JP5582080B2 - Cold storage air conditioner - Google Patents

Description

  The present invention relates to a cold storage type air conditioner having a plurality of evaporators corresponding to a plurality of spaces to be air-conditioned and having a cold storage function in at least one of the evaporators.

  Conventionally, by providing a cold storage material in an evaporator, the low temperature obtained when operating the refrigeration cycle apparatus is stored, and when the refrigeration cycle apparatus is stopped, a cold storage type air conditioner that uses the stored low temperature It has been known. For example, cold storage type air conditioners such as Patent Document 1 to Patent Document 6 are known.

JP 2009-184478 A JP 2009-229014 A JP 2009-298390 A JP 2010-91250 A Japanese Patent No. 4043776 Japanese Patent Laid-Open No. 10-157449

  Patent Literature 1, Patent Literature 2, and Patent Literature 3 disclose a cold storage type heat exchanger including a cold storage heat exchanger and an evaporator. However, application to an air conditioner that air-conditions a plurality of spaces such as a dual air conditioner is not disclosed. Moreover, in the structure described in these patent documents 1 thru | or patent document 3, both a cool storage heat exchanger and an evaporator will be provided corresponding to each of several space. For this reason, it was difficult to provide an inexpensive cold storage type air conditioner.

  Patent document 4 is disclosing the structure which air-conditions several space by a cool storage heat exchanger. However, in this configuration, a cold storage heat exchanger is provided for each of the spaces. This configuration has a problem in that two cold storage heat exchangers are required.

  Patent document 5 is disclosing the air conditioner which has a normal evaporator and the evaporator which can be stored cold. However, these two evaporators are arranged in parallel in one air guide duct. For this reason, a plurality of spaces cannot be air-conditioned.

  Patent Document 6 discloses an air conditioner having a normal evaporator and an evaporator capable of storing cold. Moreover, a normal evaporator is arranged corresponding to the cab, and an evaporator capable of storing cold is arranged corresponding to the nap room. However, in the apparatus disclosed in Patent Document 4, the nap room is only air-conditioned by an evaporator capable of storing cold while the refrigeration cycle apparatus is stopped. And even if the low temperature of the evaporator which can store cold disappears, a refrigerating cycle device is not restarted. For this reason, there is a problem that the room temperature cannot be lowered and the comfort is impaired.

  This invention is made | formed in view of the said problem, The objective is to provide the cool storage type | formula air conditioner which can provide comfortable air conditioning to several different space.

  Another object of the present invention is to provide a regenerative air conditioner that can provide comfortable air conditioning in a plurality of spaces with a relatively simple and inexpensive configuration.

  The present invention employs the following technical means to achieve the above object.

The invention described in claim 1 includes a compression device (11) that is temporarily stopped, and a cold storage material (17) that stores a low temperature, and cools the air with the refrigerant and cools the refrigerant when the compression device is in operation. The first evaporator (16, 316) that cools the material and cools the refrigerant and the air with the cold storage material when the compressor is stopped, and the first and second chambers that are different spaces A first blower (23) that blows air through one evaporator, a second evaporator (19, 319) that cools air with a refrigerant when the compressor is operating, and the other of the main chamber and the sub chamber And the second evaporator (24) for blowing air through the second evaporator and the second evaporator (19, 319) when the compression device is stopped, the first evaporator (16 316), a passage for forming a cooling passage through which the refrigerant flows. A temperature sensor (21) for detecting an index related to a blow-off temperature (TF) of air that is cooled by the first evaporator or the second evaporator and is supplied to a main room that is a main air-conditioning target. 25, 26) and restarting means (27a) for restarting the compression device when it is determined that the blowing temperature exceeds the upper limit temperature based on the index detected by the temperature sensor. .

  According to this configuration, even when the compressor is temporarily stopped, the first evaporator cools the air with the cold storage material and continues air conditioning. Further, when the compression device is temporarily stopped, the refrigerant in the first evaporator is cooled by the cold storage material. Thereby, a refrigerant | coolant flows into a 1st evaporator via a 2nd evaporator. For this reason, even when the compressor is temporarily stopped, the second evaporator can cool the air and continue air conditioning. Furthermore, an index related to the blowing temperature of the air supplied to the main room is detected, and when it is determined that the blowing temperature exceeds the upper limit temperature based on the index related to the blowing temperature, the compressor is restarted. The Thereby, it can avoid that the blowing temperature to a main room rises excessively and comfort is impaired. Further, it is avoided that the compression device is restarted in response to the increase in the temperature of the blowout into the sub chamber. Therefore, it is suppressed that the compressor is restarted with an excessive frequency. As a result, the advantage of temporarily stopping the compression device can be sufficiently obtained.

  The invention according to claim 2 is characterized in that the second evaporator is a normal evaporator having no cold storage material. According to this configuration, the air can be cooled by the second evaporator even when the compression apparatus is temporarily stopped without providing the cold storage material in the second evaporator. Therefore, comfortable air conditioning can be provided in a plurality of spaces with a simple and inexpensive configuration.

  The invention described in claim 3 is characterized in that it includes air volume suppression means (27b, 327b) for suppressing the air volume passing through the second evaporator when the compression device is stopped. According to this configuration, even when the compressor is temporarily stopped, an increase in the blowing temperature of the air cooled by the second evaporator can be suppressed. The second evaporator has no cold storage material. However, by suppressing the amount of air passing through the second evaporator, the blowing temperature of the air cooled by the second evaporator is changed to the blowing temperature of the air cooled by the first evaporator having the cold storage material. You can get closer.

  The invention according to claim 4 is characterized in that the air volume suppressing means (27b, 327b) suppresses the air volume passing through the second evaporator to be smaller than the air volume passing through the first evaporator. To do. According to this configuration, the amount of air passing through the second evaporator having no cold storage material is suppressed to be smaller than the amount of air passing through the first evaporator having the cold storage material. Therefore, the blowing temperature of the air cooled by the second evaporator can be brought close to the blowing temperature of the air cooled by the first evaporator.

  According to a fifth aspect of the present invention, the first evaporator and the second evaporator are connected in parallel to the compression device, and an expansion valve provided on the upstream side of the second evaporator ( 20), a bypass passage (21) as a passage forming means is provided in parallel. According to this configuration, even when the expansion valve provided on the upstream side of the second evaporator is closed when the compression device is stopped, the cooling passage can be formed by the bypass passage.

  According to a sixth aspect of the present invention, the first evaporator is disposed so as to cool the air blown into the front seat space of the vehicle, and the second evaporator is blown into the rear seat space of the vehicle. It is arranged to cool the air. According to this configuration, the front seat space can be air-conditioned by the first evaporator having the cold storage material. As a result, comfortable air conditioning can be provided in the front seat space of the vehicle.

  In the invention according to claim 7, the first evaporator is arranged to cool the air blown into the rear seat space of the vehicle, and the second evaporator is blown into the front seat space of the vehicle. It is arranged to cool the air. According to this configuration, the rear seat space can be air-conditioned by the first evaporator having the cold storage material. As a result, comfortable air conditioning can be provided in the rear seat space of the vehicle.

  The invention according to claim 8 is provided with switching means (527c) for selectively setting the space conditioned by the first evaporator and the space conditioned by the second evaporator as the main room. Features. According to this configuration, the main room can be selected in accordance with a user instruction. As a result, user convenience can be improved.

  The invention according to claim 9 is characterized in that the compression device is driven by an engine that is also a power source for traveling of the vehicle, and is temporarily stopped to stop the engine when the vehicle is temporarily stopped. And According to this configuration, even if the engine is temporarily stopped in order to save fuel consumption of the engine, the air conditioning in the vehicle interior can be continued. Furthermore, the fuel consumption saving effect due to idle stop can be brought out without impairing the comfort of the main room.

  Note that the reference numerals in parentheses described in the claims and the above-described means indicate the correspondence with the specific means described in the embodiments described later as one aspect, and are technical terms of the present invention. It does not limit the range.

It is a block diagram which shows the driving | running state of the multi-room air conditioning of the cool storage type air conditioner which concerns on 1st Embodiment to which this invention is applied. It is a block diagram which shows the operation state of the main room independent air conditioning of the cool storage type air conditioner which concerns on 1st Embodiment. It is a block diagram which shows the cool-down operation state of the cool storage type air conditioner which concerns on 1st Embodiment. It is a graph which shows the change of the blowing temperature of the cool storage type air conditioner which concerns on 1st Embodiment, 4A shows the operating state of a compressor, 4B shows the blowing temperature of a main chamber, 4C shows the blowing temperature of a subchamber. Show. It is a block diagram which shows the operation state of the main room independent air conditioning of the cool storage type air conditioner which concerns on 2nd Embodiment to which this invention is applied. It is a block diagram which shows the driving | running state of the multi-room air conditioning of the cool storage air conditioner which concerns on 3rd Embodiment to which this invention is applied. It is a block diagram which shows the driving | running state of the main room independent air conditioning of the cool storage type air conditioner which concerns on 3rd Embodiment. It is a block diagram which shows the cool-down operation state of the cool storage air conditioner which concerns on 3rd Embodiment. It is a graph which shows the change of the blowing temperature of the cool storage type air conditioner which concerns on 3rd Embodiment, 4A shows the operating state of a compressor, 4B shows the blowing temperature of a main chamber, 4C shows the blowing temperature of a subchamber. Show. It is a block diagram which shows the operating state of the main room independent air conditioning of the cool storage type | formula air conditioner which concerns on 4th Embodiment to which this invention is applied. It is a block diagram which shows the cool storage type air conditioner which concerns on 5th Embodiment to which this invention is applied.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.

(First embodiment)
FIG. 1 is a block diagram showing an operation state of multi-room air conditioning of a regenerative air conditioner 1 according to a first embodiment to which the present invention is applied. The regenerative air conditioner 1 is a vehicle air conditioner that air-conditions a passenger compartment. The regenerative air conditioner 1 is an air conditioner called a dual air conditioner that can air-condition different spaces set in the passenger compartment to different temperatures.

  The regenerative air conditioner 1 includes a refrigeration cycle apparatus 2 that cools at least air supplied to a space to be air-conditioned. The refrigeration cycle apparatus 2 constitutes a refrigeration cycle in which a refrigerant circulates by a plurality of devices and piping. The refrigeration cycle apparatus 2 includes a compression device 11 that sucks, compresses, and discharges refrigerant. The compressor 11 includes a compressor 12, a check valve 13, and an engine (ENG) 14. The compressor 12 sucks the refrigerant from the low pressure side of the refrigeration cycle, compresses it, and discharges it to the high pressure side. The check valve 13 is provided in the suction portion of the compressor 12. The check valve 13 prevents the refrigerant from flowing backward from the high pressure side to the low pressure side when the compressor 12 is stopped.

  The engine 14 is a power source for the compression device 11. The engine 14 drives the compressor 12 through a power transmission mechanism such as a belt mechanism. The engine 14 is also a power source for driving the vehicle. The compression device 11 may be temporarily stopped for idling stop of the engine 14 when the vehicle stops temporarily.

  The refrigeration cycle apparatus 2 includes a radiator 15 that radiates heat from the high-pressure refrigerant discharged from the compressor 11 and cools the refrigerant. When a condensable refrigerant is used as the refrigerant, the radiator 15 is also called a condenser.

  The refrigerant passage provided by the refrigeration cycle apparatus 2 includes a common passage portion in which the compressor 12 and the radiator 15 are disposed, and a plurality of parallel passages provided in parallel to the common passage portion. Yes. The refrigerant passage provided by the refrigeration cycle apparatus 2 is branched into a plurality of parallel passages downstream of the radiator 15. An evaporator is provided in each of the plurality of parallel passages. The plurality of parallel passages are joined downstream of the evaporator. The joined passage communicates with the compression device 11.

  A cold storage evaporator 16 is provided in the first parallel passage. The cold storage evaporator 16 is also called a first evaporator. The cold storage evaporator 16 includes a refrigerant passage and an air passage. The regenerator evaporator 16 provides heat exchange between the refrigerant and air. Further, the cold storage evaporator 16 includes a cold storage material 17 for storing a low temperature. The cold storage material 17 is provided so as to be able to exchange heat directly and / or indirectly with the refrigerant flowing through the passage. The cold storage material 17 is provided so as to be able to exchange heat directly and / or indirectly with the air flowing through the passage. The cold storage material 17 is provided so as to be cooled by exchanging heat with the refrigerant. The cold storage material 17 is provided so as to cool both the refrigerant and the air at a low temperature by exchanging heat directly and / or indirectly with both the refrigerant and the air. The cold storage evaporator 16 cools the air with the refrigerant when the compressor 11 is in operation, and stores the cold in the cold storage material 17. The cold storage evaporator 16 cools the refrigerant and air by the cold storage material 17 when the compression device 11 is stopped. Regarding the structure of the cold storage evaporator 16, the structure disclosed in Patent Document 4 (Japanese Patent Application Laid-Open No. 2010-91250) can be adopted, and the description thereof can be introduced by reference.

  The cold storage evaporator 16 is arranged so as to exchange heat with the main air-conditioned space in the passenger compartment, that is, air supplied to the main compartment. The main room is a driver seat space or a passenger seat space in the passenger compartment. In this embodiment, the main room is a driver seat space, that is, a front seat space. Therefore, the cold storage evaporator 16 is also a main room evaporator that air-conditions the front seat space which is the main room.

  The refrigeration cycle apparatus 2 includes an expansion valve 18 between the cold storage evaporator 16 and the radiator 15. The expansion valve 18 adjusts the refrigerant flow rate so as to maintain the refrigerant superheat degree at the outlet portion of the cold storage evaporator 16 at an appropriate value. The expansion valve 18 can be provided by a temperature sensitive expansion valve. When the compressor 12 stops, the pressure on the suction side of the compressor 12 increases. For this reason, when the compressor 12 stops, the expansion valve 18 is automatically closed.

  A normal evaporator 19 is provided in the second parallel passage. The evaporator 19 is also called a second evaporator. The evaporator 19 does not have a cold storage material. The evaporator 19 cools the air with the refrigerant when the compressor 11 is operated. The cold storage evaporator 16 is specially designed to include the cold storage material 17. However, the evaporator 19 is also used in other types of air conditioners that are widely installed in many vehicles. This configuration contributes to providing an inexpensive refrigeration cycle apparatus 2.

  The evaporator 19 is disposed so as to exchange heat with air supplied to a preliminary conditioned space in the passenger compartment, that is, the sub-chamber. The sub-room may be a passenger seat space in the passenger compartment, or a rear seat space, and / or a storage space such as a beverage. In this embodiment, the sub chamber is a rear seat space. Therefore, the evaporator 19 is also a sub-chamber evaporator that air-conditions the rear seat space that is the sub-chamber.

  The refrigeration cycle apparatus 2 includes an expansion valve 20 between the evaporator 19 and the radiator 15. The expansion valve 20 adjusts the refrigerant flow rate so as to maintain the refrigerant superheat degree at the outlet portion of the evaporator 19 at an appropriate value. The expansion valve 20 can be provided by a temperature sensitive expansion valve. The refrigeration cycle apparatus 2 includes a bypass passage 21 that is provided in parallel with the expansion valve 20 and allows the refrigerant to flow even when the expansion valve 20 is closed. The bypass passage 21 can be provided by a bleed port that communicates the upstream and downstream of the valve portion of the expansion valve 20.

  The bypass passage 21 and the members that partition the bypass passage 21 are passage forming means that form a cooling passage through which the refrigerant flows into the cold storage evaporator 16 via the evaporator 19 when the compression device 11 is stopped. The cold storage evaporator 16 and the normal evaporator 19 are connected in parallel to the compressor 11. An expansion valve 20 is provided on the upstream side of the evaporator 19 so as to be in series with only the ordinary evaporator 19. The expansion valve 20 is provided with a bypass passage 21 as a passage forming means in parallel. According to this configuration, even when the expansion device 20 provided on the upstream side of the evaporator 19 is closed when the compressor 11 is stopped, the cooling passage can be formed by the bypass passage 21.

  The refrigeration cycle apparatus 2 includes a solenoid valve 22 in the second parallel passage. The solenoid valve 22 can intermittently flow the refrigerant in the second parallel passage. Therefore, when the electromagnetic valve 22 is open, the refrigerant flows through the second parallel passage and the evaporator 19 provided there. On the other hand, when the electromagnetic valve 22 is closed, the refrigerant does not flow through the second parallel passage and the evaporator 19 provided there.

  The cold storage type air conditioner 1 includes a blower 23 that blows air through the cold storage evaporator 16 toward the main room. The regenerative air conditioner 1 includes a blower 24 that blows air through the evaporator 19 toward the sub chamber. The cold storage air conditioner 1 includes a temperature sensor 25 provided downstream of the cold storage evaporator 16. The temperature sensor 25 is means for detecting the temperature of the air cooled by the cold storage evaporator 16. Moreover, the temperature of the air cooled by the cool storage evaporator 16 also affects the blowing temperature to the main chamber. Particularly during cooling, the blowing temperature is substantially proportional to the temperature of the air cooled by the cold storage evaporator 16. Therefore, the temperature sensor 25 is also a means for detecting an index related to the temperature of the air blown into the main room. The regenerator air conditioner 1 includes a temperature sensor 26 provided downstream of the evaporator 19. The temperature sensor 26 is means for detecting the temperature of the air cooled by the evaporator 19. Moreover, the temperature of the air cooled by the evaporator 19 also affects the blowing temperature to the sub chamber. Particularly during cooling, the blowing temperature is approximately proportional to the temperature of the air cooled by the evaporator 19. Therefore, the temperature sensor 26 is also a means for detecting an index related to the temperature at which air is blown into the sub chamber.

  The regenerative air conditioner 1 includes an air conditioning control unit (ACU) 27. The air conditioning control device 27 controls the regenerative air conditioner 1 by inputting signals from detection means such as a plurality of sensors and switches in the regenerative air conditioner 1 and outputting control signals to driving means such as a plurality of electric devices. To do. The air conditioning control device 27 inputs signals indicating the blowing temperature from the temperature sensors 25 and 26. Here, the temperature sensor 25 detects the blowing temperature TF of the air cooled by the cold storage evaporator 16 and supplied to the main room that is the main air conditioning target. The air conditioning control device 27 inputs signals indicating the operation and stop of the compressor 12 from the compressor 11. The air conditioning control device 27 outputs control signals to at least the compression device 11, the electromagnetic valve 22, and the blower 24. Furthermore, the air-conditioning control device 27 controls the blower 23, the hot water heating device for the main room (not shown), and the hot water heating device for the sub chamber.

  The air-conditioning control device 27 includes restarting means (RSM) 27 a that instructs the compression device 11 to restart in response to the blowout temperature TF to the main room detected by the temperature sensor 25. When the restarting means 27a determines that the blowing temperature TF exceeds the upper limit temperature based on the index related to the blowing temperature TF, the compressor 11 is restarted. Specifically, when the blowing temperature TF exceeds a predetermined threshold temperature, the compressor 11 is restarted. The restart of the compression device 11 is executed by restarting the engine 14. Instead of this, the restart of the compressor 11 may be executed by reconnection of the power transmission mechanism between the engine 14 and the compressor 12. In this embodiment, the air conditioning control device 27 does not command the restart of the compression device 11 in response to the blowout temperature TR to the sub chamber detected by the temperature sensor 26.

  Furthermore, the air-conditioning control device 27 includes air volume suppression means (VRM) 27b that suppresses the air volume passing through the evaporator 19 during the period of the cooling operation. The air volume suppression means 27b controls the blower 24 so as to suppress the air volume during the period when the compressor 12 is stopped to an amount smaller than the normal air volume. The normal air volume is, for example, an air volume set according to the air conditioning heat load of the sub chamber. The air volume suppression means 27b suppresses the air volume during the period when the compressor 12 is stopped (the air volume in the operation state of FIG. 3) to an amount smaller than the normal air volume (the air volume in the operation state of FIG. 1). The blower 24 can be controlled. When the compressor 12 is stopped for the idle stop control when the multi-chamber air conditioning is selected, the air volume suppression unit 27b is configured such that the air volume passing through the evaporator 19 is greater than the air volume passing through the cold storage evaporator 16. The blowers 23 and 24 are controlled to be small. According to this configuration, the amount of air passing through the evaporator 19 having no cold storage material 17 is suppressed to be smaller than the amount of air passing through the cold storage evaporator 16 having the cold storage material 17. Therefore, the blowing temperature of the air cooled by the evaporator 19 can be brought close to the blowing temperature of the air cooled by the cold storage evaporator 16.

  The engine 14 is automatically stopped and automatically restarted in order to suppress fuel consumption. For example, when the vehicle stops at a traffic signal, the engine 14 is automatically stopped and automatically restarted by a predetermined operation of the driver. Such engine control is also called, for example, idle stop control and idling stop and start control. Such automatic stop / restart control of the engine 2 is executed by an engine control unit (ECU) 28. Therefore, the engine control device 28 provides stop means for automatically stopping the compression device 11. Further, when the engine 14 is restarted in response to a command from the restarting means 27a, the engine control device 28 functions as part of the restarting means 27a.

  The control devices 27 and 28 are provided by a microcomputer provided with a computer-readable storage medium. The storage medium stores a computer-readable program. The storage medium can be provided by a memory. By being executed by the control device, the program causes the control device to function as the device described in this specification, and causes the control device to function so as to execute the control method described in this specification. The means provided by the control device can also be called a functional block or module that achieves a predetermined function.

  In FIG. 1, the refrigerant flow and the air flow when air-conditioning both the main chamber and the sub chamber by operating the compressor 11 are illustrated by arrows. At this time, the refrigerant is decompressed by the expansion valve 18 and evaporated in the cold storage evaporator 16. As a result, the refrigerant cools the air supplied to the driver's seat space and cools the cold storage material 17. As a result, the main room is air-conditioned and cold temperature is stored in the cold storage material 17. On the other hand, the refrigerant that has passed through the opened electromagnetic valve 22 is decompressed by the expansion valve 20 and evaporated in the evaporator 19. As a result, the refrigerant cools the air supplied to the rear seat space. Thereby, a subchamber is air-conditioned. The illustrated operating state is referred to as a first cold storage operation state in which both the main room and the sub-room are air-conditioned and stored in the cold storage material 17.

  The cold storage evaporator 16 is arranged to cool the air blown into the front seat space of the vehicle, and the normal evaporator 19 is arranged to cool the air blown into the rear seat space of the vehicle. . According to this configuration, the front seat space can be air-conditioned by the cold storage evaporator 16 having the cold storage material. As a result, comfortable air conditioning can be provided in the front seat space of the vehicle.

  FIG. 2 is a block diagram showing an operating state of the main room single air conditioning of the cold storage type air conditioner according to the first embodiment. In the figure, the refrigerant flow and the air flow when only the main room is air-conditioned by operating the compressor 11 are indicated by arrows. At this time, the refrigerant is decompressed by the expansion valve 18 and evaporated in the cold storage evaporator 16. As a result, the refrigerant cools the air supplied to the driver's seat space and cools the cold storage material 17. As a result, the main room is air-conditioned and cold temperature is stored in the cold storage material 17. On the other hand, the electromagnetic valve 22 is closed. The blower 24 is stopped. As a result, neither refrigerant nor air flows through the evaporator 19. The illustrated operating state is referred to as a second cold storage operation state in which only the main room is air-conditioned and the cold storage material 17 is stored cold. The main room is the driver's seat space. For this reason, the refrigeration cycle apparatus 2 is often operated to air-condition the main room. In this embodiment, since the cold storage evaporator 16 is provided corresponding to the main room, the cold storage material 17 has many chances of cold storage.

  FIG. 3 is a block diagram illustrating a cooling operation state of the regenerative air conditioner according to the first embodiment. At this time, the compression device 11 is stopped. The air conditioning control device 27 provides the illustrated operating state during a period in which the engine 14 is automatically stopped temporarily by the engine control device 28 and the compressor 12 is stopped. At this time, in the cold storage evaporator 16, the air passing therethrough is cooled by the cold temperature stored in the cold storage material 17. As a result, the cool storage material 17 cools the air supplied to the driver's seat space. Thereby, the main room is air-conditioned.

  On the other hand, since the cold storage material 17 tries to maintain the cold storage evaporator 16 at a low temperature, the refrigerant condenses in the cold storage evaporator 16. As a result, the inside of the cold storage evaporator 16 is reduced in pressure, and the refrigerant in the refrigeration cycle apparatus 2 is sucked into the cold storage evaporator 16. The refrigerant flows from the high-pressure portion of the refrigeration cycle apparatus 2 into the cold storage evaporator 16 via the electromagnetic valve 22, the bypass passage 21, and the evaporator 19. At this time, the refrigerant flowing through the evaporator 19 evaporates and maintains the evaporator 19 at a low temperature. Even in a state where the compression device 11 is stopped, the evaporator 19 cools the air supplied to the sub chamber for a time corresponding to the amount of cold stored in the cold storage material 17. The illustrated operating state is referred to as a cooling operation state in which both the main room and the sub chamber are air-conditioned by allowing the cool storage material 17 to cool.

  FIG. 4 is a graph showing changes in the blowing temperature of the cold storage type air conditioner 1 according to the first embodiment. FIG. 4A shows the operating state of the compressor 11. FIG. 4B shows the blowing temperature TF of the main room. FIG. 4C shows the outlet temperature TR of the sub chamber. The horizontal axis is time. In the ON state in which the compressor 12 is operated, the blowing temperatures TF and TR are maintained at a low temperature.

  When the vehicle temporarily stops at time t1, the engine control device 28 automatically stops the engine 14 for idle stop control. As a result, the compressor 12 is also stopped and turned off. In the OFF state, the air conditioning control device 27 operates the cold storage air conditioning device 1 in the cooling operation state of FIG. At this time, the expansion valve 18 closes the passage in response to an increase in the low pressure due to the stop of the compressor 12. As a result, the expansion valve 18 provides a blocking means for blocking direct communication from the downstream of the radiator 15 to the cold storage evaporator 16. As a result, the cold storage material 17 gradually cools. From time t1, the blowing temperature TF gradually increases as shown by the solid line. However, since there is a cooling effect by the cold storage material 17, it does not rise rapidly as shown by the broken line. As a result, the blowing temperature TF can be maintained below the upper limit temperature TH set as the predetermined threshold temperature in a long period of the period in which the vehicle is temporarily stopped.

  The upper limit temperature TH is a temperature at which the vehicle occupant clearly senses an increase in temperature by the skin temperature sensation and complains of discomfort during cooling operation. For example, the upper limit temperature during cooling can be set to about + 15 ° C.

  On the other hand, from time t1, the blowout temperature TR of the sub chamber gradually increases. At this time, the refrigerant flows from the high-pressure side of the refrigeration cycle apparatus 2 through the evaporator 19 into the cold storage evaporator 16. Accordingly, the refrigerant also flows through the evaporator 19 and slightly evaporates. For this reason, the blowing temperature TR does not rise rapidly as shown by the broken line. The air volume suppression means 27b controls the blower 24 so as to suppress the air volume during the period when the compressor 12 is stopped to an amount smaller than the normal air volume. If the normal air volume is supplied while the compressor 12 is stopped, the blowout temperature TR rises rapidly as indicated by a one-dot chain line. However, by suppressing the air volume, the increase in the blowing temperature TR becomes even slower as illustrated by the solid line. As a result, it is possible to maintain the blowing temperature TR below the predetermined upper limit temperature TH during a long period of the period in which the vehicle is temporarily stopped.

  Here, the air-conditioning control device 27 can include an air volume suppression unit that controls the blower 24 so that the air volume passing through the evaporator 19 becomes a predetermined air volume. The suppressed predetermined air volume can be fixed. Further, the suppressed predetermined air volume can be made variable. For example, it can be several tens of percent of the normal air volume. Moreover, the air-conditioning control apparatus 27 can be equipped with the air volume control means which controls the air blower 24 so that the raise of blowing temperature TR may be suppressed to the same extent as the raise of blowing temperature TF.

  Eventually, at time t2, the main room blowing temperature TF reaches the upper limit temperature TH. The restarting means 27a of the air conditioning control device 27 constitutes a detecting means for detecting that the air outlet temperature TF in the main room has reached the upper limit temperature TH. Furthermore, the restarting means 27a restarts the compression device 11 when the blowing temperature TF reaches the upper limit temperature TH. Here, the compressor 12 is restarted by restarting the engine 14. Thereby, it will be in the ON state in which the compressor 12 is drive | operated again. As a result, a sufficient amount of refrigerant is supplied to the cold storage evaporator 16 and the evaporator 19, and the blowing temperatures TF and TR are lowered toward a lower temperature.

  According to this embodiment, the cold storage evaporator 16 was provided corresponding to the main room. Thereby, even when the compression apparatus 11 is stopped temporarily, the cool storage evaporator 16 cools air with the cool storage material 17, and continues air conditioning. Moreover, the evaporator 19 was provided corresponding to the subchamber. Further, the refrigeration cycle apparatus 2 is configured so that the refrigerant also flows through the evaporator 19 during the cooling operation in the cold storage evaporator 16. Specifically, a refrigerant cooling passage that can reach the cold storage evaporator 16 from the high-pressure side of the refrigeration cycle apparatus 2 via the evaporator 19 when the compressor 12 is stopped is formed. This passage includes a bypass passage 21. When the compressor 11 is temporarily stopped, the refrigerant in the cold storage evaporator 16 is cooled by the cold storage material 17. Thereby, the refrigerant flows to the cold storage evaporator 16 via the evaporator 19. For this reason, even when the compressor 11 is temporarily stopped, the evaporator 19 can cool the air and continue the air conditioning. Such a configuration makes it possible to provide comfortable air conditioning in a plurality of spaces with a relatively inexpensive configuration.

  Further, the compressor 11 is restarted in response to the blowout temperature TF of the main room. That is, the compression apparatus 11 is not restarted in response to the increase in the blowing temperature TR caused by the evaporator 19. For this reason, the excessive restart of the compression apparatus 11 can be suppressed. In addition, when the blowing temperature TF reaches the upper limit temperature TH, the compressor 11 is restarted. Therefore, comfortable air conditioning can be provided to the main room. Even if the engine 14 is temporarily stopped in order to save fuel consumption of the engine 14, the air conditioning in the vehicle interior can be continued. Furthermore, the fuel consumption saving effect due to idle stop can be brought out without impairing the comfort of the main room.

  Further, in the cooling operation, an increase in the temperature TR blown into the sub chamber is suppressed by suppressing the amount of air blown into the sub chamber. For this reason, even if the normal evaporator 19 is used to air-condition the sub chamber, it is possible to avoid a rapid rise in the blowing temperature TR. As a result, rapid deterioration of the temperature sensation can be suppressed even in the sub chamber.

(Second Embodiment)
FIG. 5 is a block diagram showing an operating state of the main room single air conditioning of the cold storage type air conditioner according to the second embodiment to which the present invention is applied. In the preceding embodiment, in the operation state for the main room alone, the solenoid valve 22 was closed to cut off the refrigerant supply to the evaporator 19. Instead of this, a configuration without the electromagnetic valve 22 may be employed. In this embodiment, the air conditioning control device 27 stops the blower 24 in the operation state for the main room alone. For this reason, the subchamber is not air-conditioned. However, since the solenoid valve 22 is not provided, the refrigerant flows into the evaporator 19 even in this operation state.

(Third embodiment)
FIG. 6 is a block diagram showing an operation state of the multi-room air conditioning of the cold storage type air conditioner 1 according to the third embodiment to which the present invention is applied. FIG. 7 is a block diagram showing an operating state of the main room single air conditioning of the cold storage type air conditioner 1 according to the third embodiment. FIG. 8 is a block diagram illustrating a cooling operation state of the regenerative air conditioner 1 according to the third embodiment. FIG. 9 is a graph showing changes in the blowing temperature of the cold storage type air conditioner according to the third embodiment. FIG. 9A shows the operating state of the compression device 11. FIG. 9B shows the blowing temperature TF of the main room. FIG. 9C shows the outlet temperature TR of the sub chamber.

  In the preceding embodiment, the cold storage evaporator 16 is provided corresponding to the main room. Instead, in this embodiment, the refrigeration cycle apparatus 2 includes a normal evaporator 319 corresponding to the main chamber. The refrigeration cycle apparatus 2 includes a cold storage evaporator 316 corresponding to the sub chamber. The cold storage evaporator 316 is arranged to cool the air blown into the rear seat space of the vehicle, and the normal evaporator 319 is arranged to cool the air blown into the front seat space of the vehicle. . According to this configuration, the rear seat space can be air-conditioned by the cold storage evaporator 316 having the cold storage material. As a result, comfortable air conditioning can be provided in the rear seat space of the vehicle.

  Also in this embodiment, the air-conditioning control device 27 includes restarting means 27a that restarts the compression device 11 in response to the blowing temperature TF to the main room. The air-conditioning control device 27 includes air volume suppression means 327b that suppresses the air volume passing through the evaporator 319 during the period of the cooling operation. According to this embodiment, the restart of the compressor 11 is executed in response to the blowing temperature TF of the air cooled by the normal evaporator 319 provided corresponding to the main chamber. Specifically, when the blowing temperature TF exceeds a predetermined upper limit temperature, the compression device 11 is restarted. Also in this embodiment, the blower 23 is controlled so that the air volume sent to the main room is suppressed by the air volume suppression means 327b. For this reason, the rise of the blowing temperature TF to the main room is suppressed slowly. Since the rise of the blowing temperature TF is slow, it is difficult for the passengers in the main room to feel the rise in the blowing temperature. In other words, it becomes difficult for the passengers in the main room to sense the deterioration of the temperature sensation, that is, the deterioration of the cooling feeling. As a result, comfortable air conditioning can be provided to the main room. On the other hand, in the sub chamber, the cool storage evaporator 316 sufficiently cools the air. Therefore, comfortable air conditioning can also be provided to the sub room.

  According to this embodiment, the cold storage evaporator 316 is provided corresponding to the sub chamber, and the evaporator 319 is provided corresponding to the main chamber. Furthermore, the refrigeration cycle apparatus 2 was configured such that the refrigerant also flows through the evaporator 319 during the cooling operation in the cold storage evaporator 316. Specifically, when the compressor 12 is stopped, a refrigerant cooling passage that can reach the cold storage evaporator 316 from the high pressure side via the evaporator 319 is formed. This passage includes a bypass passage 21. Such a configuration makes it possible to provide comfortable air conditioning in a plurality of spaces with a relatively inexpensive configuration.

  Further, the compressor 11 is restarted in response to the blowout temperature TF of the main room. In other words, the compressor 11 is not restarted in response to the increase in the blowing temperature TR caused by the cold storage evaporator 316 in the sub chamber. For this reason, the excessive restart of the compression apparatus 11 can be suppressed and the effect of energy saving can fully be drawn out. In addition, when the blowing temperature TF reaches the upper limit temperature TH, the compressor 11 is restarted. Therefore, comfortable air conditioning can be provided to the main room.

  Furthermore, in the cooling operation, an increase in the temperature TF to the main room is suppressed by suppressing the amount of air blown into the main room. For this reason, even if the normal evaporator 319 is used for air-conditioning the main room, a rapid rise in the blowing temperature TF can be avoided. As a result, rapid deterioration of the temperature sensation can be suppressed even in the main room.

(Fourth embodiment)
FIG. 10: is a block diagram which shows the operation state of the main room independent air conditioning of the cool storage type air conditioner which concerns on 4th Embodiment to which this invention is applied. In the previous embodiment, in the operation state for the main room alone, the solenoid valve 22 was closed to cut off the refrigerant supply to the cold storage evaporator 316. Instead of this, a configuration without the electromagnetic valve 22 may be employed. In this embodiment, the air conditioning control device 27 stops the blower 24 in the operation state for the main room alone. For this reason, the subchamber is not air-conditioned. However, since the solenoid valve 22 is not provided, the refrigerant flows through the cold storage evaporator 316 even in this operation state. Therefore, at this time, the cold storage material 17 and the refrigerant exchange heat without air-conditioning the sub chamber, and the low temperature is stored in the cold storage material 17.

(Fifth embodiment)
FIG. 11 is a block diagram showing a cold storage type air conditioner according to a fifth embodiment to which the present invention is applied. In the preceding embodiment, the front seat space of the passenger compartment is the main room. Instead of this, the space that is air-conditioned by the cold storage evaporator 16 and the space that is air-conditioned by the evaporator 19 may be switched so as to be selectively set in the main room.

  In the illustrated example, a changeover switch 527c is provided. The changeover switch 527c switches the signal input to the restarting means 27a between the temperature sensor 25 and the temperature sensor 26. Thereby, the restarting means 27 restarts the compression apparatus 11 in response to either the temperature sensor 25 or the temperature sensor 26 selected by the changeover switch 527c. For example, when the temperature sensor 25 is selected by the changeover switch 527c, the restarting unit 27 sets the front seat space as the main room, and restarts the compressor 11 when the blowout temperature TF reaches the upper limit temperature TH. To do. At this time, the air volume suppression means 27b suppresses the air volume that passes through the normal evaporator 19. Further, when the temperature sensor 26 is selected by the changeover switch 527c, the restarting unit 27 sets the rear seat space as the main room, and restarts the compressor 11 when the blowout temperature TR reaches the upper limit temperature TH. To do. At this time, the temperature sensor 26 detects the blowing temperature TR of the air cooled by the evaporator 19 and supplied to the main room which is the main air conditioning target. Also at this time, the air volume suppression means 27b suppresses the air volume passing through the normal evaporator 19.

  The changeover switch 527c can also be referred to as a priority switch that designates a space where priority should be given to maintaining comfort by air conditioning. The restarting means 27 restarts the compressor 11 so that the blowing temperature to the designated air-conditioned space is maintained below the upper limit temperature TH. The changeover switch 527c provides a switching means for selectively setting a space conditioned by the cold storage evaporator 16 and a space conditioned by the normal evaporator 19 as a main room. According to this configuration, the main room can be selected in accordance with a user instruction. As a result, user convenience can be improved.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention. The structure of the said embodiment is an illustration to the last, Comprising: The scope of the present invention is not limited to the range of these description. The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

  For example, in the said embodiment, the cool storage evaporator and the normal evaporator were arrange | positioned in parallel in the refrigerating cycle. Instead of this, the cold storage evaporator and the normal evaporator may be arranged in series in the refrigeration cycle. Moreover, in the said embodiment, although the engine 14 was used as a motive power source, you may use an electric motor. Moreover, in the said embodiment, the refrigerating-cycle apparatus 2 provided only the freezing operation. Instead of this, a refrigeration cycle apparatus capable of both refrigeration operation and heat pump operation may be employed. In addition, the refrigeration cycle apparatus 2 can include a receiver and / or an accumulator that stores the refrigerant.

  Moreover, in 3rd Embodiment, you may employ | adopt the structure which is not provided with the air volume suppression means 327b. In this case, the blowing temperatures TF and TR change as shown by a one-dot chain line in FIG. In this configuration, the amount of air passing through the evaporator 319 is not suppressed. Therefore, the blowing temperature TF rises faster than the blowing temperature TR. When the blowing temperature TF eventually exceeds the upper limit temperature TH at time t12, the compressor 11 is restarted. Also in this configuration, it is possible to maintain both the main room blow temperature TF and the sub chamber blow temperature TR below the upper limit temperature TH while suppressing an excessive rise in the main room blow temperature TF.

  Moreover, in the said embodiment, the temperature of the air immediately after the evaporator which is also a parameter | index which shows the cooling state by an evaporator was employ | adopted as a parameter | index relevant to blowing temperature. It can replace with this and the various parameter | index which can determine that blowing temperature exceeds upper limit temperature is employable. For example, the temperature of the surface of a cold storage evaporator or a normal evaporator may be adopted as an index related to the blowing temperature. In this case, the surface temperature of the evaporator can be detected by a temperature sensor provided on the surface of the heat exchange fin or a temperature sensor provided on the surface of the refrigerant tube. Moreover, you may employ | adopt the low pressure of the refrigerant | coolant inside an evaporator as a parameter | index relevant to blowing temperature. In this case, the low pressure can be detected by a pressure sensor that detects the refrigerant pressure in the low pressure pipe in the evaporator or downstream of the evaporator. Moreover, you may employ | adopt the temperature of the refrigerant | coolant in the inside of an evaporator, or the temperature of a cool storage material as a parameter | index relevant to blowing temperature. In this case, the refrigerant temperature can be detected by a temperature sensor that detects the refrigerant temperature at a representative position inside the evaporator. Moreover, the temperature of the cool storage material can be detected by a temperature sensor that detects the temperature of the cool storage material.

  For example, the means and functions provided by the control device can be provided by software only, hardware only, or a combination thereof. For example, the control device may be configured by an analog circuit.

DESCRIPTION OF SYMBOLS 1 Cold storage type air conditioner 2 Refrigeration cycle apparatus 11 Compressor 12 Compressor 13 Check valve 14 Engine 15 Radiator 16 Cold storage evaporator 17 Cold storage material 18 Expansion valve 19 Evaporator 20 Expansion valve 21 Bypass passage 22 Electromagnetic valve 23 Blower 24 Blower Reference Signs List 25 temperature sensor 26 temperature sensor 27 air conditioning control device 27a restarting means 27b air volume suppression means 28 engine control device 316 cool storage evaporator 319 evaporator 327b air volume suppression means 527c changeover switch

Claims (9)

A compression device (11) temporarily stopped;
A cold storage material (17) for storing a low temperature is provided, air is cooled by the refrigerant when the compressor is operated, and is stored in the cold storage material, and the refrigerant is stored by the cold storage material when the compressor is stopped. And a first evaporator (16, 316) for cooling the air;
A first blower (23) for blowing air through the first evaporator to one of a main chamber and a sub chamber which are different spaces;
A second evaporator (19, 319) that cools the air with a refrigerant when the compressor is in operation;
A second blower (24) for blowing air through the second evaporator to the other of the main chamber and the sub chamber;
Passage formation that forms a cooling passage through which refrigerant flows to the first evaporator (16, 316) via the second evaporator (19, 319) when the compression device is stopped Means (21);
The cooled by the first evaporator or the second evaporator, a sensor (25, 26) for detecting an indication related to blowing temperature (TF) of the air supplied to the main chamber which is a main air conditioning target ,
A regenerative air conditioner comprising: restarting means (27a) for restarting the compression device when it is determined that the blowing temperature exceeds an upper limit temperature based on the index detected by the sensor.   The regenerative air conditioner according to claim 1, wherein the second evaporator is a normal evaporator not having the regenerator material.   3. The regenerative air conditioner according to claim 2, further comprising an air volume suppression unit (27 b, 327 b) that suppresses an air volume that passes through the second evaporator when the compression apparatus is stopped.   The said air volume suppression means (27b, 327b) suppresses the air volume which passes through the said 2nd evaporator so that it may become smaller than the air volume which passes through the said 1st evaporator. Cold storage air conditioner.   The first evaporator and the second evaporator are connected in parallel to the compressor, and in parallel with an expansion valve (20) provided on the upstream side of the second evaporator. The regenerative air conditioner according to any one of claims 1 to 4, wherein a bypass passage (21) is provided as the passage forming means. The first evaporator is arranged to cool the air blown into the front seat space of the vehicle,
The regenerative air conditioner according to any one of claims 1 to 5, wherein the second evaporator is arranged to cool air blown into a rear seat space of the vehicle. The first evaporator is arranged to cool the air blown into the rear seat space of the vehicle,
The regenerative air conditioner according to any one of claims 1 to 5, wherein the second evaporator is disposed so as to cool air blown into a front seat space of the vehicle.   The switching means (527c) for selectively setting the space conditioned by the first evaporator and the space conditioned by the second evaporator in the main room is provided. The regenerative air conditioner according to claim 7.   The compressor is driven by an engine that is also a power source for traveling of the vehicle, and is temporarily stopped for an idle stop of the engine when the vehicle is temporarily stopped. The cold storage type air conditioner according to claim 8.

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