JP2014196863A - Evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an evaporator arranged in a refrigeration cycle in which a compressor is controlled to be turned on or off, and capable of preventing the generation of odor resulting from a response delay of a temperature sensor as much as possible.SOLUTION: An evaporator 6 arranged in a steam compression refrigeration cycle 2 in which a compressor 3 is turned on or off on the basis of a temperature sensor 12 that detects a downstream temperature of the evaporator 6, and cooling air flowing outside with a refrigerant flowing in the evaporator 6 when the compressor 3 is turned on, comprises a cold storage agent. The cold storage agent has a freezing point in a temperature range equal to or higher than a temperature exceeding a water freezing temperature and lower than a temperature at which condensed water adhering to the evaporator 6 is evaporated and dried.

Description

  The present invention relates to an evaporator disposed in a refrigeration cycle in which a compressor is on / off controlled.

  The evaporator disposed in the vapor compression refrigeration cycle cools the air by exchanging heat between the refrigerant inside and the air passing outside. During this cooling, water in the air condenses and adheres to the surface of the evaporator as condensed water. When this condensed water freezes, the heat exchange performance between the refrigerant and the air decreases. For this reason, the temperature downstream of the evaporator is detected by a temperature sensor, and the compressor is controlled on and off (for example, off temperature: 3 ° C., on temperature: 5 ° C.) according to the detected temperature to prevent the evaporator from freezing. .

  However, when the rate of decrease in temperature on the downstream side of the evaporator is fast, a response delay of the temperature sensor occurs as shown in FIG. If this response delay is large, the compressor will not turn off even if the actual temperature downstream of the evaporator reaches the off temperature, so-called undershoot occurs, and the evaporator freezes or burnt odor due to water freezing. Occur.

  In order to solve such a problem, there is a conventional example disclosed in Patent Document 1. In this conventional example, a temperature sensor that detects a temperature downstream of the evaporator, a compressor that is turned on / off by a thermo switch, and a thermoswitch operating set temperature according to the slow speed of the evaporator downstream temperature detected by the temperature sensor. And a control unit having a circuit for correcting.

  According to the above conventional example, when the rate of decrease in the temperature on the downstream side of the evaporator is fast, the control unit raises the operating set temperature of the thermoswitch and turns off the compressor at a higher temperature. This prevents a delay in the compressor off timing caused by a response delay of the temperature sensor, and thus prevents the evaporator from freezing. In order to prevent the evaporator from freezing, the generation of a burning odor due to freezing of water can be prevented.

  Patent Document 2 discloses a configuration in which the evaporator is prevented from freezing and the generation of a burning odor due to water freezing is prevented by the correction circuit of the control unit.

Japanese Utility Model Publication No. 3-43047 JP 2007-99072 A

  However, the conventional example has a problem that a circuit for correcting the operation set temperature of the thermoswitch in accordance with the changing speed of the temperature downstream of the evaporator detected by the temperature sensor is required.

  In addition, in an evaporator of a vapor compression refrigeration cycle that controls the compressor on / off, a odor (so-called steamy odor) is generated not only when the evaporator is frozen, but also when the condensed water adhering to the evaporator surface evaporates. There is a request to prevent this odor.

  Accordingly, the present invention has been made to solve the above-described problems, and is provided in a refrigeration cycle in which a compressor is controlled to be turned on / off, and the generation of odor due to a response delay of a temperature sensor is minimized. An object is to provide an evaporator that can be prevented.

  The present invention is arranged in a refrigeration cycle in which a compressor is turned on and off based on a temperature sensor that detects a temperature downstream of the evaporator, and when the compressor is turned on, an evaporator that cools air that flows through the inside of the refrigerant and flows outside. And having a cold storage agent, the cold storage agent having a freezing point in a range of a temperature higher than the freezing temperature of water and less than the temperature at which condensed water adhering to the evaporator surface evaporates and dries. It is a featured evaporator.

  The freezing point of the regenerator may be in the range between the off temperature and the on temperature of the compressor.

  The freezing point of the regenerator may be in the range of (A−a) ° C. to A ° C., where the off temperature of the compressor is A ° C., where the temperature difference between the on / off temperatures of the compressor is a ° C.

  The freezing point of the regenerator may be in the range of B ° C. to (B + a) ° C., where the on temperature of the compressor is B ° C., where the temperature difference of the on / off temperature of the compressor is a ° C.

  The cool storage agent is composed of a first cool storage agent and a second cool storage agent having different freezing points, and the freezing point of the first cool storage agent is defined as an off temperature of the compressor when a temperature difference between on and off temperatures of the compressor is a ° C. Is A ° C., and is in the range of A ° C. to (A + (a / 2)) ° C., and the freezing point of the second regenerator is that the temperature difference of the on / off temperature of the compressor is a ° C. The ON temperature may be B ° C., and may be in the range of (B− (a / 2)) to B ° C.

  The cool storage agent is composed of a first cool storage agent and a second cool storage agent having different freezing points, and the freezing point of the first cool storage agent is defined as an off temperature of the compressor when a temperature difference between on and off temperatures of the compressor is a ° C. Is the range of (A−a) ° C. to A ° C., and the freezing point of the second regenerator is the on-off temperature of the compressor when the temperature difference of the on-off temperature of the compressor is a ° C. The temperature may be B ° C and may be in the range of B ° C to (B + a) ° C.

  According to the present invention, when the compressor is turned on and the temperature change on the downstream side of the evaporator is fast, the response of the temperature sensor is delayed. Since it absorbs from air etc. and delays the temperature drop downstream of the evaporator, the response delay of the temperature sensor is eliminated as much as possible. Thereby, undershoot can be prevented as much as possible, and so-called burning odor can be prevented. In addition, when the compressor is turned off and the temperature change on the downstream side of the evaporator is fast, the response of the temperature sensor is delayed. However, the condensate adhering to the evaporator surface evaporates and cools before the temperature rises to dry. Since the agent releases the heat of fusion to air or the like and delays the temperature rise on the downstream side of the evaporator, the response delay of the temperature sensor is eliminated as much as possible. Thereby, an overshoot can be prevented as much as possible, and the generation of so-called steamy odor can be prevented.

1 is a schematic configuration diagram of a vehicle air conditioner according to a first embodiment of the present invention. 1 is a front view of an evaporator according to a first embodiment of the present invention. 1A and 1B show a first embodiment of the present invention, in which FIG. 2A is a cross-sectional view taken along the line A1-A1 of FIG. 2, and FIG. FIG. 5 is a characteristic diagram of an actual temperature on the downstream side of the evaporator and a detected temperature of the temperature sensor according to the first embodiment of the present invention. FIG. 6 is a characteristic diagram of an actual temperature on the downstream side of an evaporator and a temperature detected by a temperature sensor, showing a second embodiment of the present invention. 3A and 3B show a third embodiment of the present invention, in which FIG. 4A is a cross-sectional view of an evaporator (corresponding to line A1-A1 in FIG. 2), and FIG. FIG. 6 is a characteristic diagram of an actual temperature downstream of an evaporator and a detected temperature of a temperature sensor according to a third embodiment of the present invention. It is a front view of the heat exchange part for cold storage of an evaporator which shows 4th Embodiment of this invention. The 5th Embodiment of this invention is shown, (a) is a front view of a pair of flat plate, (b) is the EE sectional view taken on the line of (a). 6A and 6B show a sixth embodiment of the present invention, where FIG. 6A is a front view of a pair of flat plates, FIG. 5B is a cross-sectional view taken along line F1-F1 in FIG. FIG. It is a figure explaining the range of the freezing point of the cool storage agent in each modification. It is a characteristic line figure of the actual temperature of the evaporator downstream in a prior art example, and the detection temperature of a temperature sensor.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
1 to 4 show a first embodiment of the present invention. As shown in FIG. 1, the vehicle air conditioner 1 has a vapor compression refrigeration cycle 2. The vapor compression refrigeration cycle 2 includes a compressor 3, a condenser 4, an expansion valve 5, an evaporator 6, and a refrigerant pipe 7 that connects these. The compressor 3 adiabatically compresses the refrigerant to high temperature and pressure. The compressor 3 is turned on / off by a thermo switch 13 described below. The condenser 4 performs heat exchange between the high-temperature and high-pressure refrigerant and the air outside the vehicle, and cools the refrigerant. The expansion valve 5 depressurizes the refrigerant cooled by the condenser 4. The evaporator 6 exchanges heat between the low-temperature and low-pressure refrigerant and the air supplied to the passenger compartment, thereby cooling the air. The refrigerant that has passed through the evaporator 6 returns to the compressor 3 as a low-temperature and low-pressure vaporized refrigerant.

  The evaporator 6 is disposed in the air passage 10. A blower 11 and the like are disposed in the air passage 10 together with the evaporator 6. The blower 11 is driven regardless of whether the compressor 3 is on or off in the air conditioning mode. The blower 11 sucks air to be supplied into the passenger compartment into the air passage 10, and the sucked air is supplied into the passenger compartment through the evaporator 6 and the like. The cold air that has passed through the evaporator 6 is reheated to a predetermined temperature, or is supplied into the vehicle compartment without being reheated. The detailed configuration of the evaporator 6 will be described below.

  A temperature sensor 12 is disposed downstream of the evaporator 6. The temperature sensor 12 detects the air temperature downstream of the evaporator 6. The fin temperature on the downstream side of the evaporator 6 may be detected. The thermoswitch 13 is turned on / off by the temperature detected by the temperature sensor 12. The thermoswitch 13 is set to an off set temperature of 3 ° C. and an on set temperature of 5 ° C. As described above, the compressor 3 is turned on and off by turning on and off the thermo switch 13. That is, the compressor 3 is turned off when the temperature sensor 12 detects 3 ° C., and turned on when the temperature sensor 12 detects 5 ° C. The on / off set temperature is changed depending on the sensitivity / accuracy of the temperature sensor, the usage environment, and the like.

  Next, the configuration of the evaporator 6 will be described. As shown in FIGS. 2 and 3, the evaporator 6 includes a plurality of tubes 20 arranged in parallel at intervals, a plurality of fins 21 arranged in an air passage between the tubes 20, and a plurality of tubes 20. A pair of tanks 22 disposed at both ends of the tube 20 are provided.

  Each tube 20 has a refrigerant passage 20a and a regenerator storage passage 20b extending in the longitudinal direction. Each tank 22 has a refrigerant tank chamber 22a and a regenerator tank chamber 22b. The ends of the refrigerant passages 20a of the tubes 20 are opened in the refrigerant tank chambers 22a on both sides. The refrigerant that flows into the evaporator 6 passes through the tubes 20, exchanges heat with the air flowing outside, and flows out of the evaporator 6. In the cool storage agent tank chambers 22b on both sides, the end portions of the cool storage agent storage paths 20b of the tubes 20 are opened. A cool storage agent is stored in the cool storage agent storage path 20b and the cool storage agent tank chamber 22b. The regenerator has a freezing point in a range that is higher than the freezing temperature of water and lower than the temperature at which condensed water adhering to the surface of the evaporator 6 evaporates and dries. Here, the range of the freezing point of the regenerator is preferably in the range of A ° C. to B ° C. when the off temperature of the compressor 3 is A ° C. and the on temperature of the compressor 3 is B ° C. (FIG. 11 ( a)). In the first embodiment, the off temperature A ° C. of the compressor 3 is 3 ° C., the on temperature B ° C. is 5 ° C., and the freezing point of the regenerator is 3.5 ° C. The temperature is close to the off temperature of the compressor 3.

  In the above configuration, when the compressor 3 is on and the cooling load is high, the temperature drop rate on the downstream side of the evaporator 6 is slow. Therefore, the temperature sensor 12 detects the actual temperature with no response delay. Accordingly, when the actual temperature on the downstream side of the evaporator 6 falls to 3 ° C., the temperature sensor 12 also detects approximately 3 ° C., and the compressor 3 is turned off. Undershoot hardly occurs.

  When the compressor 3 is on and the cooling load is low (for example, when the outside air temperature is around 15 ° C. and the condensed water does not adhere to the surface of the evaporator), as shown by the solid line in FIG. Moreover, the rate of decrease in temperature on the downstream side of the evaporator 6 is fast. Then, as shown by a broken line in FIG. 4, a response delay of the temperature sensor 12 occurs with respect to the actual temperature change of the evaporator 6. However, when the temperature on the downstream side of the evaporator 6 falls to 3.5 ° C., the cool storage agent absorbs solidification heat from air or the like and delays the temperature drop on the downstream side of the evaporator 6. Due to this temperature drop delay, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature, and the response delay of the temperature sensor 12 is eliminated. As a result, when the actual temperature downstream of the evaporator 6 drops to 3 ° C., the temperature sensor 12 also detects approximately 3 ° C., and the compressor 3 is turned off. Therefore, the occurrence of undershoot can be substantially prevented, and so-called burning odor can be prevented.

  Further, when the compressor 3 is turned off and the temperature rising speed of the downstream side of the evaporator 6 is slow, the temperature sensor 12 detects the actual temperature with no response delay. Therefore, when the actual temperature on the downstream side of the evaporator 6 rises to 5 ° C., the temperature sensor 12 also detects approximately 5 ° C., and the compressor 3 is turned on. Overshoot does not occur.

  When the compressor is off and the temperature rise on the downstream side of the evaporator 6 is fast, the response of the temperature sensor 12 is delayed. As shown in FIG. 4, the actual temperature downstream of the evaporator 6 is 3 At 5 ° C. (before the condensed water adhering to the surface of the evaporator 6 evaporates and dries), the regenerator releases the heat of fusion to the air and delays the temperature rise on the downstream side of the evaporator 6. Due to this temperature rise delay, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature, and the response delay of the temperature sensor 12 becomes smaller. When the temperature on the downstream side of the evaporator 6 rises to 5 ° C., the temperature sensor 12 detects 5 ° C. with a slight delay. As a result, the compressor 3 is turned on when the actual temperature downstream of the evaporator 6 rises slightly from 5 ° C. Thereby, an overshoot can be prevented as much as possible, and the generation of so-called steamy odor can be prevented. The steamy odor is generated around 12 ° C., depending on the amount of condensed water adhering to the evaporator 6 and the like.

  The freezing point of the regenerator is in a range between the off temperature and the on temperature of the compressor 3. Therefore, since both undershoot and overshoot can be prevented as much as possible, not only the generation of odor but also cold air with little temperature fluctuation can be supplied. Further, there is no need to set on / off assuming large undershoot or large overshoot, and the on / off cycle of the compressor 3 can be lengthened, so that the load on the compressor 3 is reduced, the power is reduced, and the like.

(Second Embodiment)
FIG. 5 shows a second embodiment of the present invention. In this 2nd Embodiment, compared with the said 1st Embodiment, only the kind of cool storage agent accommodated in the evaporator 6 is different. In the second embodiment, the cold storage agent has a freezing point near 4.5 ° C. This is close to the ON temperature of the compressor 3.

  Since other configurations are the same as those of the first embodiment, description thereof will be omitted to avoid redundant description.

  In the above configuration, when the compressor 3 is on and the cooling load is low (for example, when the outside air temperature is around 15 ° C. and the condensed water does not adhere to the surface of the evaporator 6), FIG. As shown by the solid line, the speed of the temperature drop on the downstream side of the evaporator 6 is fast. Then, as shown by a broken line in FIG. 5, a response delay of the temperature sensor 12 occurs with respect to the actual temperature change of the evaporator 6. However, when the temperature on the downstream side of the evaporator 6 falls to around 4.5 ° C., the cool storage agent absorbs solidification heat from air or the like and delays the temperature drop on the downstream side of the evaporator 6. Due to this delay in temperature drop, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature. When the cool storage agent is completely solidified, the temperature drop speed on the downstream side of the evaporator 6 is increased again, and the response of the temperature sensor 12 is delayed. When the temperature sensor 12 detects 3 ° C., the compressor 3 is turned off. Here, the response delay of the temperature sensor 12 becomes a value corresponding to the delay of the temperature drop due to the heat of solidification of the regenerator, so that only a small undershoot occurs compared to the conventional case, and so-called burning odor can be prevented. .

  Further, when the compressor 3 is turned off and the temperature rise on the downstream side of the evaporator 6 is fast, a response delay of the temperature sensor 12 occurs. However, as shown by a solid line in FIG. At a temperature of 4.5 ° C. (before the condensed water adhering to the surface of the evaporator 6 evaporates and dries), the regenerator releases heat of fusion to the air and delays the temperature rise on the downstream side of the evaporator 6. Due to this delay in temperature rise, the response delay of the temperature sensor 12 catches up as shown by the broken line in FIG. Thus, when the actual temperature downstream of the evaporator 6 rises to 5 ° C., the temperature sensor 12 also detects approximately 5 ° C., and the compressor 3 is turned on. Therefore, the occurrence of overshoot can be almost prevented, and so-called steamy odor can be prevented.

  The range of the freezing point of the cool storage agent is between the off temperature and the on temperature of the compressor 3. Therefore, since both undershoot and overshoot can be prevented as much as possible, not only the generation of odor but also cold air with little temperature fluctuation can be supplied. Further, there is no need to set on / off assuming large undershoot or large overshoot, and the on / off cycle of the compressor 3 can be lengthened, so that the load on the compressor 3 is reduced, the power is reduced, and the like.

(Third embodiment)
6 and 7 show a third embodiment of the present invention. In this 3rd Embodiment, as shown in FIG. 6, each tube 20A has the refrigerant | coolant channel | path 20a and the 1st and 2nd cool storage agent accommodation paths 20c and 20d which each extend in a longitudinal direction. Each tank 22A has a refrigerant tank chamber 22a and first and second regenerator tank chambers 22c and 22d. The first cool storage agent storage path 20c and the first cool storage agent tank chamber 22d store the first cool storage agent. The second cool storage agent storage path 20d and the second cool storage agent tank chamber 22d store the second cool storage agent.

  The first and second regenerators each have a freezing point in a range that is higher than the freezing temperature of water and less than the temperature at which condensed water adhering to the evaporator surface evaporates and dries. Here, the range of the freezing point of the regenerator is preferably in the range of A ° C to B ° C, where the off temperature of the compressor 3 is A ° C and the on temperature of the compressor 3 is B ° C.

  More specifically, the freezing point of the first regenerator is defined as A ° C. to (A + (a / 2)), where the temperature difference between the on / off temperatures of the compressor 3 is a ° C. and the off temperature of the compressor 3 is A ° C. More preferably, it is in the range of ° C. (see FIG. 11B). The freezing point of the second regenerator is in the range of (B− (a / 2)) to B ° C. where the temperature difference of the on / off temperature of the compressor 3 is a ° C. and the on temperature of the compressor 3 is B ° C. More preferably (see FIG. 11B). In the third embodiment, the off temperature A ° C. of the compressor 3 is 3 ° C., the on temperature B ° C. is 5 ° C., and the freezing point of the first regenerator is 3.5 ° C. It is close to the off temperature of the compressor. The freezing point of the second cold storage agent is 4.5 ° C., which is close to the ON temperature of the compressor 3.

  Since other configurations are the same as those of the first embodiment, description thereof will be omitted to avoid redundant description.

  In the above configuration, when the compressor 3 is turned on and the cooling load is low (for example, when the outside air temperature is around 15 ° C. and the condensed water does not adhere to the surface of the evaporator 6), FIG. As shown by the solid line, the speed of the temperature drop on the downstream side of the evaporator 6 is fast. Then, as shown by a broken line in FIG. 7, a response delay of the temperature sensor 12 occurs with respect to the actual temperature change of the evaporator 6. However, when the temperature on the downstream side of the evaporator 6 is lowered to about 4.5 ° C., the second cool storage agent absorbs solidification heat from air or the like and delays the temperature drop on the downstream side of the evaporator 6. Due to this delay in temperature drop, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature. When the second cold storage agent is completely solidified, the temperature drop speed on the downstream side of the evaporator 6 is increased again, and a response delay of the temperature sensor 12 occurs. When the temperature on the downstream side of the evaporator 6 is lowered to 3.5 ° C., the first cool storage agent absorbs the heat of solidification from air or the like and delays the temperature drop on the downstream side of the evaporator 6. Due to this delay in temperature drop, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature. As a result, when the actual temperature downstream of the evaporator 6 drops to 3 ° C., the temperature sensor 12 also detects approximately 3 ° C., and the compressor 3 is turned off. Therefore, the occurrence of undershoot can be substantially prevented, and so-called burning odor can be prevented.

  When the compressor 3 is off and the temperature rise on the downstream side of the evaporator 6 is fast, a response delay of the temperature sensor 12 occurs. However, as shown by a solid line in FIG. At 3,5 ° C. (before the condensed water adhering to the surface of the evaporator 6 evaporates and dries), the first regenerator releases heat of fusion to the air and delays the temperature rise on the downstream side of the evaporator 6. Due to this delay in temperature rise, the temperature detected by the temperature sensor 12 gradually catches up with the actual temperature, as indicated by a broken line in FIG. When the first cool storage agent is completely melted, the temperature rise speed on the downstream side of the evaporator 6 is increased again, and a response delay of the temperature sensor 12 occurs. As shown by the solid line in FIG. 7, the second regenerator melts when the actual temperature downstream of the evaporator 6 is 4.5 ° C. (before the condensed water adhering to the surface of the evaporator 6 evaporates and dries). Heat is released to air or the like to delay the temperature rise on the downstream side of the evaporator 6. Due to this delay in temperature rise, the response delay of the temperature sensor 12 catches up as shown by the broken line in FIG. Thus, when the actual temperature downstream of the evaporator 6 rises to 5 ° C., the temperature sensor 12 also detects approximately 5 ° C., and the compressor 3 is turned on. Therefore, the occurrence of overshoot can be almost prevented, and so-called steamy odor can be prevented.

  The range of the freezing point of the cool storage agent is between the off temperature and the on temperature of the compressor 3. Therefore, since both undershoot and overshoot can be prevented as much as possible, not only the generation of odor but also cold air with little temperature fluctuation can be supplied. Further, there is no need to set on / off assuming large undershoot or large overshoot, and the on / off cycle of the compressor 3 can be lengthened, so that the load on the compressor 3 is reduced, the power is reduced, and the like.

(Fourth embodiment)
FIG. 8 shows a fourth embodiment of the present invention. Unlike the first embodiment, the evaporator of the fourth embodiment has a refrigerant heat exchange section (not shown) through which a refrigerant flows and a cold storage heat exchange section 15 in which a cold storage agent is accommodated. A refrigerant heat exchanging portion is disposed upstream along the air flow, and a cold storage heat exchanging portion 15 is disposed immediately downstream thereof.

  As shown in FIG. 8, the cold storage heat exchanging unit 15 includes a plurality of tubes 20B, 20C arranged in parallel at intervals, and a plurality of fins arranged in the air passages between the tubes 20B, 20C ( (Not shown) and a pair of tanks 22B disposed at both ends of the plurality of tubes 20B and 20C.

  The plurality of tubes 20B and 20C have a first tube 20B having a short dimension and a second tube 20C having a long dimension, which are alternately arranged. Inside the pair of tanks 22B, a first cool storage agent tank chamber 22c is provided inside, and a second cool storage agent tank chamber 22d is provided outside. Each first tube 20B communicates with the first cool storage agent tank chamber 22c, and the second tube 20C communicates with the second cool storage agent tank chamber 22d. The 1st cool storage agent is accommodated in the 1st tube 20B and the 1st cool storage agent tank chamber 22c. The second cold storage agent is accommodated in the second tube 20C and the second cold storage agent tank chamber 22d.

  Each freezing point of the first and second cool storage agents is set in the same manner as in the third embodiment.

  In the fourth embodiment, the same operation and effect as the third embodiment can be obtained.

(Fifth embodiment)
FIGS. 9A and 9B show a fifth embodiment of the present invention. In this fifth embodiment, the evaporator has a plurality of a pair of flat plates 30 that are joined reversely. Fins (not shown) are respectively disposed between a pair of adjacent flat plates 30. Inside the pair of flat plates 30, a refrigerant passage 30a and first and second regenerator storage passages 30c and 30d are provided. The 1st cool storage agent accommodation path 30c and the 2nd cool storage agent accommodation path 30d are each formed over the whole area of the flat plate 30 in the longitudinal direction. Each refrigerant passage 30a of each flat plate 30 communicates with each other through a communication hole 30e. The first and second regenerator storage paths 30c and 30d of the flat plates 30 communicate with each other through communication holes 30f and 30g, respectively. The 1st cool storage agent accommodation path 30c stores the 1st cool storage agent. The second cool storage agent storage path 30d stores the second cool storage agent. Each freezing point of the 1st cool storage agent and the 2nd cool storage agent is the same as that of the 3rd and 4th embodiment.

  In the fifth embodiment, the same operation and effect as in the third embodiment can be obtained.

(Sixth embodiment)
FIGS. 10A to 10C show a sixth embodiment of the present invention. This sixth embodiment is partially different from the fifth embodiment in the configuration of the flat plate 30A. In 6th Embodiment, the 1st cool storage agent accommodation path 30c and the 2nd cool storage agent accommodation path 30d are divided | segmented into the upper area | region and lower area of the longitudinal direction of the flat plate 30A, respectively.

  Other configurations are the same as those of the fifth embodiment, and thus description thereof is omitted to avoid redundant description.

  In the sixth embodiment, the same operation and effect as in the third embodiment can be obtained.

(First modification)
When only a single type of regenerator is used, the freezing point of the regenerator may be within the following range. That is, as shown in FIG. 11A, the freezing point of the regenerator is (A−a) ° C. where the temperature difference between the on / off temperatures of the compressor 3 is a ° C. and the off temperature of the compressor 3 is A ° C. It is set as the range of -A degreeC.

  When the compressor 3 is on and the temperature change on the downstream side of the evaporator 6 is fast, the cool storage agent delays the temperature drop on the downstream side of the evaporator 6 at a temperature close to the freezing temperature of water, and the temperature sensor 12. Therefore, it is possible to effectively prevent the generation of a burning odor due to undershoot.

(Second modification)
When only a single type of regenerator is used, the freezing point of the regenerator may be within the following range. That is, as shown in FIG. 11 (a), the freezing point of the regenerator is such that the temperature difference between the on / off temperatures of the compressor 3 is a ° C and the on temperature of the compressor 3 is B ° C. The range is ° C.

  When the compressor 3 is turned off and the temperature change on the downstream side of the evaporator 6 is fast, the regenerator is at a temperature close to the temperature at which the condensed water adhering to the surface of the evaporator 6 evaporates and dries. Since the temperature rise on the downstream side is delayed and there is no response delay of the temperature sensor 12, it is possible to effectively prevent the generation of a bad smell due to overshoot.

(Third Modification)
When two types of cool storage agents are used, the freezing point of each cool storage agent may be within the following range. That is, as shown in FIG. 11B, the freezing point of the first regenerator is defined as (A−a) where the temperature difference between the on / off temperatures of the compressor 3 is a ° C. and the off temperature of the compressor 3 is A ° C. ) ° C. to A ° C., and the freezing point of the second regenerator is B ° C. to (B + a), where the temperature difference of the on / off temperature of the compressor 3 is a ° C. and the on temperature of the compressor 3 is B ° C. The range is ° C.

  When the compressor 3 is on and the temperature change on the downstream side of the evaporator 6 is fast, the cool storage agent delays the temperature drop on the downstream side of the evaporator 6 at a temperature close to the freezing temperature of water, and the temperature sensor 12. Therefore, it is possible to effectively prevent the generation of a burning odor due to undershoot. When the compressor 3 is turned off and the temperature change on the downstream side of the evaporator 6 is fast, the regenerator is at a temperature close to the temperature at which the condensed water adhering to the surface of the evaporator 6 evaporates and dries. Since the temperature rise on the downstream side is delayed so that there is no response delay of the temperature sensor, it is possible to effectively prevent the generation of a bad smell due to overshoot.

(Other)
In each embodiment, the off-temperature of the compressor 3 is 3 ° C. and the on-temperature is 5 ° C. However, the present invention is not limited to this and can be applied to other temperature settings. The on / off temperature of the compressor 3 may be an off temperature of 1.5 ° C., an on temperature of 3 ° C., an off temperature of 5 ° C., an on temperature of 7 ° C., or the like.

2 Vapor compression refrigeration cycle (refrigeration cycle)
3 Compressor 6 Evaporator 12 Temperature sensor

Claims (6)

The evaporator (6) is arranged in a refrigeration cycle (2) in which the compressor (3) is turned on / off based on a temperature sensor (12) for detecting the temperature on the downstream side, and when the compressor (3) is turned on, the refrigerant passes inside. An evaporator (6) for cooling the air flowing and flowing outside,
It has a cold storage agent, and the cold storage agent has a freezing point in a range that is higher than the freezing temperature of water and less than the temperature at which the condensed water adhering to the surface of the evaporator (6) evaporates and dries. An evaporator (6). The evaporator (6) according to claim 1, comprising:
The evaporator (6), wherein a freezing point of the cold storage agent is in a range between an off temperature and an on temperature of the compressor (3). An evaporator (6) according to claim 1 or claim 2, wherein
The freezing point of the regenerator is a range of (A−a) ° C. to A ° C., where the temperature difference between the on / off temperatures of the compressor (3) is a ° C. and the off temperature of the compressor (3) is A ° C. An evaporator (6) characterized in that An evaporator (6) according to any of claims 1-3,
The freezing point of the regenerator is in the range of B ° C. to (B + a) ° C., where the on temperature of the compressor (3) is B ° C. where the temperature difference of the on / off temperature of the compressor (3) is a ° C. An evaporator (6) characterized in that. The evaporator (6) according to claim 1, comprising:
The cool storage agent is composed of a first cool storage agent and a second cool storage agent having different freezing points, and the freezing point of the first cool storage agent is defined as a compressor when the temperature difference between on and off temperatures of the compressor (3) is a ° C. The off temperature of (3) is A ° C, and is in the range of A ° C to (A + (a / 2)) ° C.
The freezing point of the second cool storage agent is defined as follows. When the temperature difference of the on / off temperature of the compressor (3) is a ° C, the on temperature of the compressor (3) is B ° C, and (B- (a / 2)) An evaporator (6) characterized in that it is in the range of ~ B ° C. An evaporator (6) according to claim 1 or claim 5, wherein
The cool storage agent is composed of a first cool storage agent and a second cool storage agent having different freezing points, and the freezing point of the first cool storage agent is defined as a compressor when the temperature difference between on and off temperatures of the compressor (3) is a ° C. The off temperature of (3) is A ° C, and is in the range of (Aa) ° C to A ° C.
The freezing point of the second regenerator is a range of B ° C to (B + a) ° C, where the on-off temperature of the compressor (3) is B ° C, where the temperature difference of the on / off temperature of the compressor (3) is a ° C. An evaporator (6) characterized in that

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