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WO1996011369A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

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Publication number
WO1996011369A1
WO1996011369A1 PCT/JP1995/002039 JP9502039W WO9611369A1 WO 1996011369 A1 WO1996011369 A1 WO 1996011369A1 JP 9502039 W JP9502039 W JP 9502039W WO 9611369 A1 WO9611369 A1 WO 9611369A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
valve
dehumidification
refrigerant passage
Prior art date
Application number
PCT/JP1995/002039
Other languages
English (en)
Japanese (ja)
Inventor
Tomomi Umeda
Tomomichi Kaneko
Hidenori Yokoyama
Motoo Morimoto
Hiroo Nakamura
Original Assignee
Hitachi, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi, Ltd. filed Critical Hitachi, Ltd.
Publication of WO1996011369A1 publication Critical patent/WO1996011369A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to an air conditioner capable of performing a dehumidification operation that performs dehumidification while preventing a decrease in room temperature by using a refrigeration cycle, and is particularly suitable for reducing refrigerant flow noise generated by a dehumidification expansion device during a dehumidification operation.
  • air conditioners Related to air conditioners. Background art
  • the refrigerant flows into the dehumidification expansion device, so that the upstream side of the two-part indoor heat exchanger is used as the evaporator, the downstream side is used as the evaporator, and the evaporator is used as the evaporator. It cools and dehumidifies and heats it with a coke oven to enable a dehumidifying operation that lowers the humidity without significantly lowering the temperature blown out of the air conditioner.
  • a two-way valve structure with a small hole that uses a small hole provided in the movable part of the two-way valve as the dehumidifying throttle device S.
  • a large refrigerant flow noise which is a continuous sound or a discontinuous sound
  • the magnitude of the refrigerant flow noise is generated by the expansion device. It is greatly influenced by the flow mode of the high-pressure refrigerant flowing in.
  • the refrigerant flow noise becomes very loud when a slag flow or a plug flow occurs in which shell-shaped bubbles and liquid appear alternately in a two-phase flow state of gas and liquid.
  • the continuous flow noise is mainly caused by the liquid refrigerant being decompressed and expanded at the throttle section of the expansion device to form a high-speed gas-liquid two-phase jet.
  • Discontinuous flow noise is mainly due to pressure
  • the gas refrigerant and the liquid refrigerant, which is an incompressible fluid, are caused by large pressure fluctuations that occur when they alternately pass through the narrow flow path of the expansion device.
  • a conventional example aimed at reducing such refrigerant flow noise is disclosed in Japanese Patent Publication No. 57-129371.
  • This conventional example relates to a reduction in refrigerant flow noise in a throttling device provided between an outdoor heat exchanger and a room-to-heat exchanger used in a cooling operation or a heating operation, and an expansion valve which is a throttling device g.
  • a fixed orifice is provided on the upstream side (high pressure side) to increase the number of air bubbles in the refrigerant when passing through the expansion valve, and to make the distribution uniform to reduce the noise level.
  • the chamber that acts as a condenser upstream of the dehumidification expansion device and the outlet of the heat exchanger have a gas-liquid two-phase outlet.
  • loud refrigerant flow noise is generated at the dehumidifying expansion device.
  • the dehumidifying squeezing device S is provided on the room ⁇ side, it gives a feeling of discomfort to a person in the living space.
  • noise reduction has conventionally been attempted by providing damping material and sound insulation material.
  • the demand for comfort has become extremely high, and noise has also been required to be further reduced.
  • An object of the present invention is to provide an air conditioner capable of a dehumidifying operation in which dehumidification is performed while preventing a decrease in room temperature by a refrigeration cycle, and to prevent a decrease in performance in a cooling operation or a heating operation, and to perform a dehumidifying expansion device during a dehumidifying operation.
  • An object of the present invention is to provide an air conditioner capable of reducing the refrigerant flow noise generated in the air conditioner. Disclosure of the invention
  • an air conditioner of the present invention includes a pressure box machine, a heat source side heat exchanger, and a use side heat exchanger, and the child side heat exchanger is thermally divided into two.
  • a dehumidifying throttle device used during the dehumidifying operation is provided between the two heat exchangers.
  • the upstream side of the use-side heat exchanger is a coagulator and the downstream side is an evaporator.
  • the dehumidification expansion device includes a high-pressure side refrigerant flow path and a low-pressure side refrigerant flow path that are provided in the valve body and allow the refrigerant to flow.
  • a valve port that penetrates the high-pressure side refrigerant flow path and an open port that communicates with the low-pressure side refrigerant flow path, and forms a main refrigerant passage connecting the valve port and the open port. Adjusting the refrigerant flow i passing through the main refrigerant passage connecting the valve port and the opening port.
  • a valve stem that can reciprocate in the main refrigerant passage for changing the opening area of the refrigerant passage, separately from the main refrigerant passage, a high-pressure side refrigerant flow path and a low-pressure side refrigerant flow.
  • a dehumidification control valve having a sub-refrigerant passage that passes through the passage.
  • the heat exchanger further includes a compressor, a heat source-side heat exchanger, and a use-side heat exchanger, wherein the use-side heat exchanger is thermally divided into two parts.
  • a dehumidifying expansion device used during dehumidification operation is provided, and a refrigeration cycle is configured so that during dehumidification operation, dehumidification is performed by using a condenser upstream of the utilization side heat exchanger and an evaporator downstream.
  • the dehumidifying expansion device communicates with the high-pressure side refrigerant flow path, the low-pressure side refrigerant flow path, and the high-pressure side refrigerant flow path through which the refrigerant flows through the valve body.
  • Changing the opening area of the refrigerant passage to adjust the flow rate of the refrigerant passing through the main refrigerant passage A valve stem capable of reciprocating in the main refrigerant passage ⁇ for causing And a dehumidification control valve having an auxiliary refrigerant passage for allowing the refrigerant to flow from the high-pressure side refrigerant flow path to the low-pressure side refrigerant flow path through the valve stem and the valve body poorly. It is characterized by having.
  • a pressure box machine a heat source side heat exchanger, and a use side heat exchanger are provided, and the use side heat exchanger is thermally divided into two parts.
  • a dehumidifying expansion device e used during dehumidification operation is inserted, and during dehumidification operation, dehumidification is performed by using a box box on the upstream side of the heat exchanger on the utilization side and an evaporator on the downstream side.
  • the dehumidifying throttle device e is provided in the valve body and has a high-pressure side refrigerant flow path and a low-pressure side refrigerant flow path through which refrigerant flows, and the high-pressure side refrigerant flow path.
  • a low-pressure side refrigerant flow path having a valve port and an open port through which a main refrigerant passage connecting the valve port and the open port is formed, and the valve port and the open port.
  • the special dehumidification control valve is provided as a special hinoki.
  • sub-refrigerant passage of the dehumidification control valve is configured such that an inlet hole on the high-pressure side refrigerant flow path side is provided at an upper end of the high-pressure side refrigerant flow path.
  • the air conditioner is configured as described above, in the dehumidification control valve used as the dehumidification expansion device, the gap between the main refrigerant passage connecting the valve port and the opening port, that is, the gap between the valve rod and the valve seat.
  • a sub-refrigerant passage that penetrates through the valve stem and the valve body and allows the refrigerant to flow through the high-pressure side refrigerant flow path and the low-pressure side refrigerant flow path is provided. It can be diverted.
  • the refrigerant flow rate can be differentiated, Since the momentum and kinetic energy of the fluid decrease, the exciting force of the fluid is reduced, and the refrigerant flow noise generated when the refrigerant flow passes through the valve of the dehumidifying expansion device is reduced.
  • an inlet hole on the low-pressure side refrigerant flow path is provided at the upper end of the high-pressure side refrigerant flow path, and the main refrigerant passage is located at the lower end of the high-pressure side refrigerant flow path.
  • the refrigerant flows into the dehumidification control valve in a gas-liquid two-phase state, it has a gas-liquid separation function, so that liquid refrigerant flows through the main refrigerant passage and gas refrigerant flows through the sub-refrigerant passage. Since a refrigerant passage can be secured, it is possible to prevent gas from flowing into the throttle portion in a gas-liquid two-phase state.
  • the flow path is discontinuously changed in shape, so that the pressure is reduced stepwise and the flow path is made maze, so that the kinetic energy of the refrigerant flow is reduced. Since the heat is dissipated and the excitation force can be reduced, the flow noise of the refrigerant can be reduced.
  • FIG. 1 is a configuration diagram of a freezing cycle using a dehumidification control valve having two refrigerant passages according to one embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional view showing a dehumidifying expansion device using the dehumidifying control valve having two refrigerant passages of the present embodiment.
  • FIG. 3 is a longitudinal sectional view showing a dehumidifying expansion device using a dehumidifying control valve having two refrigerant passages and a gas-liquid separation function of the present embodiment.
  • FIG. 4 is a longitudinal sectional view showing a dehumidification expansion device using the dehumidification control valve having two refrigerant passages of the present embodiment.
  • FIG. 5 is a longitudinal sectional view showing a dehumidifying expansion device using a dehumidifying control valve having two refrigerant passages according to the present embodiment.
  • FIG. 6 shows a throttling device used in a cooling and heating operation according to another embodiment of the present invention.
  • FIG. 3 is a configuration diagram of a refrigeration cycle using a dehumidification control valve.
  • FIG. 1 is a diagram showing a configuration of a refrigeration cycle of the present embodiment
  • FIG. 2 is a longitudinal sectional view showing a structure of a dehumidification control valve which performs a throttling operation during a dehumidification operation of a dehumidification expansion device 7 of the present embodiment
  • FIG. 4 is a longitudinal sectional view showing a structure of a dehumidification control valve having a gas-liquid separation function
  • FIG. 4 is a longitudinal sectional view showing a dehumidification throttle device S using a dehumidification control valve having two refrigerant passages, and FIG. It is a longitudinal section showing a dehumidification expansion device using a dehumidification control valve which has a passage.
  • the air conditioner of this embodiment includes a pressure box machine 1, a four-way valve 2 for switching operation states such as a cooling operation and a heating operation, an outdoor heat exchanger 3, and a cooling operation and a heating operation.
  • the main throttle device S 4 through which the refrigerant flows at the time, the two-way valve 5 that is provided in parallel with the main throttle device S 4 and allows the refrigerant to flow during the dehumidifying operation, the indoor heat exchangers 6 a and 6 b divided into two, and the indoor heat exchanger
  • It consists of an outdoor fan 9 for blowing air, an indoor fan 10 for blowing air to the indoor heat exchangers 6a and 6b, and the like.
  • the valve body 23 is formed integrally with a valve seat 36 having a valve port 31 and an open port 30, and a valve rod 34 and a valve rod 34 positioned therein.
  • the valve body 3 5 attached to the valve stem 3 4, the electromagnetic coil 20 for driving the valve body 35, the suction element 21 for sucking the valve body 35, and the valve body 35 3 Consists of springs 22 pressed against the 1 side.
  • the electromagnetic coil 20 When the electromagnetic coil 20 is energized, a magnetic force is generated in the attraction element 21, and the valve stem 34 is provided due to the balance between the spring force of the spring 22 and the attraction force of the attraction element 21.
  • the valve body 35 moves up and down the valve body 23 ⁇ .
  • valve stem 34 moves up and down between the valve seats 36, and the throttle amount changes. At this time, it is set so that the valve rod 34 can be removed from the valve seat 36 and the main refrigerant passage 27 can be opened.
  • the refrigerant flows from the inlet pipe 33 of the dehumidification control valve into the refrigerant passage 32 on the high pressure side, passes through the two refrigerant passages, flows into the refrigerant passage 28 on the low pressure side, and exits. Outflow from pipe 29.
  • the branched refrigerant passages are formed in the main refrigerant passage 27 formed by a gap between the valve rod 34 and the valve seat 36, the refrigerant passage 32 on the high pressure side, and the valve body 23.
  • the refrigerant passage 25 provided in the valve rod 34 penetrates the refrigerant passage 25 passing through the space 24 and the space 2 formed in the valve body 23 and the refrigerant passage 28 on the low pressure side. 6 is a sub refrigerant passage.
  • the space 24 formed in the valve body 23 may use a gap such as a moving mechanism or may form a flow path in the valve body 23.
  • the dehumidification control valve shown in FIG. 3 has the same basic configuration as the dehumidification control valve shown in FIG. 2, but the inlet 37 of the sub-refrigerant passage is provided at the upper end of the refrigerant passage 32 on the high pressure side. Have been. Therefore, when refrigerant flows into the dehumidification control valve in a gas-liquid two-phase flow, gas refrigerant 38 flows to the upper layer and liquid refrigerant 39 flows 5 to the lower layer in general except for vertical piping. As a result, a liquid refrigerant 39 flows through the sub-refrigerant passage 25, and a gas refrigerant 38 flows through the sub-refrigerant passage 25.
  • valve port 31 as an inlet of the main refrigerant passage 27 is provided at a lower end side of the high-pressure side refrigerant passage 32 facing the inlet 37 of the sub-refrigerant passage 25. It is desirable. Further, the gas-liquid separation function has a great effect when the inlet pipe 33 and at least the high-pressure side refrigerant flow path 32 are installed horizontally.
  • the sub-refrigerant passage 25 provided to be connected to the high-pressure side refrigerant passage 32 is provided with a valve body 23.
  • the clearance between the valve stem 34 and the valve stem 34 may be used. Configuration in this way Even in the same manner as described above, it can have the function of dividing the refrigerant flow and the function of separating gas and liquid.
  • the two-way valve 5 is closed and the dehumidifying expansion device 7 is opened.
  • the opening surfaces of the valve stem and the valve seat of the dehumidification control valve operating as the dehumidification expansion device 7 are opened so that pressure loss is almost eliminated.
  • the refrigerant flows from the compressor 1 to the four-way valve 2 to the outdoor heat exchanger 3 to the main expansion device 4—the indoor heat exchanger 6a—to the dehumidification expansion device.
  • the four-way valve 2 is switched as in the cooling operation, the two-way valve 5 is opened, and the dehumidifying expansion device 7 is closed.
  • the valve rod 34 of the dehumidification control valve used as the dehumidification expansion device 7 is lowered to be located in the valve seat 36, and a main refrigerant passage 27 and a sub refrigerant passage 25 are formed.
  • pressure is reduced in each case.
  • the refrigerant flows from compressor 1 ⁇ four-way valve 2 to ⁇ outdoor heat exchanger 3 ⁇ two-way valve 5 ⁇ indoor heat exchanger 6 a-dehumidifying expansion device 7 ⁇ Indoor heat exchanger 6 b-Four-way valve 2 ⁇ ⁇ Accumulator 8 ⁇ Compressor 1 Circulates in this order, and the dehumidification control valve as dehumidification expansion device 7 restricts outdoor heat exchanger 3 Upstream condenser, room heat exchanger 6a is the downstream box and the indoor heat exchanger 6b is the evaporator. Then, the indoor heat exchanger 6b cools and dehumidifies the indoor air, and also heats the air with the indoor heat exchanger 6a. It can be carried out.
  • the condensing capacity in the indoor heat exchanger 6a that is, the amount of radiated heat is changed to change the indoor fan capacity.
  • the temperature of the air blown out by the air conditioner 10 can be controlled over a wide range from a cooling tendency to a heating tendency.
  • the indoor heat exchangers 6a and 6b may be arranged in front and rear, and the wind may flow from the indoor heat exchangers 6b to 6a by the indoor fan 10 or the indoor heat exchangers 10a may be arranged vertically. Therefore, the wind may flow in parallel to the indoor heat exchangers 6a and 6b.
  • the refrigerant flow is in a gas-liquid two-phase state at the inlet of the dehumidifying expansion device 7, depending on the indoor and outdoor temperature and humidity conditions, the operating conditions of the pressure box machine fan, and the like.
  • the gas-liquid two-phase flow may be a slag flow or plug flow in which gun-shaped bubbles flow intermittently in the liquid flow.
  • the flow may be a laminar flow or a wavy flow in which the upper part is a gas phase and the lower part is a two-phase, a yes phase.
  • the auxiliary refrigerant passage is provided only in the valve stem 34.
  • This sub-refrigerant passage is composed of a horizontal hole 40 and a vertical hole 41.
  • the refrigerant flow flowing from the lateral hole 40 changes the flow direction at right angles in the valve rod 34 and flows out from the longitudinal hole 41 to the refrigerant passage 28 on the low pressure side.
  • the horizontal hole 40 in the upper part of the refrigerant passage on the low pressure side when the refrigerant flows in a gas-liquid two-phase, it can also have a gas-liquid separation function.
  • the momentum and kinetic energy serving as the exciting force due to the split flow of the refrigerant flow can be dissipated with respect to the gas-liquid two-phase refrigerant flow, as in the above-described embodiment. This has the effect of reducing flowing noise.
  • FIG. 6 is a diagram showing the configuration of the refrigeration cycle of this embodiment.
  • the dehumidification control valve shown in FIGS. 2 to 5 is replaced by an expansion valve 1 shown in FIG. 2 shows a frozen cycle when used. It is necessary to set the expansion valve 12 so as to have a throttling function during the cooling / heating operation, and it is necessary to set the expansion valve 12 so that there is almost no pressure loss during the dehumidifying operation.
  • the function of the refrigeration cycle shown in FIG. can be the same as the function.
  • the expansion valve 12 even if the refrigerant flows into the expansion valve 12 in a gaseous two-phase flow state, the expansion valve 12 The refrigerant flow noise generated in step 1 and 2 can be reduced.
  • the drive device for the valve stem of the dehumidification control valve is described as being composed of an electromagnetic coil, an attractor, and a spring.
  • a device that uses a motor and is mechanically driven A pressure control method using a temperature sensor may be applied, and a driving method of various configurations may be applied.
  • the valve may have a structure in which a valve rod moves through a valve seat ⁇ , and may have a structure in which a main refrigerant passage and a sub-refrigerant passage are provided.
  • a part of the sub-refrigerant passage is provided in the valve rod.
  • a passage (not shown) penetrating the high-pressure side refrigerant flow path and the low-pressure side refrigerant flow path may be provided in the valve body.
  • the refrigerant flow noise can be reduced.
  • the present invention is not limited to this, and can be applied to other refrigeration cycles.
  • a refrigeration cycle in which the four-way valve 2 is not provided and a cooling operation and a dehumidification operation in the cooling cycle is possible, that is, the indoor heat exchanger 6 b and the accumulator 8
  • the dehumidifying operation can be performed by applying the embodiment shown in any of FIGS. 2 to 5.
  • the refrigerant flow noise generated in the dehumidifying expansion device can be similarly reduced.
  • the refrigeration cycle without the four-way valve 2 and the dehumidification operation in the heating cycle can be performed, that is, the outdoor heat exchanger 3, the accumulator 8,
  • the box box 1 and the indoor heat exchanger 6b are connected so as to be in series (not shown)
  • one of the embodiments shown in FIGS. Refrigerant flow noise generated in the device can be reduced.
  • an accumulator is not necessarily required, and an accumulator without an accumulator may be used depending on the type of press used, the type of main squeezing device, and the control method. It can be configured as a frozen cycle.
  • the types of refrigerant flowing in the refrigeration cycle include single refrigerant such as HCFC22 currently used in air conditioners, ozone layer destruction, and the like.
  • a mixed refrigerant which is an alternative to HCFC22, can be used.
  • intermittent or continuous refrigerant flow noise is considered to be significant when the gas-liquid two-phase refrigerant flow flows into the throttle, but as described above, Applying the embodiment has the effect of reducing the flow noise of the refrigerant.
  • the present invention is not limited to this, and the present invention can be applied to a device for other uses requiring a dehumidifying operation.
  • the heat exchanger is generally not necessarily used indoors or outdoors.
  • the indoor heat exchanger is the use side heat exchanger
  • the outdoor heat exchanger is the heat source side heat exchanger
  • the indoor The fan is called the use side fan
  • the outdoor fan is called the heat source side fan.
  • the indoor heat exchanger (use-side heat exchanger) is divided into two parts, and the dehumidifying throttle device used during the dehumidifying operation is provided between the two parts.
  • the dehumidifying throttle device used during the dehumidifying operation is provided between the two parts.
  • one of the user-side heat exchangers is used as an evaporator and the other is used as a refrigerating box, and air is cooled, dehumidified and heated by a refrigeration cycle.
  • a sub-refrigerant passage that penetrates the main refrigerant passage connecting the valve port and the open port, the valve rod, and the valve body, and circulates the high-pressure refrigerant passage and the low-pressure refrigerant passage,
  • the refrigerant flow is divided into two, and the kinetic energy and momentum of each flow can be dispersed.
  • the inlet hole of the high-pressure remote refrigerant flow passage in the sub-refrigerant passage at the upper end of the flow passage it is possible to have a gas-liquid separation function, and when the refrigerant flow is a single-phase flow, Therefore, even in the case of the gas-liquid two-phase flow, the generation of the refrigerant flow noise due to the refrigerant flow passing through the dehumidification control valve can be reduced. Further, since the heating capacity by the refrigerating cycle is relatively large, it is possible to perform a quiet and comfortable dehumidifying operation for lowering the humidity without lowering the room temperature.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention vise à réduire le bruit présent dans un dispositif de restriction de déshumidification pendant une opération de déshumidification, et induit par l'écoulement d'un réfrigérant dans un conditionneur d'air capable de réaliser une opération de déshumidification et d'empêcher une baisse de la température ambiante, particulièrement au moyen d'un cycle de réfrigération. Un échangeur de chaleur côté utilisateur (3) est divisé en deux parties entre lesquelles est prévu un dispositif de restriction de déshumidification (7) utilisé au cours d'une opération de déshumidification pour former un cycle de réfrigération. On crée un dispositif de restriction de déshumidification (7) en formant un passage à réfrigérant principal (27) présentant un espace libre entre une tige de soupape (34) et un siège de soupape (36), et un passage de réfrigérant auxiliaire (25) reliant entre eux un passage à réfrigérant côté haute pression (32) et un passage à réfrigérant côté basse pression (25), une partie du passage à réfrigérant auxiliaire (25) étant formée dans une tige de soupape lorsque celle-ci est utilisée. Ainsi on peut réduire, pendant une opération de déshumidification, le bruit d'écoulement du réfrigérant qui survient lorsque le courant de réfrigérant dans une partie de restriction du dispositif de restriction de déshumidification est un courant diphasique tel qu'un courant à phases gaz/liquide.
PCT/JP1995/002039 1994-10-05 1995-10-05 Conditionneur d'air WO1996011369A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP6/241024 1994-10-05
JP24102494A JP3872824B2 (ja) 1994-10-05 1994-10-05 空気調和機

Publications (1)

Publication Number Publication Date
WO1996011369A1 true WO1996011369A1 (fr) 1996-04-18

Family

ID=17068206

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1995/002039 WO1996011369A1 (fr) 1994-10-05 1995-10-05 Conditionneur d'air

Country Status (3)

Country Link
JP (1) JP3872824B2 (fr)
CN (1) CN1082179C (fr)
WO (1) WO1996011369A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
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WO2005106354A1 (fr) * 2004-04-22 2005-11-10 Ice Energy, Inc Regulateur a phases mixtes pour gerer un caloporteur dans un systeme de refroidissement et de stockage d'energie hautement efficace s'appuyant sur un refrigerant
US20230272868A1 (en) * 2020-08-04 2023-08-31 Eagle Industry Co., Ltd. Valve

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JP3817981B2 (ja) * 1999-08-06 2006-09-06 三菱電機株式会社 冷凍サイクル装置および空気調和装置
JP2008151351A (ja) * 2006-12-14 2008-07-03 Matsushita Electric Ind Co Ltd 空気調和機
CN105115181B (zh) * 2015-07-21 2018-06-26 上海海立电器有限公司 一种空调系统
CN106885387A (zh) * 2015-12-16 2017-06-23 上海日立电器有限公司 一种空调系统
CN106885403B (zh) * 2015-12-16 2018-11-02 上海海立电器有限公司 显热潜热分离控制的空调系统
CN106885402B (zh) * 2015-12-16 2019-01-29 上海海立电器有限公司 显热潜热分离控制的空调系统
CN106885388B (zh) * 2015-12-16 2018-07-27 上海海立电器有限公司 一种空调系统
CN112648761A (zh) * 2020-12-21 2021-04-13 上海交通大学 基于记忆合金的节流控制元件

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JPH01152176U (fr) * 1988-04-12 1989-10-20
JPH04113864U (ja) * 1991-03-25 1992-10-06 株式会社鷺宮製作所 オリフイス内蔵電磁弁
JPH05164432A (ja) * 1991-12-17 1993-06-29 Hitachi Ltd 膨張弁

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
JPH01152176U (fr) * 1988-04-12 1989-10-20
JPH04113864U (ja) * 1991-03-25 1992-10-06 株式会社鷺宮製作所 オリフイス内蔵電磁弁
JPH05164432A (ja) * 1991-12-17 1993-06-29 Hitachi Ltd 膨張弁

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005106354A1 (fr) * 2004-04-22 2005-11-10 Ice Energy, Inc Regulateur a phases mixtes pour gerer un caloporteur dans un systeme de refroidissement et de stockage d'energie hautement efficace s'appuyant sur un refrigerant
JP2007534914A (ja) * 2004-04-22 2007-11-29 アイス エナジー インコーポレーテッド 高性能冷媒式蓄熱冷却システムにおける冷却剤管理のための混合相調節器
US7690212B2 (en) 2004-04-22 2010-04-06 Ice Energy, Inc. Mixed-phase regulator for managing coolant in a refrigerant based high efficiency energy storage and cooling system
JP2011208939A (ja) * 2004-04-22 2011-10-20 Ice Energy Inc 冷媒の圧力および流量を制御する方法
JP4864876B2 (ja) * 2004-04-22 2012-02-01 アイス エナジー インコーポレーテッド 冷媒の圧力および流量を調節するための閉鎖システムならびに冷媒の圧力および流量を制御する方法
US8109107B2 (en) 2004-04-22 2012-02-07 Ice Energy, Inc. Mixed-phase regulator
US20230272868A1 (en) * 2020-08-04 2023-08-31 Eagle Industry Co., Ltd. Valve

Also Published As

Publication number Publication date
JP3872824B2 (ja) 2007-01-24
CN1082179C (zh) 2002-04-03
JPH08105672A (ja) 1996-04-23
CN1136350A (zh) 1996-11-20

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