WO2013035130A1 - 車両用空調装置 - Google Patents
車両用空調装置 Download PDFInfo
- Publication number
- WO2013035130A1 WO2013035130A1 PCT/JP2011/004981 JP2011004981W WO2013035130A1 WO 2013035130 A1 WO2013035130 A1 WO 2013035130A1 JP 2011004981 W JP2011004981 W JP 2011004981W WO 2013035130 A1 WO2013035130 A1 WO 2013035130A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- control unit
- flow path
- refrigerant control
- Prior art date
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Classifications
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
- B60H1/00785—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models by the detection of humidity or frost
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
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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
- F25B2600/2501—Bypass valves
Definitions
- the present invention relates to a vehicle air conditioner having a function of dehumidifying heating, and more particularly to a vehicle air conditioner capable of ensuring a dehumidifying capacity during a dehumidifying heating operation regardless of fluctuations in heat load.
- Patent Document 1 Japanese Patent Laid-Open No. 6-341732
- FIG. 8 this is because the first heat exchanger 2 in which the air flow rate is adjusted by the damper 5 in the air conditioning unit 1 and the first heat exchanger 2 arranged upstream of the first heat exchanger 2.
- the second expansion device 41, the second heat exchanger 3, and the accumulator 10 are connected in this order to form a closed loop between the inflow side and the outflow side of the first expansion device 7.
- the outflow side of the first heat exchanger 2 and the inflow side of the second expansion device 41 are opened and closed by on-off valves V1, V3 and V4, respectively, to control the on-off of the on-off valves V1 to V4 and the opening of the damper 5. It is, in which to be able to switch the operating mode cooling operation mode, heating operation mode, and the dehumidification heating operation mode.
- V1 is opened, V2 is opened, V3 is closed, V4 is closed, and the first heat exchanger 2 is passed through the second heat exchanger with no air flow.
- the damper 5 is set at the full cool position so that all of the air is bypassed by the first heat exchanger 2, and the refrigerant compressed by the compressor 6 is allowed to pass through the first heat exchanger 2 and then heat exchange outside the vehicle interior.
- the heat is radiated by the vessel 4, the pressure is reduced by the second expansion device 41, the heat is absorbed by the second heat exchanger 3, and then returned to the compressor 6 via the accumulator 10.
- V1 is closed, V2 is closed, V3 is closed, and V4 is opened so that all the air that has passed through the second heat exchanger 3 passes through the first heat exchanger 2.
- the damper 5 is set to the full hot position, the refrigerant compressed by the compressor 6 is radiated by the first heat exchanger 2, and then the pressure is reduced by the first expansion device 7 and the heat is absorbed by the vehicle exterior heat exchanger 4. After that, it is returned to the compressor 6 through the accumulator 10.
- V1 is closed, V2 is closed, V3 is opened, V4 is opened, and the damper is set to a full hot position or an intermediate position, and as shown in FIG.
- the compressed refrigerant is dissipated by the first heat exchanger 2, and then a part of the refrigerant is decompressed by the second expansion device 41 and absorbed by the second heat exchanger 3, and the remaining refrigerant is removed.
- the pressure is reduced by the first expansion device 7 and absorbed by the vehicle exterior heat exchanger 4 and then returned to the compressor 6 via the accumulator 10.
- the dehumidifying capacity in the dehumidifying and heating operation mode varies depending on the temperature of the outside air, and during the intermediate heat load where the outside air temperature is 15 to 25 ° C., the outside air temperature is low and the low heat load ( There is a concern that the dehumidifying ability is lower than that of 5 to 15 ° C.
- the present invention has been made in view of such circumstances, and provides a vehicle air conditioner capable of ensuring a dehumidifying capacity even during a medium heat load in which the outside air temperature becomes high during dehumidifying heating operation.
- the main issue is to ensure a dehumidifying capacity even during a medium heat load in which the outside air temperature becomes high during dehumidifying heating operation.
- a vehicle air conditioner includes a compressor, a first heat exchanger that is disposed in an air conditioning unit and has an air flow rate adjusted by a damper, and the air conditioning unit.
- a second heat exchanger that is disposed upstream of the first heat exchanger in the air flow direction in the air conditioning unit, a vehicle exterior heat exchanger that can exchange heat with the outside air, and a refrigerant flow
- a first refrigerant control unit capable of restricting the passage
- a second refrigerant control unit capable of restricting and closing the refrigerant flow path
- a third refrigerant capable of restricting and closing the refrigerant flow path.
- a refrigerant control unit, and a fourth refrigerant control unit capable of closing the refrigerant flow path, the compressor, the first heat exchanger, the first refrigerant control unit, and the vehicle exterior heat.
- the exchanger, the second refrigerant control unit, and the second heat exchanger are routed at least in this order.
- the first refrigerant control unit capable of restricting the refrigerant flow path for using the vehicle exterior heat exchanger as the heat absorber and the vehicle exterior heat exchanger as the heat radiator are used.
- a second refrigerant control unit capable of restricting a refrigerant flow path for using the heat exchanger of No. 2 as a heat absorber, and a third refrigerant control capable of restricting a refrigerant flow path used during dehumidifying heating operation
- the second and fourth refrigerant control units can each close the refrigerant flow path, so that the second heat can be switched by switching the flow of the refrigerant that has passed through the vehicle exterior heat exchanger. It is possible to ensure the dehumidifying ability even during a medium heat load where the outside air temperature is relatively high by appropriately suppressing the increase in the evaporation pressure of the exchanger.
- the refrigerant flow path is throttled by the first control unit, and the refrigerant flow path is closed by the second refrigerant control unit.
- the third refrigerant control unit throttles the refrigerant flow path, and the fourth refrigerant control unit does not close the refrigerant flow path, and the refrigerant discharged from the compressor is supplied to the first heat exchanger, the first 1 refrigerant control unit, the vehicle exterior heat exchanger, the fourth refrigerant control unit, and the compressor circulate in the order of the compressor, the first heat exchanger, the third refrigerant control unit, Circulating the refrigerant in the order of the second heat exchanger and the compressor;
- the first refrigerant control unit throttles the refrigerant flow path
- the second refrigerant control unit throttles the refrigerant flow path
- the third refrigerant The control unit narrows the refrigerant flow path
- the fourth refrigerant control unit closes the refrigerant flow path, and discharges the refrigerant discharged from the compressor to the first heat exchanger, the first refrigerant control unit, While circulating
- the compressor and the first heat exchanger are routed through the heat absorption path via the vehicle exterior heat exchanger and the second heat exchanger.
- the heat absorption paths in parallel with each other, it becomes possible to have the same function as the conventional one in which the air is dehumidified by the second heat exchanger and the air is heated by the first heat exchanger.
- the refrigerant flowing out of the heat exchanger outside the passenger compartment is returned directly to the suction side of the compressor, the pressure on the suction side of the compressor rises, and the second As the evaporating pressure of the heat exchanger increases, the refrigerant that has passed through the outside heat exchanger is adiabatically expanded again by the second refrigerant control unit, and the adiabatic expanded refrigerant is adiabatically expanded by the third refrigerant control unit.
- the second heat exchanger is made to absorb heat in the second heat exchanger together with the cooled refrigerant. Evaporation pressure of no longer be affected by the outlet pressure of the outer heat exchanger, even when the thermal load in the outside air temperature is relatively high, it is possible to ensure the dehumidification capacity.
- the outside air temperature changes from a relatively high medium heat load state to a relatively low low heat load state, and the condition where the heat load exceeds a predetermined value is not exceeded. If it changes, it is determined that the thermal load does not exceed the predetermined value. Therefore, the thermal load exceeds the predetermined value from the refrigerant circulation state when it is determined that the thermal load exceeds the predetermined value as described above. It can be changed to the refrigerant circulation state when it is determined that the refrigerant is not present.
- the heat absorbed by the exterior heat exchanger 4 is adiabatically expanded by the second refrigerant control unit, and the heat load of the blown air is low even though it absorbs heat again by the second heat exchanger. Since the amount of heat absorption cannot be obtained and the refrigerant is returned to the compressor 6 in a state where the temperature and pressure are relatively low, the temperature of the refrigerant discharged from the compressor 6 is not increased, and sufficient heating capacity cannot be secured.
- each stage area has a dehumidifying heating operation mode.
- the relationship of A ⁇ C is established.
- a ⁇ C ⁇ B is satisfied. It is desirable that the relationship is controlled or set so that the relationship is established.
- the restriction of the refrigerant flow path in the first refrigerant controller is determined from the viewpoint of securing the heating capacity, that is, in order to increase the refrigerant temperature of the first heat exchanger.
- the refrigerant control unit it is preferable to keep the refrigerant pressure of the first heat exchanger high by narrowing the cross-sectional area of the refrigerant flow path relatively small.
- the second refrigerant control unit restricts the refrigerant flow path from the viewpoint of securing the cooling capacity, that is, in order to obtain an endothermic amount in the second heat exchanger.
- the third refrigerant control unit determines the degree of throttling from the viewpoint of securing the dehumidifying heating capacity, that is, there is a request for securing the heating capacity of the first heat exchanger, while the cooling of the second heat exchanger is performed.
- the second refrigerant Since the refrigerant also flows through the control unit, it is desirable to define the magnitude relationship with respect to the cross-sectional area of the refrigerant flow path controlled or set by the second refrigerant control unit.
- the first refrigerant control unit includes a first expansion device and a first on-off valve connected in parallel
- the second refrigerant control unit includes the second expansion device and a second opening / closing.
- the third refrigerant control unit is formed by connecting a third expansion device and a third on-off valve in series
- the fourth refrigerant control unit is a fourth unit. It may comprise so that it may consist of an on-off valve (claim 4).
- the first expansion device, the second expansion device, and the third expansion device described above may be configured by fixed orifices (Claim 5), but the third expansion device is configured to meet the outside air condition. You may make it comprise with a variable type expansion valve so that setting conditions can be changed (Claim 6).
- the configuration is simpler than the expansion valve that controls the opening degree of the expansion valve, and the cost can be further reduced.
- the third expansion device is constituted by a variable expansion valve, the refrigerant flow rate of the first bypass passage can be changed according to the heat load condition of the outside air, and the controllability of the dehumidifying heating capacity can be improved.
- the second on-off valve and the fourth on-off valve may be replaced with one three-way valve since the other is opened when one is closed (Claim 7). The number of parts can be reduced.
- the first refrigerant control unit is a variable expansion valve capable of restricting or not restricting the refrigerant flow path (Claim 8), and the second refrigerant control unit and / or the third refrigerant control unit is provided.
- a variable expansion valve that can throttle and close the refrigerant flow path may be used.
- the air conditioning control can be performed more finely by reducing the number of parts of the refrigerant control unit and controlling the throttle of the refrigerant flow path.
- the refrigerant is circulated through the first heat exchanger disposed in the air conditioning unit.
- the refrigerant is disposed in the air conditioning unit, the amount of ventilation is adjusted by the damper, and the liquid heat A third heat exchanger in which the medium circulates; a pump that pumps the liquid heat medium; a fourth heat exchanger that exchanges heat between the liquid heat medium and the refrigerant discharged from the compressor;
- a hot water cycle configured by connecting pipes to replace the first heat exchanger with the hot water cycle (claim 10).
- the above-described configuration can be realized using an existing hot water heater unit, and the conventional air conditioning unit that is mounted on a vehicle equipped with an internal combustion engine and performs heating by a hot water cycle is provided. It can be used.
- an internal heat exchanger that exchanges heat between the refrigerant on the suction side of the compressor and the refrigerant on the outflow side of the first heat exchanger may be provided. .
- the amount of heat released from the first heat exchanger can be increased.
- the first refrigerant control unit capable of restricting the refrigerant flow path when performing the heating operation using the vehicle exterior heat exchanger as the heat sink, and the vehicle exterior heat exchange.
- a second refrigerant control unit capable of restricting the refrigerant flow path when performing a cooling operation using the second heat exchanger as a heat sink and a second heat exchanger as a heat sink, and a refrigerant when performing a dehumidifying heating operation
- a third refrigerant control unit capable of restricting the flow path, and switching the flow of the refrigerant that has passed through the heat exchanger outside the passenger compartment, thereby making it possible to adjust the dehumidifying capacity of the second heat exchanger.
- a vehicle air conditioner capable of ensuring the dehumidifying ability even when the outside air temperature varies from the low heat load to the medium heat load during the dehumidifying heating operation.
- the refrigerant after absorbing heat by the vehicle exterior heat exchanger is further depressurized by the second refrigerant control unit so as to flow into the second heat exchanger. It is possible to prevent the evaporation pressure of the exterior heat exchanger from propagating to the second heat exchanger, thereby suppressing the increase in the evaporation pressure of the second heat exchanger and ensuring the dehumidifying capacity. It becomes possible.
- a possible vehicle air conditioner can be obtained. That is, when the outside air load becomes low, the refrigerant after absorbing heat by the vehicle exterior heat exchanger is returned to the compressor without adiabatic expansion by the second refrigerant control unit, thereby Energy absorbed by the exchanger can be supplied to the first heat exchanger via the compressor, and heating capacity can be ensured.
- FIG. 1 shows a vehicle air conditioner according to the present invention
- FIG. 1 (a) is an overall configuration diagram thereof
- FIG. 1 (b) is a table showing operation modes, states of on-off valves and dampers.
- FIG. 2 is a diagram for explaining the flow of the refrigerant in the cooling operation mode of the vehicle air conditioner according to the present invention.
- FIG. 3 is a diagram for explaining the flow of the refrigerant in the heating operation mode of the vehicle air conditioner according to the present invention.
- FIG. 4 is a diagram for explaining the flow of refrigerant during the dehumidifying and heating operation mode of the vehicle air conditioner according to the present invention.
- FIG. 4 (a) shows a low heat load when the outside air load is low (outside air temperature: 5 to 15 ° C.).
- FIG. 5 is a view showing a modification of the vehicle air conditioner according to the present invention (an example in which the second on-off valve and the fourth on-off valve are replaced with one three-way valve), and FIG. It is the whole block diagram, FIG.5 (b) is a table
- FIG. 6 shows a first heat exchanger of the vehicle air conditioner shown in FIG. 1A, a third heat exchanger that circulates hot water, and a fourth heat exchanger that exchanges heat between the hot water and the refrigerant.
- FIG. 7 shows a configuration example in which an internal heat exchanger for exchanging heat between the refrigerant on the compressor inflow side and the refrigerant on the outflow side of the first heat exchanger of the vehicle air conditioner shown in FIG.
- FIG. 8 shows a conventional vehicle air conditioner
- FIG. 8 (a) is an overall configuration diagram thereof
- FIG. 8 (b) is a table showing an operation mode and states of on-off valves and dampers.
- FIG. 9 is a diagram for explaining the refrigerant flow in the dehumidifying and heating operation mode in the conventional vehicle air conditioner.
- FIG. 1 a vehicle air conditioner according to the present invention is shown.
- the vehicle air conditioner is mounted on, for example, an automobile, and includes first and second heat exchangers 2 disposed in an air conditioning unit 1. 3 and a vehicle exterior heat exchanger 4 which is disposed outside the air conditioning unit 1 and can exchange heat with the outside air.
- An inside / outside air switching device (not shown) is provided on the most upstream side of the air conditioning unit 1, and the inside air inlet and the outside air inlet are selectively opened by an intake door.
- the inside air or the outside air selectively introduced into the air conditioning unit 1 is sucked by the rotation of the blower 20 and is sent to the first and second heat exchangers 2 and 3 where heat is exchanged therefor and a desired outlet. Is supplied to the passenger compartment.
- the first heat exchanger 2 is disposed downstream of the second heat exchanger 3 in the air flow direction in the air conditioning unit, and on the upstream side of the first heat exchanger 2 in the air flow direction, A damper 5 is provided.
- the damper 5 can be varied from a position (full hot position: 100% opening) to a position (full cool position: 0% opening) where the air flow rate of the first heat exchanger 2 is maximized.
- the ratio between the air passing through the first heat exchanger 2 and the bypassing air can be adjusted by adjusting the opening degree.
- the inflow side 2 a of the first heat exchanger 2 is connected to the discharge side A of the compressor 6, and the outflow side 2 b of the first heat exchanger 2 is connected to the first expansion device (O-1) 7 and the first heat exchanger 2.
- One on-off valve (V-1) 8 is connected to the inflow side 9a of the first refrigerant control unit 9 configured to be connected in parallel.
- the outflow side 3 b of the second heat exchanger 3 is connected to the suction side B of the compressor 6 via the accumulator 10.
- the outflow side 9b of the first refrigerant control unit 9 is connected to the inflow side 4a of the vehicle exterior heat exchanger 4, and the outflow side 4b of the vehicle exterior heat exchanger 4 is connected to the second on-off valve (V-2). ) 11 and the second expansion device (O-2) 12 are connected to the inflow side 3a of the second heat exchanger 3 via the second refrigerant control unit 13 configured to be connected in series. Yes. Therefore, the compressor 6, the first heat exchanger 2, the first refrigerant control unit 9, the vehicle exterior heat exchanger 4, the second refrigerant control unit 13, the second heat exchanger 3, the accumulator 10, and the compressor A refrigerant circulation cycle connected in a loop in the order of 6 is formed.
- the second on-off valve (V-2) 11 and the expansion device (O-2) 12 only need to be connected in series, and which one is arranged upstream in the refrigerant flow direction (on the downstream side). There is no restriction on whether or not to place them.
- a refrigerant flow path between the inflow side 3a of the exchanger 3 includes a third refrigerant control unit 16 including a third on-off valve (V-3) 14 and a third expansion device (O-3) 15.
- the refrigerant flow path between the outflow side 4b of the vehicle exterior heat exchanger 4 and the inflow side 13a of the second refrigerant control unit 13 and the second heat exchanger 3 are connected by a first bypass flow path 21 having The refrigerant flow path between the outflow side 3b of the compressor and the suction side B of the compressor 6 (between the inflow side 10a of the accumulator 10) is opened and closed by a fourth on-off valve (V-4) 17.
- the two bypass flow paths 22 are connected.
- the third on-off valve (V-3) 14 and the third expansion device (O-3) 15 only need to be connected in series, and which is arranged upstream in the refrigerant flow direction. There is no restriction on whether it is arranged on the downstream side.
- the on-off valve (V-4) 17 is arranged as a fourth refrigerant control unit.
- the first to third expansion devices 7, 12, and 15 are configured by fixed orifices, and the passage cross section of the throttle portion of the first expansion device 7 has a viewpoint of increasing the heating capacity.
- the passage section of the throttle portion of the second expansion device 12 is set to be relatively large from the viewpoint of ensuring the cooling capacity, that is, from the viewpoint of increasing the refrigerant supply amount while reducing the refrigerant pressure.
- the passage section of the throttle portion of the third expansion device 15 is set to be equal to or larger than the passage section of the first expansion device 7 because it is necessary to ensure the dehumidifying capacity and the heating capacity to some extent.
- the passage section of the second expansion device 12 is preferably set smaller. That is, assuming that the cross-sectional areas of the throttle portions of the first expansion device 7, the second expansion device 12, and the third expansion device 15 are A, B, and C, a relationship of A ⁇ C ⁇ B is set. Has been.
- the ratio of the refrigerant passing through the first bypass passage 21 provided with the third expansion device 15 becomes too small, and most of the refrigerant circulation amount is outside the passenger compartment. Since it passes through the heat exchanger 4, even if the dehumidifying and heating operation is performed at a low heat load as shown in FIG. 4A, the dehumidifying capacity is insufficient because the refrigerant flowing through the second heat exchanger is small. There is a fear. Also, if B ⁇ C, the ratio of the refrigerant passing through the first bypass passage 21 provided with the third expansion device 15 becomes too large, and most of the refrigerant circulation amount is outside the vehicle compartment heat.
- This control unit 23 is a publicly known unit having an input circuit including an A / D converter and a multiplexer, an arithmetic processing circuit including a ROM, a RAM, and a CPU, and an output circuit including a drive circuit.
- An outside air temperature signal from the outside air temperature sensor 24 and various signals for setting the operation mode are inputted, and these signals are processed in accordance with a predetermined program.
- the mode of dehumidifying and heating is switched according to the outside air temperature. If the outside air temperature is in the range of 5 to 15 ° C. (when the outside air load is low and the heat load is low) If it is set to the dehumidifying and heating operation mode for low heat load described later and the outside air temperature is in the range of 15 to 25 ° C. (if the outside air load is relatively high during medium heat load), The dehumidifying heating operation mode for heat load is set.
- the control unit 23 opens the first and second on-off valves 8, 11 as shown in FIG.
- the on-off valves 14 and 17 are closed, and the damper 5 is set to the full cool position (position where the opening is 0%).
- the compressed refrigerant discharged from the discharge side A of the compressor 6 passes through the first on-off valve 8 without passing through the first heat exchanger 2 because there is no air passing through the first heat exchanger 2.
- the second expansion device 12 After entering into the vehicle exterior heat exchanger 4 where heat is dissipated (condensed and liquefied), it reaches the second expansion device 12 via the second on-off valve 11 and is depressurized by the second expansion device 12 to be second.
- the heat exchanger 3 is then absorbed, and after being absorbed (evaporated and vaporized), it is returned to the compressor 6 via the accumulator 10. For this reason, the air sent from the upstream of the air conditioning unit 1 is cooled by the second heat exchanger 3, bypasses the first heat exchanger 2, and is supplied as it is to the vehicle interior as cold air.
- the control unit 23 closes the first and second on-off valves 8 and 11 and closes the third on-off valve 14 as shown in FIG. Then, the fourth on-off valve 17 is opened, and the damper 5 is set to the full hot position (position of 100% opening). Then, the compressed refrigerant discharged from the discharge side A of the compressor 6 dissipates heat (condensates and liquefies) in the first heat exchanger 2, is decompressed by the first expansion device 7, and reaches the vehicle exterior heat exchanger 4. Then, after the heat absorption (vaporization and vaporization), it passes through the fourth on-off valve 17 and is returned to the compressor 6 through the accumulator 10. For this reason, the air sent from the upstream of the air conditioning unit 1 passes through the second heat exchanger 3 but is not heat-exchanged, and is all guided to the first heat exchanger 2 to be heated, as hot air. Supplied in the passenger compartment.
- the dehumidifying heating operation mode when the outside air temperature is 5 to 15 ° C., as shown in FIG. 4 (a), the dehumidifying heating operation mode for low heat load is set,
- the control unit 23 closes the first and second on-off valves 8 and 11, opens the first and fourth on-off valves 14 and 17, and sets the opening of the damper 5 to the full hot position or an arbitrary intermediate position. Set. For this reason, the compressed refrigerant discharged from the discharge side A of the compressor 6 is radiated (condensed and liquefied) by the first heat exchanger 2, depressurized by the first expansion device 7, and then transferred to the vehicle exterior heat exchanger 4.
- the heat is absorbed (evaporated and vaporized) and then returned to the compressor 6 through the fourth on-off valve 17 and the accumulator 10.
- the refrigerant that has passed through the first heat exchanger 2 is depressurized by the third expansion device 15 and reaches the second heat exchanger 3, where it is absorbed (evaporated and vaporized) and then passed through the accumulator 10. And returned to the compressor 6.
- the air sent from the upstream of the air conditioning unit 1 is dehumidified by the second heat exchanger 3, heated when passing through the first heat exchanger 2, and dried as warm air in the vehicle interior. To be supplied.
- the dehumidifying and heating operation mode for the intermediate heat load is set.
- the control unit 23 closes the first on-off valve 8, opens the second on-off valve 11, opens the third on-off valve 14, closes the fourth on-off valve 17, and opens the damper 5. Set the degree to the full hot position or any intermediate position. Then, the compressed refrigerant discharged from the discharge side A of the compressor 6 is radiated (condensed and liquefied) by the first heat exchanger 2, is decompressed by the first expansion device 7, and reaches the exterior heat exchanger 4.
- the pressure is reduced by the second expansion device 12 through the second on-off valve 11 and supplied to the second heat exchanger 3.
- the heat is returned to the compressor 6 through the accumulator 10.
- the refrigerant that has passed through the first heat exchanger 2 is decompressed by the third expansion device 15 and enters the second heat exchanger 3, where it is absorbed (evaporated and vaporized), and then passed through the accumulator 10. And returned to the compressor 6.
- the air sent from the upstream of the air conditioning unit 1 is dehumidified by the second heat exchanger 3, heated when passing through the first heat exchanger 2, and dried as warm air in the vehicle interior. To be supplied.
- the evaporation pressure of the refrigerant that has passed through the vehicle exterior heat exchanger 4 is high during an intermediate heat load, but the refrigerant that has passed through the vehicle exterior heat exchanger 4 may be directly guided to the accumulator 10. Therefore, the evaporating pressure of the second heat exchanger 3 is not increased by the propagation of the evaporating pressure of the vehicle exterior heat exchanger 4, and the third pressure after the pressure is reduced via the second expansion device 12. Since it is led to the second heat exchanger 3 together with the refrigerant adiabatically expanded via the expansion device 15, it is possible to increase the heat absorption capability in the second heat exchanger 3, and to ensure sufficient dehumidification capability. Is possible.
- V-2) 11 and V-4 on-off valve (V-4) 17 are selectively opened with respect to the cycle configuration described above. As shown in FIG. 4, these may be combined and constituted by one three-way valve 25.
- the first to third expansion devices 7, 12, and 15 are configured by fixed orifices.
- the first expansion device 7 and the second expansion device 12 have heating capacity and Although the passage cross section of the throttle portion is determined almost uniquely from the viewpoint of determining the cooling capacity, in the dehumidifying and heating operation, the third expansion device 15 can be varied to finely adjust the ratio between the dehumidifying capacity and the heating capacity. It may be replaced with a type expansion valve.
- the heat dissipation amount of the first heat exchanger 2 can be increased by setting the throttle of the variable expansion valve to be narrow when the dehumidifying and heating operation is performed at a low heat load where it is desired to ensure the heating capacity. It is possible to increase the heating capacity, and when the dehumidifying and heating operation is performed at a medium heat load where it is desired to ensure the dehumidifying capacity, the throttle of the variable expansion valve is set open to make the first bypass flow path open. It is possible to increase the circulation amount of the refrigerant that passes through, that is, the refrigerant that does not absorb heat from the air outside the passenger compartment without passing through the heat exchanger outside the passenger compartment, thereby increasing the dehumidifying capacity of the second heat exchanger 3.
- variable expansion valve By introducing such a variable expansion valve, it is possible to finely adjust the ratio between the dehumidifying capacity and the heating capacity in each dehumidifying and heating operation at the time of low heat load and medium heat load.
- the variable expansion valve At the time of low heat load, when the outside air temperature is much lower, the variable expansion valve is throttled to increase the heating capacity at the time of extremely low heat load, and at other low heat loads, the variable expansion valve The heating capacity is set to be relatively low by setting the throttle of the expansion valve to be relatively open, and the throttle of the variable expansion valve is also adjusted at the time of medium to low heat load when the heat load is relatively low even at medium heat load. It is possible to perform control such that the throttle of the variable expansion valve is slightly opened when the heat load is somewhat higher than when the heat load is medium and low.
- the hot water type heat exchanger used conventionally is used as it is. Although it cannot be used, when the existing hot water heat exchanger is used, the configuration shown in FIG. 6 may be adopted.
- a known liquid heat medium such as water or coolant is used as a working fluid
- a third heat exchanger 26 that exchanges heat between the liquid heat medium and air
- a pump 27 that pumps the liquid heat medium
- a water heater 30 that heats the liquid heat medium
- a hot water cycle 30 that is configured by sequentially pipe-connecting a liquid heat medium and a fourth heat exchanger 29 that exchanges heat between the liquid heat medium and the refrigerant discharged from the compressor 6.
- a third heat exchanger 26 is disposed in place of the first heat exchanger 2, and the ventilation amount of the third heat exchanger 26 is adjusted by the damper 5.
- a fourth heat exchanger 29 is interposed between the discharge side of the compressor 6 and the portion where the first bypass passage 21 is connected, and the fourth heat exchanger 29 discharges from the compressor 6.
- Heat exchange between the refrigerant and the liquid heat medium of the hot water cycle 30, The liquid heat medium third by heat exchanger 26 may be come heat exchange with the air sent from the upstream of the air conditioning unit 1.
- the refrigerant on the suction side of the compressor 6 for example, the outflow side 10a of the accumulator 10
- the first An internal heat exchanger (IHX) 31 that exchanges heat with the refrigerant on the discharge side of the one heat exchanger 2 may be further provided. That is, the refrigerant flowing into the compressor 6 passes through the low pressure side passage 31a of the internal heat exchanger 31 (the inflow side of the low pressure side passage 31a is connected to the outflow side 10a of the accumulator, and the outflow side of the low pressure side passage 31a is compressed.
- the refrigerant flowing out from the first heat exchanger 2 is allowed to pass through the high-pressure side passage 31b of the internal heat exchanger 31 (the high-pressure side passage 31b is connected to the first heat exchanger 2). It may be configured to be interposed in a portion on the outflow side and upstream of the portion where the first bypass passage 21 is connected in the refrigerant flow direction. Further, in order to be able to select whether or not to exchange heat with the internal heat exchanger 31, a third bypass passage 32 that bypasses the high-pressure side passage 31b or the low-pressure side passage 31a is provided (in this example, a high-pressure passage 31).
- a passage that bypasses the side passage 31b is provided), and the third bypass passage 32 may be switched to the high-pressure side passage 31b by the three-way valve 33.
- the first heat exchanger can be controlled by switching the three-way valve 33. 2 is adjusted, the pressure of the refrigerant flowing into the compressor 6 is prevented from becoming too high, and the driving power of the compressor is prevented from being excessive, and the pressure of the refrigerant compressed by the compressor 6 is increased. It becomes possible to prevent the compressor 6 from becoming too high and failing.
- the form for implementing this invention has been demonstrated, of course, it can change suitably in the range which does not deviate from the objective of this invention.
- the dehumidifying and heating operation mode it is described that the outside air temperature is used as an index to determine whether the heat load is low or medium heat load.
- the second heat exchanger is directly connected to the second heat exchanger.
- a cooling temperature detection unit may be provided downstream, a predetermined cooling temperature may be set, and the determination may be made based on whether or not the temperature detected by the cooling temperature detection unit exceeds the predetermined cooling temperature.
- a heating temperature detecting means is provided directly or downstream in the first heat exchanger and a predetermined heating temperature is set, and it is determined whether or not the temperature detected by the heating temperature detecting means exceeds the predetermined heating temperature. May be. Further, in the process in which the load of the outside air rises from the low heat load to the medium heat load, it is determined whether the refrigerant flow is switched from the cooling temperature detecting means and the predetermined cooling temperature, and the temperature falls from the medium heat load to the low heat load. In the process, it may be determined whether the refrigerant flow is switched from the heating temperature detecting means and the predetermined heating temperature. In this way, it is possible to reliably prevent shortage of the dehumidifying capacity and the heating capacity regardless of how the outside air load fluctuates in the dehumidifying and heating operation mode.
- the first refrigerant control unit, the second refrigerant control unit, and the third refrigerant control unit each include an expansion device and an on-off valve, and any or all of the refrigerant control units are provided with variable expansion. You may concentrate on a valve. Even if it is a variable expansion valve, the first refrigerant control unit selects whether or not the refrigerant is adiabatically expanded, and the second and third refrigerant control units select whether the refrigerant is adiabatically expanded or whether the refrigerant flow is stopped. You can make a choice. And since a number of parts can be reduced, the productivity of the said vehicle air conditioner and the freedom degree at the time of vehicle arrangement
- finer air conditioning control can be performed.
- the second refrigerant control unit controls the degree of throttling so that the refrigerant on the outflow side 3b of the second heat exchanger 3 has a certain degree of superheat (superheat).
- the temperature of the cold air can be stabilized by adjusting the flow rate of the refrigerant to make the temperature of the second heat exchanger 3 constant.
- the temperature of the hot air is appropriately changed by adjusting the refrigerant pressure of the first heat exchanger by controlling the degree of throttling by the first refrigerant controller, and this is changed by the damper 5.
Abstract
Description
これは、図8に示されるように、空調ユニット1内にダンパ5で通風量が調整される第1の熱交換器2と、この第1の熱交換器2より上流側に配置された第2の熱交換器3とを備え、圧縮機6と、第1の熱交換器2と、第1の膨張装置7と、空調ユニット外に配置された車室外熱交換器4と、開閉弁V2と、第2の膨張装置41と、第2の熱交換器3と、アキュムレータ10とをこの順で配管接続して閉ループを形成し、第1の膨張装置7の流入側と流出側との間、第1の熱交換器2の流出側と第2の膨張装置41の流入側との間、及び車室外熱交換器4の流出側と圧縮機6の吸入側(アキュムレータ10の流入側)との間にそれぞれ開閉弁V1、V3,V4にて開閉される通路を設け、各開閉弁V1~V4の開閉とダンパ5の開度を制御することで、運転モードを冷房運転モード、暖房運転モード、及び除湿暖房運転モードに切り換えることができるようにしたものである。
前記熱負荷が所定値を超えていると判定された場合に、前記第1の冷媒制御部で冷媒流路を絞り、前記第2の冷媒制御部で冷媒流路を絞り、前記第3の冷媒制御部で冷媒流路を絞り、前記第4の冷媒制御部で冷媒流路を閉じて、前記圧縮機から吐出した冷媒を、前記第1の熱交換器、前記第1の冷媒制御部、前記車室外熱交換器、前記第2の冷媒制御部、前記第2の熱交換器、及び前記圧縮機の順で冷媒を循環させると共に、前記第1の熱交換器、前記第3の冷媒制御部、前記第2の熱交換器、及び前記圧縮機の順で冷媒を循環させるとよい(請求項2)。
ここで、第1の冷媒制御部、第2の冷媒制御部、及び第3の冷媒制御部のそれぞれの絞り部分の断面積をA,B,Cとすると、各段面積は、除湿暖房運転モードにおいて、熱負荷が所定値を超えていないと判定された場合にはA≦Cの関係となるように、熱負荷が所定値を超えていると判定された場合にはA≦C<Bの関係となるように、制御もしくは設定されていることが望ましい(請求項3)。
また第2の冷媒制御部での冷媒流路の絞りは、冷房能力を確保する観点から絞り具合が決定されるため、即ち第2の熱交換器での吸熱量を得るため、第2の冷媒制御部では冷媒流路の断面積を相対的に大きめに絞って適切な冷媒循環量を確保することが好ましく、
第3の冷媒制御部は、除湿暖房能力を確保する観点から絞り具合が決定されるため、即ち第1の熱交換器の暖房能力を確保する要請がある一方、第2の熱交換器の冷房能力も得るために一定の冷媒流量を確保する要請もあることから、第1の冷媒制御部の冷媒流路の断面積と同等以上であり、且つ、第2の冷媒制御部の冷媒流路の断面積よりも小さくしておくことが望ましいためである。
そして、熱負荷が所定値を超えていないと判定された場合には、第2の冷媒制御部には冷媒が流れないので、第1の冷媒制御部で制御もしくは設定される冷媒流路の断面積と、第3の冷媒制御部で制御もしくは設定される冷媒流路の断面積との大小関係を規定し、熱負荷が所定値を超えていると判定された場合には、第2の冷媒制御部にも冷媒が流れるので、第2の冷媒制御部で制御もしくは設定される冷媒流路の断面積についても、大小関係を規定することが望ましい。
即ち、外気負荷が高くなってきた場合には、車室外熱交換器で吸熱した後の冷媒を第2の冷媒制御部でさらに減圧して第2の熱交換器に流入させるようにすることで、車室外熱交換器の蒸発圧力が第2の熱交換器に伝搬しないようにすることが可能となり、これにより第2の熱交換器の蒸発圧力の上昇を抑え、除湿能力を確保することが可能となる。
さらには、車室外熱交換器を通過した冷媒の流れ方を切り換えることで、除湿暖房運転時において、外気温が中熱負荷時から低熱負荷時へと変動しても暖房能力を確保することが可能な車両用空調装置を得ることが可能となる。
即ち、外気負荷が低くなってきた場合には、車室外熱交換器で吸熱した後の冷媒を第2の冷媒制御部で断熱膨張することなく圧縮機に戻すようにすることで、車室外熱交換器で吸熱したエネルギーを圧縮機を介して第1の熱交換器に供給でき、暖房能力を確保することが可能となる。
図1において、この発明に係る車両用空調装置が示され、車両用空調装置は、例えば自動車に搭載されるもので、空調ユニット1内に配置された第1及び第2の熱交換器2,3と、空調ユニット1外に配置され、外気と熱交換可能な車室外熱交換器4とを備えている。
また、このような可変式膨張弁の導入により、低熱負荷時や中熱負荷時のそれぞれの除湿暖房運転において、除湿能力と暖房能力との比率を微調整することが可能となる。即ち、低熱負荷時において、外気温が一層低い極低熱負荷時においては、可変式膨張弁の絞りを絞り気味に設定して暖房能力を一層高め、それ以外の低熱負荷時には、可変式膨張弁の絞りを相対的に開き気味に設定して暖房能力を相対的に低くするようにし、また、中熱負荷時においても、熱負荷が比較的に低い中低熱負荷時には、可変式膨張弁の絞りを幾分絞り気味とし、熱負荷が中低熱負荷時と比べて幾分高い中高熱負荷時には、可変式膨張弁の絞りを幾分開き気味とする制御を行うことが可能となる。
即ち、圧縮機6に流入する冷媒を内部熱交換器31の低圧側通路31aを通過させ(低圧側通路31aの流入側をアキュムレータの流出側10aに接続し、低圧側通路31aの流出側を圧縮機6の吸入側Bに接続し)、第1の熱交換器2から流出した冷媒を内部熱交換器31の高圧側通路31bを通過させる(高圧側通路31bを第1の熱交換器2の流出側であって第1のパイパス流路21が接続する部位よりも冷媒流れ方向上流の部分に介在させる)構成としてもよい。
また、内部熱交換器31で熱交換させるか否かを選択できるようにするために、高圧側通路31bまたは低圧側通路31aをバイパスする第3のパイパス流路32を設け(この例では、高圧側通路31bをバイパスする通路を設け)、この第3のパイパス流路32を三方弁33により、高圧側通路31bと切換え可能としてもよい。
このような構成とすれば、内部熱交換器31により第1の熱交換器2の放熱量を増大させることが可能となり、また、三方弁33を切換え制御することにより、第1の熱交換器2の放熱能力を調整することや、圧縮機6に流入する冷媒の圧力が高くなりすぎて圧縮機の駆動動力が過多になるのを防止すること、圧縮機6で圧縮される冷媒の圧力が高くなりすぎて圧縮機6が故障するのを防止することが可能となる。
例えば冷房運転モードにあっては、第2の冷媒制御部にて絞り具合を制御することで、第2の熱交換器3の流出側3bの冷媒が一定の過熱度(スーパーヒート)を持つように冷媒の流量を調整し、第2の熱交換器3の温度を一定化させて、冷風の温度を安定化することができる。暖房運転モードにあっては、第1の冷媒制御部にて絞り具合を制御することで、第1の熱交換器の冷媒圧力の調整を通じて温風の温度を適宜変化させ、これをダンパ5による第1の熱交換器2を通過する空気とバイパスする空気との割合の調整に加えることで、暖房量の制御性を向上することができる。
2 第1の熱交換器
3 第2の熱交換器
4 車室外熱交換器
5 ダンパ
6 圧縮機
7 第1の膨張装置
8 第1の開閉弁
9 第1の冷媒制御部
10 アキュムレータ
11 第2の開閉弁
12 第2の膨張装置
13 第2の冷媒制御部
14 第3の開閉弁
15 第3の膨張装置
16 第3の冷媒制御部
17 第4の開閉弁(第4の冷媒制御部)
21 第1のパイパス流路
22 第2のパイパス流路
25 三方弁
26 第3の熱交換器
27 ポンプ
29 第4の熱交換器
30 温水サイクル
31 内部熱交換器
Claims (11)
- 圧縮機と、空調ユニット内に配置されてダンパにより通風量が調整される第1の熱交換器と、前記空調ユニット内に配置されて前記第1の熱交換器よりも前記空調ユニット内の空気流れ方向上流側に配置された第2の熱交換器と、外気と熱交換が可能な車室外熱交換器と、冷媒流路を絞ることが可能な第1の冷媒制御部と、冷媒流路を絞ること及び閉じることが可能な第2の冷媒制御部と、冷媒流路を絞ること及び閉じることが可能な第3の冷媒制御部と、冷媒流路を閉じることが可能な第4の冷媒制御部と、を有し、
前記圧縮機、前記第1の熱交換器、前記第1の冷媒制御部、前記車室外熱交換器、前記第2の冷媒制御部、及び前記第2の熱交換器を少なくともこの順でループ状に接続し、
前記第1の熱交換器と前記第1の冷媒制御部との間の冷媒流路と前記第2の冷媒制御部と前記第2の熱交換器との間の冷媒流路とを、前記第3の冷媒制御部を備えた第1のバイパス流路にて接続し、
前記車室外熱交換器と前記第2の冷媒制御部との間の冷媒流路と前記第2の熱交換器と前記圧縮機との間の冷媒流路とを、前記第4の冷媒制御部を備えた第2のバイパス流路にて接続した
ことを特徴とする車両用空調装置。 - 除湿暖房運転モードにおいて、熱負荷が所定値を超えていないと判定された場合に、前記第1の冷媒制御部で冷媒流路を絞り、前記第2の冷媒制御部で冷媒流路を閉じ、前記第3の冷媒制御部で冷媒流路を絞り、前記第4の冷媒制御部で冷媒流路を閉じないで、前記圧縮機から吐出した冷媒を、前記第1の熱交換器、前記第1の冷媒制御部、前記車室外熱交換器、前記第4の冷媒制御部、及び前記圧縮機の順で冷媒を循環させると共に、前記第1の熱交換器、前記第3の冷媒制御部、前記第2の熱交換器、及び前記圧縮機の順で冷媒を循環させ、
前記熱負荷が所定の値を超えていると判定された場合に、前記第1の冷媒制御部で冷媒流路を絞り、前記第2の冷媒制御部で冷媒流路を絞り、前記第3の冷媒制御部で冷媒流路を絞り、前記第4の冷媒制御部で冷媒流路を閉じて、前記圧縮機から吐出した冷媒を、前記第1の熱交換器、前記第1の冷媒制御部、前記車室外熱交換器、前記第2の冷媒制御部、前記第2の熱交換器、及び前記圧縮機の順で冷媒を循環させると共に、前記第1の熱交換器、前記第3の冷媒制御部、前記第2の熱交換器、及び前記圧縮機の順で冷媒を循環させる
ことを特徴とする請求項1記載の車両用空調装置。 - [規則91に基づく訂正 07.09.2011]
前記第1の冷媒制御部、前記第2の冷媒制御部、及び前記第3の冷媒制御部のそれぞれの絞り部分の断面積をA,B,Cとすると、各断面積は、除湿暖房運転モードにおいて、
熱負荷が所定値を超えていないと判定された場合には、
A≦C
の関係となるように、
熱負荷が所定値を超えていると判定された場合には、
A≦C<B
の関係となるように、制御もしくは設定されていることを特徴とする請求項1又は2記載の車両用空調装置。 - 前記第1の冷媒制御部は第1の膨張装置と第1の開閉弁とを並列的に接続してなり、前記第2の冷媒制御部は第2の膨張装置と第2の開閉弁とを直列的に接続してなり、前記第3の冷媒制御部は第3の膨張装置と第3の開閉弁とを直列的に接続してなり、前記第4の冷媒制御部は第4の開閉弁よりなることを特徴とする請求項1乃至3のいずれかに記載の車両用空調装置。
- 前記第1の膨張装置、前記第2の膨張装置、及び前記第3の膨張装置は、固定オリフィスであることを特徴とする請求項4記載の車両用空調装置。
- 前記第3の膨張装置は、可変式膨張弁であることを特徴とする請求項4記載の車両用空調装置。
- 前記第2の開閉弁と前記第4の開閉弁とを1つの三方弁で置き換えたことを特徴とする請求項4乃至6のいずれかに記載の車両用空調装置。
- 前記第1の冷媒制御部は、冷媒流路を絞ること及び絞らないことが可能な可変式膨張弁によりなることを特徴とする請求項1乃至3のいずれかに記載の車両用空調装置。
- 前記第2の冷媒制御部および/または前記第3の冷媒制御部は、冷媒流路を絞ること及び閉じることが可能な可変式膨張弁によりなることを特徴とする請求項1乃至3のいずれかに記載の車両用空調装置。
- 前記空調ユニット内に配置されてダンパにより通風量が調整されると共に液体状熱媒体が内部を循環する第3の熱交換器と、前記液体状熱媒体を圧送するポンプと、前記液体状熱媒体と前記圧縮機から吐出した冷媒とを熱交換させる第4の熱交換器とを配管接続して構成された温水サイクルを備え、
前記第1の熱交換器を前記温水サイクルに置き換えたことを特徴とする請求項1乃至9のいずれかに記載の車両用空調装置。 - 前記圧縮機の吸入側の冷媒と前記第1の熱交換器の流出側の冷媒とを熱交換させる内部熱交換器を更に設けたことを特徴とする請求項1乃至9のいずれかに記載の車両用空調装置。
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EP (1) | EP2759424B1 (ja) |
JP (1) | JP5367186B2 (ja) |
WO (1) | WO2013035130A1 (ja) |
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Also Published As
Publication number | Publication date |
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EP2759424A1 (en) | 2014-07-30 |
EP2759424B1 (en) | 2017-04-19 |
US20140298837A1 (en) | 2014-10-09 |
EP2759424A4 (en) | 2016-04-20 |
JP5367186B2 (ja) | 2013-12-11 |
US9902235B2 (en) | 2018-02-27 |
JPWO2013035130A1 (ja) | 2015-03-23 |
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