruckkältemittel zu ermöglichen, in einem Gas-Flüssig-Zweiphasenzustand zu sein, indem der Druck des Hochdruckkältemittels verringert wird, und
    der Schalldämpfer (30, 40, 50) zwischen der Ausströmseite des Druckminderungsmittels (24) und der Anströmseite der Expansionseinrichtung (22) vorgesehen ist.
  2. Kühlvorrichtung nach Anspruch 1, umfassend:
    einen Expansions-Schalldämpfer (30), der einen Expansionskanal (32) aufweist, der an den jeweiligen Enden Öffnungsteile aufweist, an die Kältemittelleitungen angeschlossen sind, der Expansionskanal (32) einen Durchmesser aufweist, der größer ist als jede der Kältemittelleitungen, und
    eine Trennplatte (60), die eine Öffnung (61) mit einem Durchmesser kleiner als ein Innendurchmesser einer Kältemittelleitung an einem Öffnungsteil des Expansionskanals (32) auf der Seite der Expansionseinrichtung (22) aufweist.
  3. Kühlvorrichtung nach Anspruch 1, umfassend:
    einen Expansions-Schalldämpfer (30), der einen Expansionskanal (32) aufweist, der an den jeweiligen Enden Öffnungsteile aufweist, an die Kältemittelleitungen angeschlossen sind, der Expansionskanal (32) einen Durchmesser aufweist, der größer ist als jede der Kältemittelleitungen,
    wobei der Expansionskanal (32) in einer Spiralform ausgebildet ist.
EP07791431.5A 2006-08-01 2007-07-27 Kühlvorrichtung Active EP2048457B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006209708A JP4904970B2 (ja) 2006-08-01 2006-08-01 冷凍装置
PCT/JP2007/064737 WO2008015965A1 (fr) 2006-08-01 2007-07-27 Dispositif de réfrigération

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Publication Number Publication Date
EP2048457A1 EP2048457A1 (de) 2009-04-15
EP2048457A4 EP2048457A4 (de) 2015-03-04
EP2048457B1 true EP2048457B1 (de) 2016-08-31

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JP (1) JP4904970B2 (de)
WO (1) WO2008015965A1 (de)

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WO2008015965A1 (fr) 2008-02-07
JP4904970B2 (ja) 2012-03-28
EP2048457A4 (de) 2015-03-04
JP2008039199A (ja) 2008-02-21

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