WO2010106771A1 - 空調機 - Google Patents
空調機 Download PDFInfo
- Publication number
- WO2010106771A1 WO2010106771A1 PCT/JP2010/001812 JP2010001812W WO2010106771A1 WO 2010106771 A1 WO2010106771 A1 WO 2010106771A1 JP 2010001812 W JP2010001812 W JP 2010001812W WO 2010106771 A1 WO2010106771 A1 WO 2010106771A1
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- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- valve
- radiant heat
- refrigerant
- air conditioner
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0089—Systems using radiation from walls or panels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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- 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
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- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- 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
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
- F25B2313/02334—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during heating
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- 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
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- 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
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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- 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
- F25B2500/08—Exceeding a certain temperature value in a refrigeration component or cycle
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- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2515—Flow valves
Definitions
- the present invention relates to an air conditioner including a refrigerant circuit that performs a vapor compression refrigeration cycle.
- Patent Document 1 Japanese Patent Laid-Open No. 7-55234
- a valve for adjusting the inflow of high-pressure refrigerant to the radiant heat exchanger during heating operation is disposed on the downstream side of the radiant heat exchanger. When the exchanger temperature reaches an upper limit, the valve closes the flow path to prevent high pressure refrigerant from flowing into the radiant heat exchanger.
- the high pressure refrigerant is pushed into the radiant heat exchanger by the pressure of the compressor, and the refrigerant, compressor oil, and the like stay in the radiant heat exchanger. For this reason, it is difficult for the refrigerant temperature to decrease, and a state occurs in which the refrigerant temperature does not decrease when the temperature of the radiant heat exchanger is desired to decrease. Further, since the return of oil to the compressor is reduced, there is a high possibility that the reliability of the compressor is impaired. Therefore, the applicant provided an on-off valve for blocking the flow path of the high-pressure refrigerant toward the radiant heat exchanger on the upstream side of the radiant heat exchanger to prevent the high-pressure refrigerant from being pushed into the radiant heat exchanger.
- An object of the present invention is to provide an air conditioner in which chattering does not occur in an on-off valve even when refrigerant liquefied by a radiant heat exchanger accumulates in the vicinity of the radiant heat exchanger and the on-off valve during heating operation.
- An air conditioner is an air conditioner that includes a refrigerant circuit that performs a vapor compression refrigeration cycle and performs a heating operation using at least a high-pressure refrigerant, and the refrigerant circuit includes a convection heat exchanger and a radiant heat exchange. And a check valve.
- the convection heat exchanger exchanges heat between the high-pressure refrigerant flowing inside and the air convection outside.
- a radiant heat exchanger heats a predetermined member to the high-pressure refrigerant circulating inside, and generates radiant heat from the predetermined member.
- the on-off valve is provided on the upstream side of the radiant heat exchanger during heating operation, and blocks the high-pressure refrigerant flow path toward the radiant heat exchanger.
- the check valve is provided between the radiant heat exchanger and the on-off valve.
- this air conditioner there is a check valve between the radiant heat exchanger and the on-off valve, and when the on-off valve is closed, there is little liquid refrigerant present between the on-off valve and the check valve. Even when the refrigerant spontaneously evaporates and the internal pressure rises, the pressure does not reach a level that pushes the open / close valve open, so chattering is prevented.
- An air conditioner according to a second aspect of the present invention is the air conditioner according to the first aspect of the present invention, wherein the on-off valve is an opening adjustment valve having a function of blocking the flow passage and a function of adjusting the opening of the flow passage.
- the capacity of the radiant heat exchanger is increased or decreased by adjusting the opening of the refrigerant flow path, and when the capacity of the radiant heat exchanger reaches the set value, the flow path of the refrigerant is blocked. High nature.
- An air conditioner according to a third aspect is the air conditioner according to the first aspect or the second aspect, wherein the on-off valve blocks the flow passage when the temperature of the predetermined member reaches the upper limit of the allowable temperature.
- the high-pressure refrigerant does not flow to the radiant heat exchanger.
- the temperature drop of the refrigerant in the inside is accelerated.
- the air conditioner can return to the heating operation using the radiant heat exchanger again.
- the air conditioner according to the first aspect of the invention there is little liquid refrigerant present between the radiant heat exchanger and the check valve, and even if the liquid refrigerant spontaneously evaporates and the internal pressure rises, the open / close valve is opened. Therefore, chattering is prevented from occurring.
- the capacity of the radiant heat exchanger is increased or decreased by adjusting the opening degree of the refrigerant flow path, and when the capacity of the radiant heat exchanger reaches a set value, the refrigerant flow path is blocked. Convenience and safety are high.
- the air conditioner according to the third invention when the temperature of the predetermined member of the radiant heat exchanger reaches the upper limit of the allowable temperature during the heating operation using the radiant heat exchanger, the high-pressure refrigerant does not flow to the radiant heat exchanger.
- the temperature drop of the refrigerant in the radiant heat exchanger is accelerated.
- the air conditioner can return to the heating operation using the radiant heat exchanger again.
- the refrigerant circuit diagram of the air conditioner which concerns on one Embodiment of this invention.
- the disassembled perspective view which shows the internal structure of an indoor unit.
- the side view of a heat exchanger assembly Sectional drawing which shows the attachment structure of the panel of a radiant heat exchanger, and a heat exchanger tube.
- the graph which shows the relationship between the detection temperature of the 2nd temperature sensor in heating operation, and operation
- Sectional drawing of a radiant heat exchanger which shows the 2nd attachment structure of a panel and a heat exchanger tube.
- Sectional drawing of a radiant heat exchanger which shows the 3rd attachment structure of a panel and a heat exchanger tube.
- Sectional drawing of a radiant heat exchanger which shows the 4th attachment structure of a panel and a heat exchanger tube.
- Sectional drawing of a radiant heat exchanger which shows the 5th attachment structure of a panel and a heat exchanger tube Sectional drawing of a radiant heat exchanger which shows the 6th attachment structure of a panel and a heat exchanger tube.
- FIG. 1 is a refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
- an air conditioner 1 includes a refrigerant circuit 10 that performs a vapor compression refrigeration cycle in which an indoor unit 2 that is mainly disposed indoors and an outdoor unit 3 that is primarily disposed outdoor are connected by a refrigerant communication pipe. Is formed.
- a compressor 11, a four-way switching valve 12, a convection heat exchanger 13, an expansion valve 15, and an outdoor heat exchanger 16 are connected in order. Further, a branch pipe 40 is provided in parallel with the convection heat exchanger 13. The branch pipe 40 is connected in series with an on-off valve 41, a first check valve 42, a radiant heat exchanger 14, and a second check valve 43 in order from the side closer to the compressor 11. An accumulator 20 is connected between the four-way switching valve 12 and the suction port of the compressor 11.
- the four-way switching valve 12 allows the refrigerant that has come out of the compressor 11 to flow to either the convection heat exchanger 13 side or the outdoor heat exchanger 16 side.
- the control unit causes the four-way switching valve 12 to select the flow path indicated by the solid line in FIG. 1 and causes the refrigerant to flow to the convective heat exchanger 13 side.
- the control unit causes the four-way switching valve 12 to select the flow path indicated by the dotted line in FIG. 1 and causes the refrigerant to flow to the outdoor heat exchanger 16 side.
- the convection heat exchanger 13 is a heat exchanger including a plurality of fins and a plurality of heat transfer tubes orthogonal to the fins, and heat is generated between the refrigerant circulating in the heat transfer tubes and the air convection on the fin surface. Let the exchange take place. In the vicinity of the convective heat exchanger 13, a fan 23 for blowing air to the fin surface is disposed.
- the radiant heat exchanger 14 is a heat exchanger composed of an aluminum plate (hereinafter referred to as a panel) and a heat transfer tube fixed to the panel, and the panel is heated by a high-pressure refrigerant circulating in the heat transfer tube. Generate radiant heat from
- the expansion valve 15 is an electric expansion valve as a decompression mechanism, and is connected between the convection heat exchanger 13 and the outdoor heat exchanger 16 and depressurizes the refrigerant by narrowing the refrigerant flow path.
- the outdoor heat exchanger 16 is a heat exchanger including a plurality of fins and a plurality of heat transfer tubes orthogonal to the fins, and heat is generated between the refrigerant circulating in the heat transfer tubes and the air convection on the fin surface. Let the exchange take place. In the vicinity of the outdoor heat exchanger 16, an outdoor fan 33 for blowing air to the fin surface is disposed.
- the accumulator 20 accumulates excess liquid refrigerant and returns only the gas refrigerant to the compressor 11.
- a discharge temperature sensor 111 is attached to a discharge pipe connecting the discharge port of the compressor 11 and the four-way switching valve 12.
- the discharge temperature sensor 111 detects the temperature of the high-pressure refrigerant discharged from the compressor 11.
- the control unit controls the temperature of the panel of the radiant heat exchanger 14 based on the temperature detected by the discharge temperature sensor 111.
- Another temperature sensor hereinafter referred to as second temperature sensor 114.
- second temperature sensor 114 is attached. In the present embodiment, both the discharge temperature sensor 111 and the second temperature sensor 114 are employed.
- FIG. 2 is an exploded perspective view showing the internal structure of the indoor unit.
- the indoor unit 2 has an outer shell formed by a frame 210 and a grill 240.
- a left plate 212 is fixed to the left end of the rectangular opening 211
- a right plate 213 is fixed to the right end
- an upper plate 214 is fixed to the upper end.
- the frame 210 has a fan chamber 210a and an electrical component chamber 210b.
- the grill 240 has an upper outlet 240a, a lower outlet 240b, an opening 240c, a left inlet 240d, and a right inlet 240e.
- the upper air outlet 240 a is located at the upper part of the grill 240, and the lower air outlet 240 b is located at the lower part of the grill 240.
- the opening 240c exposes the panel 14a to the indoor space.
- the left suction port 240 d is located on the left side surface of the grill 240, and the right suction port 240 e is located on the right side surface of the grill 240.
- the air is sucked in from the left suction port 240d and the right suction port 240e by the operation of the fan 23, passes between the heat-insulated back surface of the panel 14a and the suction passage forming plates 115 and 116, and is arranged upstream of the convection heat exchanger 13. Pass through the filtered filter 218. The air that has passed through the filter 218 is guided to the convection heat exchanger 13, exchanges heat with the convection heat exchanger 13, passes through the circular hole 216 a of the bell mouth 216, and enters the fan 23.
- the air blown out from the fan 23 proceeds into the fan chamber 210a toward the upper blower outlet 240a and the lower blower outlet 240b, and is blown out from the upper blower outlet 240a and the lower blower outlet 240b.
- the circular hole 216 a of the bell mouth 216 is slightly smaller than the inner diameter of the fan 23, and the air that has passed through the circular hole 216 a enters the inside of the fan 23, is pressurized by the vane, and is blown out toward the outer periphery of the fan 23. .
- the motor support plate 215 is fixed between the upper part and the lower part of the fan chamber 210 a and supports the drive motor 23 a of the fan 23.
- the drive motor 23a is screwed to the motor support plate 215 by screws 23b.
- the bell mouth 216 closes the fan chamber 210a.
- the electrical component box 24 is held in the electrical component chamber 210b.
- the heat exchanger assembly 220 has a structure in which the convective heat exchanger 13 and the radiant heat exchanger 14 are combined.
- a drain pan assembly 217 is disposed below the convection heat exchanger 13. For example, when air passes through the convection heat exchanger 13 during cooling operation, moisture contained in the air is condensed on the surface of the convection heat exchanger 13. The drain pan assembly 217 receives condensed water falling from the convection heat exchanger 13.
- a blower outlet assembly 250 is attached to the upper blower outlet 240a.
- the blower outlet assembly 250 has a louver that changes the blowing direction of air.
- a left frame 241, a right frame 242, and an upper frame 243 are attached to the left end, the right end, and the upper end of the opening 240c of the grill 240, respectively.
- FIG. 3 is a side view of the heat exchanger assembly.
- the convection heat exchanger 13 and the radiant heat exchanger 14 are fixed by a mounting plate 221.
- the mounting plate 221 is a sheet metal member that extends in a direction opposite to the panel 14a from the frame 14c of the radiant heat exchanger 14, and has a through hole 221a.
- the convective heat exchanger 13 has tube plates 13c in the vicinity of both ends of each heat transfer tube 13b. A screw hole corresponding to the through hole 221a of the mounting plate 221 is formed in the tube plate 13c. The convective heat exchanger 13 and the mounting plate 221 are screwed through the through hole 221a.
- FIG. 4 is a cross-sectional view showing a mounting structure between a panel of a radiant heat exchanger and a heat transfer tube.
- the mounting bracket 14e faces the panel 14a with the heat transfer tube 14b interposed therebetween, and is screwed to the mounting portion 14d fixed to the panel 14a in advance by mounting screws 14f.
- the attachment portion 14d has a screw hole 14da into which the attachment screw 14f is screwed.
- the mounting bracket 14e has a flat plate portion 14ea, a raised portion 14eb, and a flange portion 14ec.
- the flat plate portion 14ea is in close contact with the rear surface of the radiation surface of the panel 14a.
- the raised portion 14eb is raised from the flat plate portion 14ea, and a U-shaped groove into which the heat transfer tube 14b is fitted is formed.
- the flange portion 14ec rises from the end of the flat plate portion 14ea and is fixed to the attachment portion 14d.
- a through hole 14ed corresponding to the screw hole 14da of the mounting portion 14d is formed in the flange portion 14ec.
- the air conditioner 1 changes the refrigerant flow path with the four-way switching valve 12 to switch between the cooling operation and the heating operation.
- the refrigerant circuit is a circuit for heating operation.
- Heating operation the flow path indicated by the solid line in FIG. 1 is selected in the four-way switching valve 12, and the high-pressure gas refrigerant discharged from the compressor 11 flows separately to the branch pipe 40 and the convection heat exchanger 13.
- the branch point is called A point.
- the gas refrigerant that has entered the branch pipe 40 from the point A flows in the order of the on-off valve 41, the first check valve 42, the radiant heat exchanger 14 and the second check valve 43, and flows from the convective heat exchanger 13 side. To join.
- the junction is called point B. Since the mounting bracket 14e and the heat transfer tube 14b are in close contact with the panel 14a (see FIG. 4), the heat of the gas refrigerant is conducted to the panel 14a through the heat transfer tube 14b, and the temperature of the panel 14a rises. Since the radiant heat is emitted from the panel 14a whose temperature has increased, the air and objects in front of the panel 14a are warmed. In the radiant heat exchanger 14, a part of the gas refrigerant is condensed by heat exchange with the panel 14a, and the liquid refrigerant and the gas refrigerant are mixed.
- the gas refrigerant that has entered the convection heat exchanger 13 from the point A is condensed by exchanging heat with the convection air outside the convection heat exchanger 13.
- the air whose temperature has increased in the convection heat exchanger 13 is blown out into the room and warms the room.
- the liquid refrigerant that has exited the convection heat exchanger 13 joins with the refrigerant that has exited the radiant heat exchanger 14 at point B, and is directed to the outdoor heat exchanger 16, and is decompressed by the expansion valve 15 and enters the outdoor heat exchanger 16. .
- the refrigerant exchanges heat with air convection outside the outdoor heat exchanger 16 and evaporates to become a gas refrigerant.
- FIG. 5 is a graph showing the relationship between the temperature detected by the second temperature sensor and the operation of the on-off valve in the heating operation.
- the on-off valve 41 switches the flow path from open to closed. That is, the on-off valve 41 switches from a state in which the refrigerant flows to the radiant heat exchanger 14 to a state in which the refrigerant flows only to the convective heat exchanger 13 without flowing to the radiant heat exchanger 14.
- the on-off valve 41 switches the flow path from closed to open again, whereby the heating operation by the radiant heat exchanger 14 is restored. While the heating operation using only the convection heat exchanger 13 is performed, the liquid refrigerant and the gas refrigerant remain between the on-off valve 41 and the point B. In this state, when the liquid refrigerant spontaneously evaporates, the internal pressure between the on-off valve 41 and the point B increases. However, in the present embodiment, since the first check valve 42 is provided between the radiant heat exchanger 14 and the on-off valve 41, even if the liquid refrigerant spontaneously evaporates and the internal pressure rises, the radiant heat exchanger 14 The internal pressure does not reach the on-off valve 41.
- the liquid refrigerant from the outdoor heat exchanger 16 is depressurized by the expansion valve 15 and enters the convection heat exchanger 13 on the way to the convection heat exchanger 13. Note that the liquid gas refrigerant tends to flow to the branch pipe 40 at the point B before entering the convection heat exchanger 13, but is blocked by the second check valve 43.
- the liquid refrigerant that has entered the convection heat exchanger 13 exchanges heat with convection air outside the convection heat exchanger 13 and evaporates to become a gas refrigerant.
- the air whose temperature has decreased in the convection heat exchanger 13 is blown out into the room and cools the room.
- the gas refrigerant discharged from the convection heat exchanger 13 passes through the point A, goes to the four-way switching valve 12, passes through the four-way switching valve 12, and the accumulator 20, and returns to the compressor 11.
- the on-off valve 41 is employed to open and close the branch pipe 40.
- the function of blocking the flow path of the branch pipe 40 and the opening degree of the flow path of the branch pipe 40 are used.
- An opening adjustment valve having a function of adjusting the angle may be employed.
- FIG. 6 is a cross-sectional view of a radiant heat exchanger showing a second mounting structure between the panel and the heat transfer tube.
- the mounting panel 141 has a flat plate portion 141a joined to the back surface of the panel 14a, and a raised portion 141b raised from the flat plate portion 141a.
- the raised portion 141b is raised higher than the diameter of the heat transfer tube 14b, and a U-shaped groove 141c into which the heat transfer tube 14b is fitted is formed. After the heat transfer tube 14b is fitted into the U-shaped groove 141c, crimping is performed so that the open end of the U-shaped groove 141c presses the outer peripheral surface of the heat transfer tube 14b.
- FIG. 7 is a cross-sectional view of the radiant heat exchanger showing a third mounting structure of the panel and the heat transfer tube.
- the panel 14a and the heat transfer tube 14b are joined by brazing. Since the solder 140 spreads around the corner formed at the contact portion between the panel 14a and the heat transfer tube 14b, the thermal conductivity from the heat transfer tube 14b to the panel 14a is high.
- FIG. 8 is a cross-sectional view of the radiant heat exchanger showing a fourth mounting structure of the panel and the heat transfer tube.
- the first mounting bracket 341 has a flat plate portion 341a joined to the back surface of the panel 14a and a raised portion 341b raised from the flat plate portion 341a.
- the flat plate portion 341a is joined so as to be in close contact with the back surface of the panel 14a by spot welding or brazing welding.
- the raised portion 341b is raised to a diameter of the heat transfer tube 14b, and a U-shaped groove 341c into which the heat transfer tube 14b is fitted is formed. Further, screw holes 341d are formed on both sides of the U-shaped groove 341c.
- the second mounting bracket 342 has a through hole 342 a corresponding to the screw hole 341 d of the first mounting bracket 341.
- the second mounting bracket 342 is screwed to the first mounting bracket 341 with a screw 343 so as to cover the heat transfer tube 14b fitted in the U-shaped groove 341c. Since the heat transfer tube 14b slightly protrudes from the U-shaped groove 341c, when the second mounting bracket 342 is screwed to the first mounting bracket 341, the heat transfer tube 14b is compressed and closely contacts the U-shaped groove 341c.
- FIG. 9 is a cross-sectional view of the radiant heat exchanger showing a fifth mounting structure of the panel and the heat transfer tube. In FIG.
- the presser fitting 441 has a flat plate portion 441a joined to the back surface of the panel 14a and a U-shaped groove 441b that sandwiches the heat transfer tube 14b by the back surface of the panel 14a. After the heat transfer tube 14b is disposed on the back surface of the panel 14a, the U-shaped groove 441b of the presser fitting 441 covers the heat transfer tube 14b. In this state, the flat plate portion 441a and the back surface of the panel 14a are joined by spot welding or brazing welding.
- FIG. 10 is a cross-sectional view of a radiant heat exchanger showing a sixth mounting structure of the panel and the heat transfer tube.
- the panel 14a has a raised portion 541 at a portion corresponding to the arrangement position of the heat transfer tube 14b on the back surface.
- the raised portion 541 is formed with a U-shaped groove 541 a into which the heat transfer tube 14 b is fitted.
- the U-shaped groove 541a has such a depth that the outer peripheral surface of the heat transfer tube 14b slightly protrudes when the heat transfer tube 14b is fitted.
- Screw holes 541b are formed on both sides of the U-shaped groove 541a.
- the presser fitting 542 has a through hole 542 a corresponding to the screw hole 541 b of the raised portion 541.
- the presser fitting 542 is screwed to the raised portion 541 with a screw 543 so as to cover the outer peripheral surface of the heat transfer tube 14 b slightly protruding from the raised portion 541.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical & Material Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
Description
そこで、出願人は、輻射熱交換器の上流側に、輻射熱交換器に向う高圧冷媒の流通路を遮断する開閉弁を設けて、高圧冷媒が輻射熱交換器に押し込まれることを防止した。但し、それだけでは、暖房運転中、輻射熱交換器で液化した冷媒が輻射熱交換器および開閉弁近傍に溜まるので、この状態で液冷媒が自然蒸発して内部圧力が上昇した場合、開閉弁が圧力に押されて開と閉を繰り返す現象、いわゆるチャタリングが発生する。
この空調機では、輻射熱交換器と開閉弁との間に逆止弁があり、開閉弁が閉じられているとき、開閉弁と逆止弁との間に存在する液冷媒は少なく、仮に、液冷媒が自然蒸発して内部圧力が上昇した場合でも、開閉弁を押し開けるほどの圧力に至らないので、チャタリングの発生は防止される。
この空調機では、輻射熱交換器の能力は冷媒の流通路の開度調整で増減され、輻射熱交換器の能力が設定値に達したとき、冷媒の流通路が遮断されるので、利便性および安全性が高い。
この空調機では、輻射熱交換器を用いた暖房運転を実行中に、輻射熱交換器の所定部材の温度が許容温度の上限に達したとき、高圧冷媒が輻射熱交換器に流れなくなるので、輻射熱交換器内の冷媒の温度低下が速まる。その結果、所定部材の温度低下が速まり、空調機は、再び輻射熱交換器を用いた暖房運転に復帰することができる。
第2発明に係る空調機では、輻射熱交換器の能力は冷媒の流通路の開度調整で増減され、輻射熱交換器の能力が設定値に達したとき、冷媒の流通路が遮断されるので、利便性および安全性が高い。
第3発明に係る空調機では、輻射熱交換器を用いた暖房運転を実行中に、輻射熱交換器の所定部材の温度が許容温度の上限に達したとき、高圧冷媒が輻射熱交換器に流れなくなるので、輻射熱交換器内の冷媒の温度低下が速まる。その結果、所定部材の温度低下が速まり、空調機は、再び輻射熱交換器を用いた暖房運転に復帰することができる。
<空調機1の冷媒回路10>
図1は、本発明の一実施形態に係る空調機の冷媒回路図である。図1において、空調機1は、主に室内に配置される室内ユニット2と、主に室外に配置される室外ユニット3とが冷媒連絡配管によって接続され、蒸気圧縮式冷凍サイクルを行う冷媒回路10が形成されている。
冷媒回路10では、圧縮機11、四路切換弁12、対流熱交換器13、膨張弁15、室外熱交換器16が順に接続されている。さらに、対流熱交換器13と並列に分岐管40が設けられている。分岐管40には、圧縮機11に近い側から順に、開閉弁41、第1逆止弁42、輻射熱交換器14及び第2逆止弁43が直列に接続されている。また、アキュームレータ20が四路切換弁12と圧縮機11の吸入口との間に接続されている。
対流熱交換器13は、複数のフィンと、それらフィンと直交する複数の伝熱管とからなる熱交換器であり、伝熱管内を流通する冷媒とフィン表面上を対流する空気との間で熱交換を行わせる。対流熱交換器13の近傍には、フィン表面に送風するファン23が配置されている。
輻射熱交換器14は、アルミ製の板(以下、パネルという)とそのパネルに固定される伝熱管とからなる熱交換器であり、伝熱管内を流通する高圧冷媒にパネルを加熱させてそのパネルから輻射熱を発生させる。
圧縮機11の吐出口と四路切換弁12とを接続する吐出管には、吐出温度センサ111が取り付けられている。吐出温度センサ111は、圧縮機11から吐出される高圧冷媒の温度を検知する。
制御部は、輻射熱交換器14のパネルの温度を、吐出温度センサ111が検出する温度に基づいて制御する。しかし、開閉弁41と輻射熱交換器14とを接続する配管が長く、圧力損失によって吐出温度センサ111が検出する温度とパネルの温度とが異なる場合は、輻射熱交換器14の高圧冷媒入口の近傍に他の温度センサ(以下、第2温度センサ114という)が取り付けられる。本実施形態では、吐出温度センサ111および第2温度センサ114の両方が採用されている。
図2は、室内ユニットの内部構造を示す分解斜視図である。図2において、室内ユニット2は、フレーム210とグリル240とによって外殻が形成されている。フレーム210は、四角形の開口部211の左端に左板212、右端に右板213、上端に上板214が固定される。フレーム210は、ファン室210aと電装品室210bとを有している。
グリル240は、上吹出口240a、下吹出口240b、開口部240c、左側吸込口240d、および右側吸込口240eを有している。上吹出口240aはグリル240の上部に位置し、下吹出口240bはグリル240の下部に位置する。開口部240cは、パネル14aを室内空間に露出させる。左側吸込口240dはグリル240の左側面に位置し、右側吸込口240eはグリル240の右側面に位置する。
ベルマウス216の円穴216aは、ファン23の羽根内径より少し小さめで、円穴216aを通過した空気はファン23の羽根の内側に入り、羽根で昇圧されてファン23の外周方向に吹き出される。
熱交換器組立体220は、対流熱交換器13と輻射熱交換器14とが合体した構造である。対流熱交換器13の下方には、ドレンパン組立体217が配置されている。例えば、冷房運転時に、空気が対流熱交換器13を通過するとき、空気中に含まれる水分が対流熱交換器13表面で結露する。ドレンパン組立体217は、対流熱交換器13から落下してくる結露水を受ける。
図3は、熱交換器組立体の側面図である。図3において、熱交換器組立体220では、対流熱交換器13と輻射熱交換器14とが取付板221によって固定されている。取付板221は、輻射熱交換器14の枠14cからパネル14aと反対の方向に延びる板金部材であり、貫通穴221aが形成されている。
対流熱交換器13は、各伝熱管13bの両端近傍に管板13cを有している。管板13cには、取付板221の貫通穴221aに対応するネジ穴が形成されている。対流熱交換器13と取付板221とは、貫通穴221aを介してネジ止めされる。
伝熱管14bがパネル14aの裏面に配置されたのち、取付金具14eの貫通穴14edが取付部14dのネジ穴14daに対向するように配置され、取付ネジ14fによってフランジ部14ecが取付部14dにネジ止めされる。その結果、取付金具14eと伝熱管14bとはパネル14aに押付けられ、取付金具14eと伝熱管14bとからパネル14aへの伝熱性が確保される。
空調機1は、四路切換弁12で冷媒の流路を変更し、冷房運転と暖房運転とを切り替える。先ず、冷媒回路が暖房運転用の回路になっている場合について説明する。
(暖房運転)
暖房運転時、四路切換弁12では図1の実線で示す流路が選択され、圧縮機11から吐出された高圧のガス冷媒が分岐管40及び対流熱交換器13へ分かれて流れる。その分岐点をA点とよぶ。A点から分岐管40に入ったガス冷媒は、開閉弁41、第1逆止弁42、輻射熱交換器14および第2逆止弁43の順に流れ、対流熱交換器13側から流れてくる冷媒と合流する。その合流点をB点とよぶ。
取付金具14eと伝熱管14bとはパネル14aに密着しているので(図4参照)、ガス冷媒の熱が伝熱管14bを介してパネル14aに伝導し、パネル14aの温度が上昇する。温度上昇したパネル14aからは輻射熱が発せられるので、パネル14a前方の空気や物体が暖められる。輻射熱交換器14では、ガス冷媒はパネル14aとの熱交換によって一部が凝縮し、液冷媒とガス冷媒が混合した状態となる。
対流熱交換器13を出た液冷媒は、B点で輻射熱交換器14を出た冷媒と合流し室外熱交換器16に向い、途中、膨張弁15で減圧されて室外熱交換器16に入る。冷媒は、室外熱交換器16の外側を対流する空気と熱交換して蒸発しガス冷媒となる。
室外熱交換器16を出たガス冷媒は、四路切換弁12、アキュームレータ20を通って圧縮機11に戻る。以上のように、空調機1では、輻射熱交換器14と対流熱交換器13とによる暖房運転が行われる。
図5は、暖房運転における第2温度センサの検出温度と開閉弁の動作との関係を示すグラフである。図5において、第2温度センサ114の検出温度が所定温度(この場合は70℃)を超えた時点で、開閉弁41は、流路を開から閉に切り換える。つまり、開閉弁41は、輻射熱交換器14に冷媒が流れている状態から、冷媒が輻射熱交換器14に流れず対流熱交換器13のみに流れる状態に切り換える。
対流熱交換器13だけによる暖房運転が行われている間、開閉弁41とB点との間に液冷媒とガス冷媒が滞留したままとなる。その状態で、液冷媒が自然蒸発した場合、開閉弁41とB点との間の内部圧力が上昇する。しかし、本実施形態では、輻射熱交換器14と開閉弁41との間に第1逆止弁42があるので、仮に、液冷媒が自然蒸発して内部圧力が上昇した場合でも、輻射熱交換器14内の圧力は開閉弁41には及ばない。また、開閉弁41と第1逆止弁42との間に存在する液冷媒が少ないので、それが自然蒸発して内部圧力が上昇した場合でも、開閉弁41を押し開けるほどの圧力に至らず、チャタリングの発生は防止される。
(冷房運転)
次に、冷媒回路が冷房運転用の回路になった場合について説明する。冷房運転時、四路切換弁12では図1の点線で示す流路が選択され、圧縮機11から吐出された高圧のガス冷媒が室外熱交換器16に向う。ガス冷媒は、室外熱交換器16の外側を対流する空気と熱交換して凝縮する。室外熱交換器16から出た液冷媒は、対流熱交換器13へ向う途中、膨張弁15で減圧され対流熱交換器13に入る。なお、液ガス冷媒は対流熱交換器13に入る前にB点で分岐管40へ流れようとするが、第2逆止弁43に阻まれる。
<特徴>
以上のように、空調機1では、輻射熱交換器14を用いた暖房運転を実行中に、輻射熱交換器14のパネル14aの温度が許容温度の上限に達したとき、開閉弁41が分岐管40を閉じて高圧冷媒は輻射熱交換器14に流れなくなる。その結果、輻射熱交換器14内の冷媒の温度低下が速まり、パネル14aの温度低下が速まるので、空調機1は、再び輻射熱交換器14を用いた暖房運転に復帰することができる。
<変形例>
上記実施形態では、分岐管40を開閉するために開閉弁41が採用されているが、開閉弁41に替えて、分岐管40の流通路を遮断する機能と分岐管40の流通路の開度を調整する機能とを有する開度調整弁が採用されてもよい。
なぜなら、輻射熱交換器14のパネル14aの温度が流通路の開度調整で増減され、パネル14aの温度が上限値に達したとき冷媒の流通路が遮断されるので、利便性および安全性が高くなる。
輻射熱交換器14のパネル14aと伝熱管14bとの取付構造は、図4に示す形態に限定されるものではない。以下、図6から図10を用いて他の取付構造について説明する。なお、説明の便宜上、パネル14aの輻射面と反対側の面を裏面という。
図6は、パネルと伝熱管との第2の取付構造を示す輻射熱交換器の断面図である。図6において、取付パネル141は、パネル14aの裏面に接合される平板部141aと、平板部141aから***する***部141bとを有している。***部141bは、伝熱管14bの直径より高く***し、伝熱管14bが嵌まり込むU字溝141cが形成されている。伝熱管14bがU字溝141cに嵌め込まれた後、U字溝141cの開口端が伝熱管14bの外周面を押えるようにカシメ加工される。
図8は、パネルと伝熱管との第4の取付構造を示す輻射熱交換器の断面図である。図8において、第1取付金具341は、パネル14aの裏面に接合される平板部341aと、平板部341aから***する***部341bとを有している。平板部341aは、スポット溶接あるいはロウ付け溶接によってパネル14aの裏面に密着するように接合される。***部341bは、伝熱管14bの直径寸法程度に***し、伝熱管14bが嵌まり込むU字溝341cが形成されている。また、U字溝341cの両側にネジ穴341dが形成されている。
図9は、パネルと伝熱管との第5の取付構造を示す輻射熱交換器の断面図である。図9において、押え金具441は、パネル14aの裏面に接合される平板部441aと、パネル14aの裏面とによって伝熱管14bを挟み込むU字溝441bとを有している。伝熱管14bがパネル14aの裏面に配置された後、押え金具441のU字溝441bが伝熱管14bを覆う。その状態で、平板部441aとパネル14aの裏面とがスポット溶接、或はロウ付け溶接によって接合される。
押え金具542は、***部541のネジ穴541bに対応する貫通穴542aを有している。押え金具542は、***部541から僅かに突出した伝熱管14bの外周面を覆うように、ネジ543によって***部541にネジ止めされる。
10 冷媒回路
13 対流熱交換器
14 輻射熱交換器
41 開閉弁
42 第1逆止弁
Claims (3)
- 蒸気圧縮式冷凍サイクルを行う冷媒回路(10)を備え、少なくとも高圧冷媒を利用して暖房運転を行う空調機であって、
前記冷媒回路(10)が、
内側を流通する前記高圧冷媒と外側を対流する空気との間で熱交換を行わせる対流熱交換器(13)と、
内側を流通する前記高圧冷媒に所定部材を加熱させて前記所定部材から輻射熱を発生させる輻射熱交換器(14)と、
前記暖房運転時の前記輻射熱交換器(14)の上流側に設けられ、前記輻射熱交換器(14)に向う前記高圧冷媒の流通路を遮断する開閉弁(41)と、
前記輻射熱交換器(14)と前記開閉弁(41)との間に設けられる逆止弁(42)と、
を有している、
空調機(1)。 - 前記開閉弁(41)は、前記流通路を遮断する機能と前記流通路の開度を調整する機能とを有する開度調整弁である、
請求項1に記載の空調機(1)。 - 前記開閉弁(41)は、前記所定部材の温度が許容温度の上限に達したとき前記流通路を遮断する、
請求項1又は請求項2に記載の空調機(1)。
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US13/256,034 US20120000224A1 (en) | 2009-03-18 | 2010-03-15 | Air conditioner |
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EP (1) | EP2410250A1 (ja) |
JP (1) | JP5229031B2 (ja) |
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CN103154621B (zh) * | 2010-10-08 | 2016-02-24 | 大金工业株式会社 | 空调机 |
CN103154621A (zh) * | 2010-10-08 | 2013-06-12 | 大金工业株式会社 | 空调机 |
EP2631560A4 (en) * | 2010-10-20 | 2014-04-30 | Daikin Ind Ltd | AIR CONDITIONING |
EP2631560A1 (en) * | 2010-10-20 | 2013-08-28 | Daikin Industries, Ltd. | Air conditioner |
AU2011319038B2 (en) * | 2010-10-20 | 2015-04-09 | Daikin Industries, Ltd. | Air conditioner |
JP2012112638A (ja) * | 2010-11-05 | 2012-06-14 | Daikin Industries Ltd | 空気調和機 |
EP2636961A4 (en) * | 2010-11-05 | 2018-03-21 | Daikin Industries, Ltd. | Air conditioner |
WO2012060227A1 (ja) * | 2010-11-05 | 2012-05-10 | ダイキン工業株式会社 | 空気調和機 |
AU2011324586B2 (en) * | 2010-11-05 | 2015-09-24 | Daikin Industries, Ltd. | Air conditioner |
CN103201565A (zh) * | 2010-11-05 | 2013-07-10 | 大金工业株式会社 | 空调机 |
JP2012149803A (ja) * | 2011-01-18 | 2012-08-09 | Daikin Industries Ltd | 空気調和機 |
CN103314259A (zh) * | 2011-01-18 | 2013-09-18 | 大金工业株式会社 | 空调机 |
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EP2667105A4 (en) * | 2011-01-18 | 2016-12-28 | Daikin Ind Ltd | AIR CONDITIONER |
JP2012149836A (ja) * | 2011-01-19 | 2012-08-09 | Daikin Industries Ltd | 空気調和機 |
EP2667108A4 (en) * | 2011-01-19 | 2017-09-27 | Daikin Industries, Ltd. | Air conditioner |
WO2012099192A1 (ja) * | 2011-01-19 | 2012-07-26 | ダイキン工業株式会社 | 空気調和機 |
Also Published As
Publication number | Publication date |
---|---|
JP5229031B2 (ja) | 2013-07-03 |
US20120000224A1 (en) | 2012-01-05 |
AU2010225998B2 (en) | 2012-12-13 |
CN102348936A (zh) | 2012-02-08 |
AU2010225998A1 (en) | 2011-11-03 |
EP2410250A1 (en) | 2012-01-25 |
JP2010216767A (ja) | 2010-09-30 |
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