EP2048456B1 - Dispositif de réfrigération - Google Patents

Dispositif de réfrigération Download PDF

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Publication number
EP2048456B1
EP2048456B1 EP07790874.7A EP07790874A EP2048456B1 EP 2048456 B1 EP2048456 B1 EP 2048456B1 EP 07790874 A EP07790874 A EP 07790874A EP 2048456 B1 EP2048456 B1 EP 2048456B1
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EP
European Patent Office
Prior art keywords
refrigerant
pressure
chamber
pipe
connection pipe
Prior art date
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EP07790874.7A
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German (de)
English (en)
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EP2048456A1 (fr
EP2048456A4 (fr
Inventor
Satoshi Ishikawa
Kazutaka Hori
Eiji Kumakura
Katsumi Sakitani
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication of EP2048456A4 publication Critical patent/EP2048456A4/fr
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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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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
    • F25B2500/13—Vibrations
    • 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
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigerating apparatus performing a vapor compression refrigeration cycle by circulating refrigerant, and particularly relates to a measure to reduce pressure pulsation of the refrigerant flowing in a refrigerant circuit.
  • 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.
  • the refrigerant compressing operation by the compressor and the refrigerant expanding operation by the expander may accompany variation in pressure of the refrigerant to cause large pressure pulsation of the refrigerant. This may lead to noise generation or malfunction of instruments connected to the refrigerant pipes.
  • Patent Document 2 proposes provision of a pulsation absorbing mechanism inside the expander for reducing the pressure pulsation of the refrigerant.
  • the pressure absorbing mechanism includes a hollow cylinder chamber formed in an expansion mechanism expanding the refrigerant, and a piston accommodated in the cylinder chamber.
  • the cylinder chamber communicates with a refrigerant inflow-side passage formed in the casing of the expander.
  • the piston shifts to change the volume of the cylinder chamber.
  • the pressure variation of the refrigerant is reduced by changing the volume of the cylinder to reduce the aforementioned pressure pulsation.
  • Patent Document 3 a high pressure refrigerant line on an inflow side of the expander is connected with a connection pipe to a back pressure chamber side of a piston in an pulsation absorbing cylinder while the other part of the cylinder connects to the same high pressure refrigerant line.
  • the present invention has been made in view of the foregoing, and its objective is to significantly reduce the pressure pulsation of refrigerant in a refrigerating apparatus performing a vapor compression refrigeration cycle.
  • a first aspect of the present invention is directed to a refrigerating apparatus according to claim 1 including a refrigerant circuit (10) to which a compressor (20) is connected and which performs a vapor compression refrigeration cycle by circulating refrigerant in refrigerant pipes (11, 12, 13 ,14).
  • the pulsation absorbing device (30) in the present invention is mounted, rather than inside the expander as in Patent Document 2, to the refrigerant pipe (11, 12, 13, 14) for connecting the compressor, the expander, and the like to each other. Accordingly, in the present invention, this pressure absorbing mechanism, which can be comparatively large in size, can be mounted to the refrigerant pipe (11, 12, 13, 14) without restraint of other components, such as those of the compressor.
  • variation in pressure of the refrigerant flowing in the refrigerant pipe (11, 12, 13, 14) connected to the first connection pipe (35) accompanies shifting of the piston (32).
  • the piston (32) shifts toward the second chamber (34) to increase the volume of the first chamber (33). This reduces each pressure in the first chamber (33) and the refrigerant pipe (11, 12, 13, 14) communicating with the first chamber (33) through the first connection pipe (35) to suppress the pressure increase of the refrigerant.
  • the piston (32) shifts toward the first chamber (33) to reduce the volume of the first chamber (33).
  • This increases each pressure in the first chamber (33) and the refrigerant pipe (11, 12, 13, 14) communicating with the first chamber (33) through the first connection pipe (35) to suppress the pressure lowering of the refrigerant.
  • the pulsation absorbing device (30) includes a second connection pipe (36) connecting the second chamber (34) and a refrigerant pipe (11, 12, 13, 14) and including a throttling mechanism (37), and the first connection pipe (35) and the second connection pipe (36) are connected to a refrigerant pipe (11, 12, 13, 14) at the same refrigerant pressure.
  • the second connection pipe (36) and the throttling mechanism (37) are provided.
  • the second connection pipe (36) and the first connection pipe (35) are connected to the refrigerant pipe(s) (11, 12, 13, 14) in which the refrigerant at the same pressure flows in the refrigerant circuit (10).
  • the pressure in the refrigerant pipe (11, 12, 13, 14) works on the first chamber (33) from the first connection pipe (35), while the pressure in the refrigerant pipe (11, 12, 13, 14) from the second connection pipe (35) works on the second chamber (34) after being reduced by the throttling mechanism (37).
  • the pressure of the refrigerant having reduced in the throttling mechanism (37) is allowed to work on the surface of the piston (32) in the second chamber (34) to absorb the pressure pulsation of the refrigerant in the first chamber (33).
  • the piston (32) stays at a predetermined point in the cylinder member (31).
  • the pressure in the first chamber (33) becomes abruptly higher than the that in the second chamber (34) due to no pressure reduction by the throttling mechanism (37) in the first connection pipe (35) to destroy the pressure balance between the chambers (33, 34).
  • the piston (32) shifts to increase the volume of the first chamber (33), so that the refrigerant is sucked by the increased volume into the first chamber (33) through the first connection pipe (35).
  • each pressure of the first chamber (33) and the refrigerant pipe (11, 12, 13, 14) communicating with the first chamber (33) lowers to suppress the pressure increase in the refrigerant pipe (11, 12, 13, 14).
  • the throttling mechanism (37) provided in the second connection pipe (36) it is hard for refrigerant in the second chamber (34) to flow into the refrigerant pipe (11, 12, 13, 14) through the second connection pipe (34). Accordingly, the volume decrease of the second chamber (34) gradually increases the pressure in the second chamber (34) to balance the pressure between the first chamber (33) and the second chamber (34) again.
  • the volume of the second chamber (34) increases.
  • the throttling mechanism (37) provided in the second connection pipe (36) it is hard for the refrigerant in the refrigerant pipe (11, 12, 13 , 14) to flow into the second chamber (34) through the second connection pipe (36). Accordingly, the volume increase of the second chamber (34) gradually lowers the pressure in the second chamber (34) to balance the pressure between the first chamber (33) and the second chamber (34) again.
  • a positive-displacement type expander (22) is connected to the refrigerant circuit (10), the first connection pipe (35) is connected to a refrigerant pipe (12) on an inflow side of the expander (22), and the second connection pipe (36) is connected to a refrigerant pipe (11) on a discharge side of the compressor (20).
  • the compressor (20) and the expander (22) are connected to the refrigerant circuit (10).
  • the refrigerant is compressed in the compressor (20) to be high-pressure refrigerant, radiates heat in a heat exchanger or the like, and then flows into the expander (22).
  • the expander (22) the high-pressure refrigerant is reduced in pressure to be low-pressure refrigerant.
  • the low-pressure refrigerant then evaporates in a heat exchanger or the like.
  • This refrigerant is compressed again in the compressor (20) to be high-pressure refrigerant.
  • the first connection pipe (35) is connected to the refrigerant pipe (12) on the inflow side of the expander (22).
  • the refrigerant on the inflow side of the expander (22) has comparatively higher density than high-pressure gas refrigerant and the like, and is therefore liable to cause large pressure pulsation.
  • the first connection pipe (35) is connected to the refrigerant pipe (12) on the inflow side of the expander (22) in the present aspect to effectively reduce the pressure pulsation of the refrigerant in the refrigerant pipe (12).
  • the second connection pipe (36) is connected to the refrigerant pipe (11) on the discharge side of the compressor (20). Accordingly, the second chamber (34) is filled with the refrigerant discharged from the compressor (20).
  • the refrigerant discharged from the compressor (20) is more compressive than high-pressure liquid refrigerant. Therefore, even when the piston (32) shifts accompanied by pressure variation of the refrigerant in the first chamber (33), the pressure in the second chamber (34) less varies. Accordingly, in the pulsation absorbing device (30) in the present aspect, the responsiveness of the piston (32) upon the pressure variation in the first chamber (33) can be enhanced to increase the efficiency of pressure pulsation absorption by the pulsation absorbing device (30).
  • a positive-displacement type expander (22) is connected to the refrigerant circuit (10), the first connection pipe (35) is connected to a refrigerant pipe (13) on an outflow side of the expander (22), and the second connection pipe (36) is connected to a refrigerant pipe (14) on a suction side of the compressor (20).
  • the first connection pipe (35) is connected to the refrigerant pipe (13) on the outflow side of the expander (22), so that the pulsation absorbing device (30) can effectively reduce the pressure pulsation on the outflow side of the expander (22) where comparatively large pressure pulsation is liable to be caused.
  • the second connection pipe (36) is connected to the refrigerant pipe (14) on the suction side of the compressor (20). Accordingly, the second chamber (34) is filled with low-pressure gas refrigerant on the suction side of the compressor (20).
  • the low-pressure gas refrigerant is more compressive than low-pressure liquid refrigerant and the like. Therefore, even when the piston (32) shifts accompanied by the pressure variation of the refrigerant in the first chamber (33), the pressure in the second chamber (34) less varies. Accordingly, in the pulsation absorbing device (30) in the present aspect, the responsiveness of the piston (32) upon the pressure variation in the first chamber (33) is enhanced to increase the efficiency of pressure pulsation absorption by the pulsation absorbing device (30).
  • a positive-displacement type expander (22) is connected to the refrigerant circuit (10), and both the first connection pipe (35) and the second connection pipe (36) are connected to one (13) of refrigerant pipes on an inflow side and an outflow side of the expander.
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipe (12) on the inflow side of the expander (22) or to the refrigerant pipe (13) on the outflow side of the expander (22). Since the refrigerant on the outflow side and the inflow side of the expander (22) has comparatively high density, large pressure pulsation of the refrigerant is liable to be caused. To tackle this problem, the pulsation absorbing device (30) is provided to the refrigerant pipes (12, 13) in the present aspect to effectively reduced the pressure pulsation of the refrigerant in the refrigerant pipes (12, 13).
  • both the first connection pipe (35) and the second connection pipe (36) are connected to one of refrigerant pipes (11, 14) on a discharge side and a suction side of the compressor (20).
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipe (11) on the discharge side of the compressor (20) or to the refrigerant pipe (14) on the suction side of the compressor (20).
  • the refrigerant compressing operation by the compressor (20) may accompany large pressure pulsation of the refrigerant on the suction side and the discharge side of the compressor (20).
  • the pulsation absorbing device (30) are provided to the refrigerant pipes (11, 14) in the present aspect to effectively reduced the pressure pulsation of the refrigerant in the refrigerant pipes (11, 14).
  • the refrigeration cycle is performed with the carbon dioxide compressed to over its critical pressure.
  • the refrigerant is compressed to over its critical pressure, large pressure pulsation of the refrigerant is liable to be caused.
  • the pressure pulsation of the refrigerant is suppressed by the pulsation absorbing device (30) effectively.
  • the pulsation absorbing device (30) is connected to the refrigerant pipe (11, 12, 13, 14) through the first connection pipe (35).
  • the pulsation absorbing device (30) is mounted directly to the refrigerant pipe (11, 12, 13, 14) unlike a pulsation absorbing mechanism provided inside the expander as in Patent Document 2. Accordingly, the present invention can contemplate enlarging the pulsation absorbing device (30), and in turn, can contemplate increasing the volume of the first chamber (33) in the cylinder member (31). This can lead to remarkable suppression of the pressure pulsation of the refrigerant by the pulsation absorbing device (30). Provision of the pulsation absorbing device (30) to the refrigerant pipe (11, 12, 13, 14) facilitates maintenance and replacement of the pulsation absorbing device (30), which is the difference from the case where it is incorporated inside the expander.
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipe(s) (11, 12, 13, 14) at the same pressure, and the throttling mechanism (37) is provided in the second connection pipe (36). Accordingly, the pressure pulsation of the refrigerant in the refrigerant pipe (11, 12, 13, 14) communicating with the first connection pipe (35) can be suppressed effectively by utilizing the pressure of the refrigerant working on the second chamber (34) through the second connection pipe (36).
  • the first chamber (33) communicates with the refrigerant pipe (12) on the inflow side of the expander (22), and the refrigerant discharged from the compressor (20) is introduced into the second chamber (34). Accordingly, the responsiveness of the piston (32) upon the pressure variation on the inflow side of the expander (22) is enhanced when compared with that in the case, for example, where liquid refrigerant works on the second chamber (34), thereby effectively absorbing the pressure pulsation of the refrigerant in the refrigerant pipe (12) on the inflow side of the expander (22).
  • the first chamber (33) communicates with the refrigerant pipe (13) on the outflow side of the expander (22), and the gas refrigerant on the suction side of the compressor (20) is introduced into the second chamber (20). Accordingly, the responsiveness of the piston (32) upon the the pressure variation on the outflow side of the expander (22) is enhanced when compared with that in the case, for example, where liquid refrigerant works on the second chamber (34), thereby effectively absorbing the pressure pulsation of the refrigerant in the refrigerant pipe (13) on the outflow side of the expander (22).
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipe (12) on the inflow side of the expander (22) or to the refrigerant pipe (13) on the outflow side of the expander (22). Accordingly, in the present aspect, the pressure pulsation of the refrigerant can be suppressed effectively at a part where large pressure pulsation of the refrigerant is liable to be caused due to comparatively large refrigerant density.
  • the present aspect since there is little temperature difference between the refrigerant flowing in the first connection pipe (35) and the refrigerant flowing in the second connection pipe (36), less or no heat exchange of the refrigerant may occur between the first chamber (33) and the second chamber (34). Hence, according to the present aspect, heat loss in the refrigerant circuit (10) accompanied by heat exchange of the refrigerant in the pulsation absorbing device (30) can be avoided.
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipe (11) on the discharge side of the compressor (20) or to the refrigerant pipe (14) on the outflow side of the compressor (20). Accordingly, in the present aspect, the pressure pulsation of the refrigerant can be suppressed effectively at a part where large pressure pulsation of the refrigerant is liable to be caused due to comparatively large refrigerant density.
  • the pulsation absorbing device (30) according to any one of the first to sixth aspects is applied to the refrigerant circuit (10) performing the refrigeration cycle in which carbon dioxide is compressed to over its critical pressure.
  • the present aspect can suppress the pressure pulsation effectively.
  • Embodiment 1 of the present invention will be described.
  • a refrigerating apparatus in accordance with Embodiment 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, 13, 14).
  • a first high-pressure refrigerant pipe (11) is connected to the discharge side of the compressor (20.
  • the other end of the first high-pressure refrigerant pipe (11) is connected to one end of the radiator (21).
  • the other end of the radiator (21) is connected to one end of a second high-pressure refrigerant pipe (12).
  • the other end of the second high-pressure refrigerant 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 a first low-pressure refrigerant pipe (13).
  • the other end of the first low-pressure refrigerant 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 second low-pressure refrigerant pipe (14).
  • the other end of the second low-pressure refrigerant pipe (14) is connected to the suction side of the compressor (20).
  • the compressor (20) is of positive displacement type.
  • the compressor (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-pressure gas refrigerant indoors.
  • the expander (22) is of 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 low-pressure refrigerant.
  • the evaporator (23) is disposed in an outdoor space, for example, and is composed of a fin-and-tube heat exchanger. In the evaporator (23), the low-pressure liquid refrigerant absorbs heat from the outdoor air to be evaporated.
  • a pulsation absorbing device (30) is provided in the refrigerant circuit (10).
  • the pulsation absorbing device (30) includes a cylinder member (31) and a piston (32).
  • the cylinder member (31) is in a hollow cylindrical shape to form a column-shaped cylinder chamber thereinside.
  • the piston (32) is in a column shape, and is accommodated in the cylinder chamber of the cylinder member (31).
  • the piston (32) divides the cylinder chamber into a pressure buffering chamber (33) as a first chamber and a back pressure chamber (34) as a second chamber.
  • the piston (32) is made of a comparatively lightweight aluminum material.
  • a spring (32a) is provided in the back pressure chamber (34) of the cylinder chamber in the cylinder member (31).
  • the spring (32a) is connected at one end thereof to the inner wall of the cylinder member (31) while being connected at the other end thereof to the piston (32).
  • the spring (32a) is composed of as an elastic member for pushing the piston (32) from the back pressure chamber (34) toward the pressure buffering chamber (33).
  • the pulsation absorbing device (30) includes a first connection pipe (35) and a second connection pipe (36).
  • the first connection pipe (35) is connected at one end thereof to the pressure buffering chamber (33), while being connected at the other end thereof to the second high-pressure refrigerant pipe (12).
  • the pressure buffering chamber (33) communicates with the second high-pressure refrigerant pipe (12) through the first connection pipe (35).
  • the second connection pipe (36) is connected at one end thereof to the back pressure chamber (34) while being connected at the other end thereof to the first high-pressure refrigerant pipe (11).
  • the back pressure chamber (34) communicates with the first high-pressure refrigerant pipe (11) through the second connection pipe (36).
  • a capillary tube (37) is provided in the second connection pipe (36).
  • the capillary tube (37) serves as a throttling mechanism for reducing the pressure of the refrigerant.
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipes (11, 12), respectively, in which the refrigerant flows at the same pressure.
  • the pressure buffering chamber (33) is filled with high-pressure refrigerant in a gas-liquid two-phase state, while the back pressure chamber (34) is filled with the refrigerant having been reduced in pressure by the capillary tube (37).
  • the piston (32) shifts in the cylinder chamber according to pressure variation of the refrigerant flowing in the second high-pressure refrigerant pipe (12) to change the volume of the pressure buffering chamber (33).
  • 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 first low-pressure refrigerant pipe (13).
  • the refrigerant flowing in the first low-pressure refrigerant pipe (13) flows into the evaporator (23).
  • the liquid refrigerant absorbs heat from the outdoor air to be evaporated.
  • the gas refrigerant having been evaporated in the evaporator (23) flows into the second low-pressure refrigerant pipe (14), and is then sucked into the compressor (20).
  • the refrigerant is compressed again to over its critical pressure.
  • refrigerant compression by the compressor (20) and refrigerant expansion by the expander (22) 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 second high-pressure refrigerant pipe (12) on the inflow side of the expander (22) the refrigerant of which the density is comparatively large flows, and therefore, large pressure pulsation is liable to be caused.
  • the pressure pulsation of the refrigerant flowing in the second high-pressure refrigerant pipe (12) is suppressed by the pulsation absorbing device (30).
  • the piston (32) In a normal state in which the pressure of the refrigerant does not vary in the second high-pressure refrigerant pipe (12), the piston (32) is in the state shown in FIG. 2(A) , for example. In this state, the balance is kept between the pressure of the refrigerant working on the surface of the piston (32) on the side of the pressure buffering chamber (33) from the first high-pressure refrigerant pipe (11) through the first connection pipe (35) and the pressure of the refrigerant working on the piston (32) on the side of the back pressure chamber (34) from the second high-pressure refrigerant pipe (12) through the second connection pipe (36) and the capillary tube (37) plus the spring force of the spring (32a) against the piston (32).
  • the volume of the back pressure chamber (34) decreases at that time.
  • the capillary tube (37) is provided in the second connection pipe (36) communicating with the back pressure chamber (34), it is hard for the refrigerant in the back pressure chamber (34) to flow into the first high-pressure refrigerant pipe (11) through the second connection pipe (36).
  • the decrease in volume of the back pressure chamber (34) leads to a gradual increase in pressure in the back pressure chamber (34) to balance the forces working on the piston (32).
  • the volume of the back pressure chamber (34) increases at that time.
  • the capillary tube (37) is provided in the second connection pipe (36), it is hard for the refrigerant flowing in the first high-pressure refrigerant pipe (11) to flow into the back pressure chamber (34) through the second connection pipe (36).
  • the increase in volume of the back pressure chamber (34) leads to a gradual decrease in pressure in the back pressure chamber (34) to balance the forces working on the piston (32).
  • the pulsation absorbing device (30) moves the piston (32) ahead or behind, as shown in FIG. 2(B) or FIG. 2(C) .
  • increase and decrease in pressure of the refrigerant flowing in the second high-pressure refrigerant pipe (12) can be suppressed to contemplate suppression of the pressure pulsation of the refrigerant.
  • the pulsation absorbing device (30) is connected to the refrigerant pipes (11, 12) by means of the first connection pipe (35) and the second connection pipe (36).
  • the pulsation absorbing device (30) is mounted directly to the refrigerant pipes (11, 12). Accordingly, in Embodiment 1, it can be contemplated to increase the size of the pulsation absorbing device (30), and in turn to increase the volume of the cylinder chamber in the cylinder member (31), thereby enabling the pulsation absorbing device (30) to remarkably reducing the pressure pulsation of the refrigerant.
  • provision of the pulsation absorbing device (30) to the refrigerant pipes (11, 12) facilitates maintenance and replacement of the pulsation absorbing device (30) unlike the case where it is incorporated in the expander.
  • the first connection pipe (35) and the second connection pipe (36) are connected to the refrigerant pipes (11, 12) at the same pressure, respectively, and the capillary tube (37) is provided in the second connection pipe (36). Accordingly, the pressure pulsation of the refrigerant in the second high-pressure refrigerant pipe (12) can be absorbed effectively by utilizing the pressure of the refrigerant working on the back pressure chamber (34) through the second connection pipe (36).
  • the pressure buffering chamber (33) communicates with the second high-pressure refrigerant pipe (12) on the inflow side of the expander (22), while the back pressure chamber (34) communicates with the first high-pressure refrigerant pipe (11) on the discharge side of the compressor (20) for introducing the refrigerant discharged from the compressor (20) into the back pressure chamber (34).
  • the refrigerant discharged from the compressor (20) is more compressive than, for example, high-pressure liquid refrigerant. Therefore, even when the piston (32) shifts accompanied by the pressure variation of the refrigerant in the pressure buffering chamber (33), the pressure in the back pressure chamber (34) hardly varies.
  • the responsiveness of the piston (32) upon the pressure variation in the pressure buffering chamber (33) is enhanced when compared with the case where liquid refrigerant is introduced into the back pressure chamber (34), thereby achieving effective absorption of the pressure pulsation of the refrigerant in the second high-pressure refrigerant pipe (12).
  • An air conditioner (1) in accordance with a modified example of Embodiment 1, not part of the invention, is different from that in Embodiment 1 in the connection point of the second connection pipe (36) of the pulsation absorbing device (30).
  • the other end of the second connection pipe (36) is connected to the second high-pressure refrigerant pipe (12) as well as that of the first connection pipe (35) is.
  • the refrigerant in the second high-pressure refrigerant pipe (12) is introduced into both the pressure buffering chamber (33) and the back pressure chamber (34).
  • the piston (32) shifts according to the pressure variation of the refrigerant flowing in the second high-pressure refrigerant pipe (12) to increase or decrease the volume of the pressure buffering chamber (33).
  • the pressure pulsation of the refrigerant flowing in the second high-pressure refrigerant pipe (12) is suppressed, similarly to the case in Embodiment 1.
  • both the first connection pipe (35) and the second connection pipe (36) are connected to the second high-pressure refrigerant pipe (12), and therefore, there is little temperature difference between the refrigerant flowing in the respective connection pipes (11, 12). Accordingly, in the present modified example, heat exchange of the refrigerant between the pressure buffering chamber (33) and the back pressure chamber (34) via the piston (32) can be prevented. Hence, according to the present modified example, heat loss in the refrigerant circuit (10), which is accompanied by heat exchange of the refrigerant in the pulsation absorbing device (30), can be avoided.
  • the first connection pipe (35) of the pulsation absorbing device (30) is connected to the first low-pressure refrigerant pipe (13) on the outflow side of the expander (22), while the second connection pipe (36) is connected to the second low-pressure refrigerant pipe (14) on the suction side of the compressor (20).
  • the low-pressure refrigerant flowing out from the expander (22) is introduced into the pressure buffering chamber (33), while the low-pressure gas refrigerant on the suction side of the compressor (20) is introduced into the back pressure chamber (34).
  • the piston (32) shifts according to the pressure variation of the refrigerant flowing in the first low-pressure refrigerant pipe (13) to suppress, similarly to the case in Embodiment 1, the pressure pulsation of the refrigerant flowing in the first low-pressure refrigerant pipe (13).
  • the back pressure chamber (34) is filled with the low-pressure gas refrigerant. Accordingly, the responsiveness of the piston (32) that shifts accompanied by the pressure variation in the pressure buffering chamber (33) is enhanced when compared with the case, for example, where the back pressure chamber (34) is filled with liquid refrigerant. Hence, according to Embodiment 2, the pressure pulsation of the refrigerant in the first low-pressure refrigerant pipe (13) can be absorbed effectively.
  • An air conditioner (1) in accordance with a modified example of Embodiment 2, not part of the invention, is different from that in Embodiment 2 in the connection point of the second connection pipe (36) of the pulsation absorbing device (30).
  • the other end of the second connection pipe (36) is connected to the first low-pressure refrigerant pipe (13), as well as that of the first connection pipe (35) is.
  • the refrigerant in the first low-pressure refrigerant pipe (13) is introduced into both the pressure buffering chamber (33) and the back pressure chamber (34).
  • the piston (32) shifts according to the pressure variation of the refrigerant flowing in the first low-pressure refrigerant pipe (13) to increase or decrease the volume of the pressure buffering chamber (33).
  • the pressure pulsation of the refrigerant flowing in the first low-pressure refrigerant pipe (13) is suppressed in a similar manner to that in Embodiment 2.
  • both the first connection pipe (35) and the second connection pipe (36) are connected to the first low-pressure refrigerant pipe (13), and accordingly, there is little temperature difference between the refrigerant flowing in the connection pipes (35, 36). Accordingly, less or no heat exchange of the refrigerant may occur between the pressure buffering chamber (33) and the back pressure chamber (34) via the piston (32).
  • heat loss in the refrigerant circuit (10) which is accompanied by heat exchange of the refrigerant in the pulsation absorbing device (30), can be avoided.
  • the first connection pipe (35) and the second connection pipe (36) of the pulsation absorbing device (30) are connected to the first high-pressure refrigerant pipe (11) on the discharge side of the compressor (20).
  • the refrigerant discharged from the compressor (20) is introduced into both the pressure buffering chamber (33) and the back pressure chamber (34).
  • the piston (32) shifts according to the pressure variation of the refrigerant flowing in the first high-pressure refrigerant pipe (11) to suppress the pressure pulsation of the refrigerant flowing in the first high-pressure refrigerant pipe (11) in a similar manner to that in each of the above embodiments.
  • both the first connection pipe (35) and the second connection pipe (36) are connected to the first high-pressure refrigerant pipe (11), and accordingly, there is little temperature difference between the refrigerant flowing in the connection pipes (35, 36).
  • heat loss in the refrigerant circuit (10) which is accompanied by heat exchange of the refrigerant in the pulsation absorbing device (30), can be avoided.
  • the first connection pipe (35) and the second connection pipe (36) of the pulsation absorbing device (30) are connected to the second low-pressure refrigerant pipe (14) on the suction side of the compressor (20).
  • the refrigerant on the suction side of the compressor (20) is introduced into both the pressure buffering chamber (33) and the back pressure chamber (34).
  • the piston (32) shifts according to the pressure variation of the refrigerant flowing in the second low-pressure refrigerant pipe (14) to suppress the pressure pulsation of the refrigerant flowing in the second low-pressure refrigerant pipe.
  • the air conditioner (1) may be switchable between a cooling operation and a heating operation, as shown in, for example, FIG. 8 .
  • a four-way switching valve (50) and a bridge circuit (60) are provided in the refrigerant circuit (10).
  • the four-way switching valve (50) is switchable between the state indicated by the solid lines and the state indicated by the broken lines in FIG. 8 to revere the refrigerant circulating direction, thereby enabling switching between the heating operation and the cooling operation.
  • provision of the pulsation absorbing device (30) of the present invention to the refrigerant pipes as shown in FIG. 8 leads to suppression of the pressure pulsation of the refrigerant in both the cooling operation and the heating operation.
  • carbon dioxide is used as the refrigerant in the refrigerant circuit (10), and the refrigeration cycle is performed while the carbon dioxide is compressed to over its critical pressure.
  • the refrigerant circuit (10) may use another refrigerant, such as R410A or the like. In this case, the refrigerant may not be necessarily 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.
  • the pulsation absorbing device (30) in the present invention is applied to an air conditioner utilizing heat radiated in the radiator (21) for indoor heating. While, the pulsation absorbing device (30) in the present invention may be applied to any of a water heater for heating water by heat radiated in the radiator (21), a refrigerating apparatus performing indoor cooling or refrigerator cooling by heat from the evaporator (23), and the like, for example.
  • the present invention is useful in measures for suppressing the pressure pulsation of refrigerant in a refrigerating apparatus performing a vapor compression refrigeration cycle by circulating the refrigerant.

Landscapes

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

Claims (2)

  1. Appareil de réfrigération comportant un circuit de fluide frigorigène (10) auquel un compresseur (20) est raccordé et qui réalise un cycle de réfrigération à compression de vapeur en faisant circuler du fluide frigorigène dans des conduites de fluide frigorigène (11, 12, 13, 14), l'appareil de réfrigération comprenant :
    un dispositif d'absorption de pulsation (30) comportant :
    un organe cylindrique creux (31) ;
    un piston (32) séparant un espace interne de l'organe cylindrique (31) en une première chambre (33) et une seconde chambre (34) et se déplaçant dans l'organe cylindrique (31) selon une variation de pression dans la première chambre (33), et
    une première conduite de raccordement (35) raccordant la première chambre (33) à une conduite de fluide frigorigène (11, 12, 13, 14), dans lequel
    le dispositif d'absorption de pulsation (30) comporte une seconde conduite de raccordement (36) raccordant la seconde chambre (34) et une conduite de fluide frigorigène (11, 12, 13, 14) et comportant un mécanisme d'étranglement (37),
    le dispositif d'absorption de pulsation (30) comporte
    la première conduite de raccordement (35) raccordée entre un côté de débit entrant d'un dispositif de détente (22) et un côté de débit sortant d'un radiateur (21), et la seconde conduite de raccordement (36) raccordée entre un côté d'évacuation du compresseur (20) et un côté de débit entrant du radiateur (21), ou
    le dispositif d'absorption de pulsation comporte la première conduite de raccordement (35) raccordée entre un côté de débit sortant du dispositif de détente (22) et un côté de débit entrant d'un évaporateur (23), et la seconde conduite de raccordement (36) raccordée entre un côté de débit sortant de l'évaporateur (23) et un côté d'aspiration du compresseur (20).
  2. Appareil de réfrigération selon la revendication 1, dans lequel
    dans le circuit de fluide frigorigène (10), du dioxyde de carbone est utilisé en tant que fluide frigorigène, et le cycle de réfrigération est réalisé tandis que le fluide frigorigène dans le compresseur (20) est comprimé jusqu'au-delà de sa pression critique.
EP07790874.7A 2006-07-26 2007-07-17 Dispositif de réfrigération Active EP2048456B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006202827A JP4140642B2 (ja) 2006-07-26 2006-07-26 冷凍装置
PCT/JP2007/064112 WO2008013079A1 (fr) 2006-07-26 2007-07-17 Dispositif de réfrigération

Publications (3)

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EP2048456A1 EP2048456A1 (fr) 2009-04-15
EP2048456A4 EP2048456A4 (fr) 2015-03-04
EP2048456B1 true EP2048456B1 (fr) 2017-08-30

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EP07790874.7A Active EP2048456B1 (fr) 2006-07-26 2007-07-17 Dispositif de réfrigération

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EP2577188B1 (fr) * 2010-06-01 2019-12-25 Carrier Corporation Suppression des impulsions
CN102072591A (zh) * 2011-01-18 2011-05-25 蔡茂林 变容积式智能热泵
CN103604245B (zh) * 2013-07-22 2016-04-13 陈恩鉴 一种装有能效增大器的蒸气压缩式空调系统
KR101461623B1 (ko) * 2013-08-12 2014-11-20 (주)한엑스 맥동 저감 기능을 구비한 냉동싸이클장치
US10591100B2 (en) * 2017-11-15 2020-03-17 Ford Global Technologies, Llc Refrigerant hammer arrestor and refrigerant loop incorporating that refrigerant hammer arrestor

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD264257A1 (de) * 1987-09-17 1989-01-25 Erfurt Kuehlmoebelwerk Daempfungseinrichtung fuer druckschwingungen in hubkolbenverdichtern
NO915127D0 (no) * 1991-12-27 1991-12-27 Sinvent As Kompresjonsanordning med variabelt volum
JPH10159719A (ja) * 1996-11-28 1998-06-16 Hitachi Constr Mach Co Ltd 油圧ポンプの脈動低減装置
JP2000234814A (ja) 1999-02-17 2000-08-29 Aisin Seiki Co Ltd 蒸気圧縮式冷凍装置
JP2002188581A (ja) * 2000-12-19 2002-07-05 Mitsubishi Heavy Ind Ltd 冷媒ポンプシステム
JP2004190938A (ja) * 2002-12-11 2004-07-08 Daikin Ind Ltd 冷凍装置
JP4093311B2 (ja) 2003-03-19 2008-06-04 シャープ株式会社 画像形成装置
US20050194207A1 (en) * 2004-03-04 2005-09-08 York International Corporation Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator
JP4617812B2 (ja) * 2004-09-30 2011-01-26 ダイキン工業株式会社 容積型膨張機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP4140642B2 (ja) 2008-08-27
JP2008032243A (ja) 2008-02-14
EP2048456A1 (fr) 2009-04-15
WO2008013079A1 (fr) 2008-01-31
EP2048456A4 (fr) 2015-03-04

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