JP2002337537A - Air conditioner for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To attain simplification in constitution and reduction of a cost for a regenerator while suppressing a change of regenerative capacity due to a change of an air conditioning operating condition of air mix door position or the like, in a regenerative air conditioner for a vehicle. SOLUTION: A regenerator 40 cooled by cold air passing through a heat exchanger 9 for cooling is arranged between the downstream of air flow of the heat exchanger 9 for cooling and the upstream of air flow of an air mix door 19. In this way, with no influence due to a position of the air mix door 19, the regenerator 40 can be always well cooled by the cold air after passing through the heat exchanger 9 for cooling, regenerative capacity by the cold air can be always stably displayed. Necessity for providing refrigerant piping in the regenerator 40 is eliminated, the regenerator 40 can be manufactured at a low cost as a simple constitution.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a regenerative air conditioner for a vehicle having a regenerator cooled by cold air after passing through a cooling heat exchanger. It is suitable to be applied to a vehicle in which a certain vehicle engine is temporarily stopped.

[0002]

2. Description of the Related Art In recent years, vehicles (eco-run vehicles, hybrid vehicles, etc.) that automatically stop the engine when the vehicle is stopped at a traffic light or the like (when engine power is not required) have been put into practical use for the purpose of environmental protection. In the future, the number of vehicles that stop the engine when the vehicle stops will tend to increase.

In a vehicle air conditioner, a compressor of a refrigeration cycle is driven by a vehicle engine. Therefore, the eco-run vehicle is stopped at a traffic light or the like, and every time the engine is stopped, the compressor is stopped. The air conditioner also stops, and the temperature of the cooling heat exchanger (evaporator) rises, and the temperature of the air blown into the passenger compartment rises, resulting in a problem that the cooling feeling of the occupant is impaired.

[0004] Therefore, a regenerator that cools the air when the compressor is operated is provided, and when the compressor is stopped (when the cooling operation of the cooling heat exchanger is stopped), the regenerator can cool the air blown into the vehicle compartment. There is a growing need for a vehicle air conditioner.

Japanese Patent Laid-Open Publication No. 2000-38015 discloses this type of regenerative vehicle air conditioner, which discloses an air flow ratio between cold air passing through a bypass passage of a heat exchanger for heating and warm air passing through a heat exchanger for heating. Adjust the air mix door,
There has been proposed a device in which a regenerator cooled by cold air is provided integrally.

Japanese Patent Application Laid-Open No. 1-153321 discloses that a regenerator is disposed in an air passage between a cooling heat exchanger and a heating heat exchanger, and a refrigerant pipe downstream of the cooling heat exchanger is provided. There has been proposed an apparatus provided in a regenerator to cool the regenerator by the cold heat of the refrigerant pipe.

[0007]

According to the former prior art, the regenerator is integrally rotated with the turning operation of the air mixing door. The condition of cold air hitting the vessel changes, and the cold storage capacity changes. In the structure of the embodiment of the prior art, since the regenerator is provided on the surface of the air mix door on the side of the bypass passage, when the air mix door is displaced to the side that closes the bypass passage, the regenerator capacity of the regenerator decreases. I will.

In the latter conventional technique, the refrigerant pipe downstream of the cooling heat exchanger needs to be disposed in the regenerator, so that the configuration of the regenerator becomes complicated, resulting in an increase in cost.

SUMMARY OF THE INVENTION In view of the above, the present invention provides a regenerative vehicle air conditioner that suppresses a change in regenerative power due to a change in air conditioning operating conditions such as an air mix door position.
It is intended to simplify the configuration of the regenerator and reduce costs.

[0010]

According to the first aspect of the present invention, a cooling heat exchanger (9) is provided.
Regenerator (40, 40a, 40b) cooled by cold air passing through the cooling heat exchanger (9) between the downstream side of the air flow of the air and the upstream side of the air flow of the air mixing door (19).
Is arranged.

[0011] Thereby, without being affected by the position of the air mixing door (19), the regenerators (40, 40a, 40b) can always be favorably cooled by the cool air after passing through the cooling heat exchanger (9). Can always exhibit the cold storage capacity stably.

Since the regenerators (40, 40a, 40b) are cooled by cold air, the regenerators (40, 40a, 40b) are cooled.
It is not necessary to provide a refrigerant pipe in b), and the regenerator (40, 4)
0a, 40b) can be manufactured at a low cost with a simple configuration.

According to the second aspect of the present invention, the temperature adjusting means (48) for adjusting the heating capacity of the heating heat exchanger (20).
In a vehicle air conditioner comprising: a cooling heat exchanger (9) between an air flow downstream of a cooling heat exchanger (9) and an air flow upstream of a heating heat exchanger (20). The regenerator (40, 40a, 40) cooled by the passed cold air
b) is arranged.

Thus, in a vehicle air conditioner of the type in which the heating capacity of the heating heat exchanger (20) is adjusted by the temperature adjusting means (48) to adjust the temperature of the air blown into the passenger compartment, the air mixing door (19). , The regenerator (4) is provided between the cooling heat exchanger (9) and the heating heat exchanger (20).
0, 40a, 40b), whereby
Similarly to the above, the regenerator (40, 40a, 40b) can always exhibit the regenerative ability stably, and
0a, 40b) can be manufactured at a low cost with a simple configuration.

According to a third aspect of the present invention, in the first or second aspect, the cooling heat exchanger (9) and the regenerator (4) are provided.
0, 40a, 40b), and a bypass passage (50) through which air flows, and a bypass door (51) for adjusting the amount of bypass air in the bypass passage (50).

Accordingly, when it is not necessary to lower the temperature of air blown into the vehicle compartment to a temperature required for cold storage of the regenerators (40, 40a, 40b) (for example, in the middle of spring and autumn),
The bypass passage (50) is opened by the bypass door (51), and the bypass air is mixed with the cool air that has passed through the cooling heat exchanger (9) and the regenerators (40, 40a, 40b) to target the vehicle interior. The blowing temperature can be made.

Therefore, the amount of air passing through the cooling heat exchanger (9) is reduced by the amount of the bypass air, and the heat load of the cooling heat exchanger (9) is reduced.
The power of the cooling system for lowering the temperature can be reduced.

If the regenerators (40, 40a, 40b) are integrally formed with the cooling heat exchanger (9), the regenerators (40, 40a, 40b) can be further increased. Simplification and cost reduction can be achieved. The regenerator (40, 40) also installs the vehicle air conditioner in the ventilation path.
a, 40b) and the cooling heat exchanger (9) can be easily integrated.

The regenerator (40, 40a, 40b) specifically has a metal tube (45, 430) cooled by cold air,
It is possible to adopt a configuration in which the cold storage material (44) is sealed in the tubes (45, 430).

According to this, the heat resistance of the tubes (45, 430) is reduced because it is made of metal as compared with the case where the cold storage material (44) is sealed in a resin pack, and the time until the completion of cold storage is reduced. Can be shortened.

According to the sixth aspect of the present invention, in the fifth aspect, a large number of tubes (45) are stacked and arranged, and a cool air meanders between the plurality of tubes (45) on the surface of the tube (45). An air passage (46) for direct contact is formed.

Thereby, the regenerators (40, 40a, 40)
b) can be a finless heat exchanger configuration having no fin on the air side, and the regenerators (40, 40a, 40)
The configuration of b) can be further simplified. Moreover, since the cold air comes into direct contact with the surface of the tube (45) while meandering, the meandering flow disturbs the flow of the cool air, thereby improving the heat transfer coefficient and ensuring the required heat transfer performance.

Further, since the finless heat exchanger is used, the space for storing the cold storage material can be expanded by the amount of no fins, and the cold storage capacity can be increased.

According to a seventh aspect of the present invention, in any one of the first to fourth aspects, the regenerator (40, 40a,
40b) is formed of a bent structure obtained by bending a metal tube (60) in a meandering manner a predetermined number of times, and is characterized in that a cold storage material (44) is sealed in the tube (60).

According to this, a tube of arbitrary length (6
Since the entire shape of the regenerator (40, 40a, 40b) having a meandering bent shape can be formed by folding the 0) a predetermined number of times, the regenerator (40, 40a, 40b)
Of the regenerator (40, 40a, 40b) can be arbitrarily adjusted by the bending dimension of the tube (60).

Therefore, the heat transfer plate (4
1, 42) and a regenerator (40, 40a, 40b)
It is not necessary to press-form the heat transfer plates (41, 42) with a dedicated press die for each regenerator size as in the case of configuring the tube (1), and a brazing step is not required.

Also, the opening at the end of the tube (60) can be used as it is as a filling port for the cold storage material (44), and after the cold storage material is filled, the opening at this end only needs to be sealed.

By constructing the regenerator (40, 40a, 40b) from the bent structure of the tube (60), the regenerator (40, 40a, 40b) can be manufactured at low cost.

[0029] As in the invention described in claim 8, as in claim 7,
In the above, if the fin member (61) is arranged between the tubes (60) of the bent structure, the fin member (61)
Can improve the heat exchange efficiency.

According to the ninth aspect of the present invention, as set forth in the seventh aspect,
In or 8, the bent structure may be divided into a plurality of parts, and the plurality of bent structures may be integrally connected.

According to the tenth aspect of the present invention, in any one of the first to fourth aspects, the regenerator (40, 40)
a, 40b) are composed of a plurality of tubes (60) in which a cold storage material (44) is sealed and fixing members (62, 63) for fixing both ends of the plurality of tubes (60). It is characterized by.

According to this, the regenerators (40, 40a, 4
The height H of 0b) can be arbitrarily adjusted by the cutting length of the tube (60). In addition, regenerators (40, 40a, 40
The width W of b) can be arbitrarily adjusted by the number of layers of the tube (60) having an arbitrary length.

Accordingly, the heat transfer plate (4
1, 42) and a regenerator (40, 40a, 40b)
It is not necessary to press-form the heat transfer plates (41, 42) with a dedicated press die for each regenerator size as in the case of configuring the tube (1), and a brazing step is not required.

Further, the opening at the end of the tube (60) can be used as it is as a filling port for the cold storage material (44), and after the cold storage material is filled, the opening at this end only needs to be sealed.

As described above, an arbitrary length tube (6
The regenerators (40, 40a, 40b) can be manufactured at low cost by configuring the regenerators (40, 40a, 40b) by fixing the both ends of (0) with the fixing members (62, 63).

In the tenth aspect, the fixing member (6
2, 63) can be formed in advance into a predetermined shape (claim 11 below). In addition to such a member, a resin molded member integrally formed with the tube (60), or an adhesive material may be used. May be used to bond and fix both ends of the tube (60).

According to the eleventh aspect, in the tenth aspect,
In the above, the tube (60) is formed in a flat cross section along the flow direction of the cold air, and the fixing members (62, 63) are provided with a plurality of grooves (62a, 63a) at predetermined intervals.
The two ends of the tube (60) are fixed to the grooves (62a, 63a).

Thus, both ends of the plurality of tubes (60) can be easily and reliably fixed at predetermined intervals in the grooves (62a, 63a) of the fixing members (62, 63). Further, since the tube (60) is formed to have a flat cross section along the flow direction of the cool air, it is possible to suppress an increase in pressure loss in the cool air flow path.

According to a twelfth aspect of the present invention, in any one of the first to eleventh aspects, as the regenerator, a plurality of regenerators (40a) in which at least two or more types of regenerator materials having different melting points are independently sealed. , 40b).

Thus, when the air conditioning (cooling) heat load is large, such as in summer, the temperature of the cold air that has passed through the cooling heat exchanger (9) is lowered, and two or more types of cold storage materials having different melting points are used. To ensure the required cold storage performance when the heat load is large.

On the other hand, air conditioning (cooling) as in the middle of spring and autumn
When the heat load is small, the temperature of the cold air that has passed through the cooling heat exchanger (9) is raised to solidify only the cold storage material with the higher melting point, ensuring the necessary cold storage performance when the heat load is small. I do. Then, since the temperature of the cool air that has passed through the cooling heat exchanger (9) is increased, the required cooling capacity of the cooling heat exchanger (9) can be reduced, and the compressor driving power of the refrigeration cycle can be reduced.

According to the thirteenth aspect, in the twelfth aspect,
Wherein the plurality of regenerators (40a, 40b) are configured as an integrated heat exchanger structure having an internal partition structure capable of independently enclosing at least two or more types of regenerator materials having different melting points.

Thus, a plurality of regenerators (40a, 40
b) can be integrated and manufactured at low cost.

According to the fourteenth aspect of the present invention,
Or in 13, the plurality of regenerators (40a, 40b)
Among them, a regenerator (4) in which a refrigerating material (44) having a high melting point is sealed.
0a) is arranged on the upstream side in the flow direction of the cool air that has passed through the cooling heat exchanger (9), and a plurality of regenerators (40a, 40a).
In the method (b), a regenerator (40b) in which a regenerative material (44) having a low melting point is sealed is arranged on the downstream side in the flow direction of the cool air.

Thus, when the air-conditioning (cooling) heat load is small and the temperature of the cold air passing through the cooling heat exchanger (9) is switched to a higher temperature as in the middle of spring and autumn, the cooling heat exchanger (9) ) Can cool the refrigerating material (44) having a high melting point with the cold air immediately after passing through. Therefore, even if the temperature of the cold air is switched to a higher temperature, the temperature difference between the cold air and the high-melting-point cold storage material (44) can be easily taken, and the cold storage of the high-melting-point cold storage material (44) is easy.

According to a fifteenth aspect of the present invention, there is provided an air conditioner mounted on a vehicle adapted to stop the vehicle engine (4) when the power of the vehicle engine (4) is unnecessary, wherein The exchanger (9) is characterized by being an evaporator of a refrigeration cycle (R) having a compressor (1) driven by a vehicle engine (4).

Thus, in a vehicle in which the engine (4) is stopped when engine power is not required, such as when the vehicle is stopped, even when the engine is stopped, the cooling operation of the regenerators (40, 40a, 40b) allows the cooling operation in the passenger compartment to be performed. Can be maintained.

Note that the reference numerals in parentheses of the above means indicate the correspondence with specific means described in the embodiments described later.

[0049]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) FIG. 1 is an overall configuration diagram of a first embodiment. A refrigeration cycle R of a vehicle air conditioner has a compressor 1 for sucking, compressing and discharging refrigerant. The compressor 1 is provided with an electromagnetic clutch 2 for power interruption. Since the power of the vehicle engine 4 is transmitted to the compressor 1 via the electromagnetic clutch 2 and the belt 3, the operation of the compressor 1 is intermittently performed by interrupting the energization of the electromagnetic clutch 2 by the electronic control unit 5 for air conditioning. Is done.

The high-temperature, high-pressure superheated gas refrigerant discharged from the compressor 1 flows into the condenser 6 and exchanges heat with the outside air blown by a cooling fan (not shown) to be cooled and condensed. The refrigerant condensed in the condenser 6 then flows into the receiver 7 where gas and liquid of the refrigerant are separated inside the receiver 7, and the excess refrigerant (liquid refrigerant) in the refrigeration cycle R is discharged into the receiver 7. Stored inside.

The liquid refrigerant from the receiver 7 is decompressed to a low pressure by an expansion valve (decompression means) 8 to be in a low-pressure gas-liquid two-phase state. The expansion valve 8 is a temperature-type expansion valve having a temperature sensing portion 8a for sensing the temperature of the outlet refrigerant of the evaporator (cooling heat exchanger) 9. The low-pressure refrigerant from the expansion valve 8 flows into the evaporator 9. The evaporator 9 is installed in an air conditioning case 10 of a vehicle air conditioner, and the low-pressure refrigerant flowing into the evaporator 9 absorbs heat from the air in the air conditioning case 10 and evaporates. The outlet of the evaporator 9 is connected to the suction side of the compressor 1 and forms a closed circuit by the above-mentioned cycle components.

In the air-conditioning case 10, a blower 11 is arranged upstream of the evaporator 9, and the blower 11 is provided with a centrifugal blower fan 12 and a drive motor 13. An inside / outside air switching box 14 is arranged on the suction side of the blower fan 12, and an inside / outside air switching door 14a in the inside / outside air switching box 14 opens and closes an outside air inlet 14b and an inside air inlet 14c.
Thereby, outside air (vehicle outside air) is stored in the inside / outside air switching box 14.
Alternatively, the inside air (vehicle interior air) is switched and introduced. The inside / outside air switching door 14a is an electric drive unit 14 including a servomotor.
Driven by e. .

In the ventilation system of the air conditioner, the air conditioning unit 15 disposed downstream of the blower 11 is usually disposed at the center position in the vehicle width direction inside the instrument panel at the front of the vehicle cabin. It is arranged offset to the passenger seat side with respect to 15 units. In the air-conditioning case 10, a regenerator 40 and an air mix door 19, which will be described later, are sequentially arranged downstream of the evaporator 9. This air mix door 19
A hot water heater core (heating heat exchanger) 20 that heats air using hot water (cooling water) of the vehicle engine 4 as a heat source is installed on the downstream side.

On the side (upper portion) of the hot water heater core 20, there is formed a bypass passage 21 for bypassing the hot water heater core 20 and flowing air (cold air). The air mix door 19 is a rotatable plate-like door, and is driven by an electric drive device 22 including a servomotor.

The air mix door 19 adjusts the ratio of the amount of hot air passing through the hot water heater core 20 and the amount of cool air passing through the bypass passage 21. Adjust the outlet air temperature. Therefore, in this example, the air mix door 19 constitutes a means for adjusting the temperature of the air blown into the vehicle interior. On the downstream side of the hot water heater core 20, a hot air passage 23 extending upward from below is formed, and the hot air from the hot air passage 23 and the cool air from the bypass passage 21 are mixed in the air mixing section 24, so Can produce temperature air.

Further, in the air-conditioning case 10, a blow-out mode switching unit is provided downstream of the air mixing unit 24. That is, a defroster opening 25 is formed in the upper surface of the air-conditioning case 10, and the defroster opening 25 blows air to the inner surface of the vehicle windshield through a defroster duct (not shown). The defroster opening 25 is
It is opened and closed by a rotatable plate-shaped defroster door 26.

A face opening 27 is formed on the upper surface of the air-conditioning case 10 at a position rearward of the vehicle from the defroster opening 25. The face opening 27 is connected to an upper body of an occupant of the passenger compartment through a face duct (not shown). It blows air toward. The face opening 27 is opened and closed by a rotatable plate-like face door 28.

In the air-conditioning case 10, a foot opening 29 is formed below the face opening 27,
The foot opening 29 blows air toward the feet of the occupant in the vehicle. The foot opening 29 is opened and closed by a rotatable plate-like foot door 30. The blowout mode doors 26, 28, 30 are connected to a common link mechanism (not shown), and are driven by an electric drive device 31 including a servomotor via the link mechanism.

The temperature sensor 32 of the evaporator 9 is connected to the air conditioning case 1
Within 0, the evaporator 9 is disposed immediately after the air is blown out, and detects the evaporator blowout temperature Te. Further, the temperature sensor 33 of the regenerator 40 is arranged at a position immediately after air is blown out of the regenerator 40, and detects the regenerator outlet temperature Tc.

Here, the evaporator outlet temperature Te detected by the evaporator temperature sensor 32 is used to control the intermittent control of the electromagnetic clutch 2 of the compressor 1 and the compressor 1 in the same manner as in an ordinary air conditioner.
Is a variable displacement type, it is used for discharge capacity control, and the cooling capacity of the evaporator 9 is adjusted by these clutch engagement control and discharge capacity control. The regenerator outlet temperature Tc detected by the regenerator outlet temperature sensor 33 is used for controlling the opening of the air mix door 19, and the opening of the air mix door 19 is corrected based on the value of the regenerator outlet temperature Tc. It has become.

The temperature sensors 32 and 33 need only have substantially the same temperature responsiveness. However, in order to suppress the fluctuation of the temperature of the air blown into the vehicle cabin, it is particularly necessary to use a regenerator temperature sensor. It is better to increase the temperature responsiveness of 33.

The air-conditioning electronic control unit 5 has an internal air temperature T for air-conditioning control in addition to the temperature sensors 32 and 33 described above.
A detection signal is input from a well-known sensor group 35 for detecting r, the outside air temperature Tam, the amount of solar radiation Ts, the hot water temperature Tw, and the like. Further, an air conditioning control panel 36 installed near the instrument panel in the vehicle compartment.
Is provided with a group of operation switches 37 that are manually operated by the occupant, and operation signals of the group of operation switches 37 are also input to the electronic control unit 5 for air conditioning.

The operation switch group 37 includes a temperature setting switch 37a for generating a temperature setting signal Tset, an air volume switch 37b for generating an air volume switching signal, a blowing mode switch 37c for generating a blowing mode signal, and generating an inside / outside air switching signal. And an air conditioner switch 37e for generating an on / off signal for the compressor 1. The blow-off mode switch 37c is used to manually switch among well-known blow-off modes such as a face mode, a foot mode, a bi-level mode, a foot differential mode, and a defroster mode.

Further, the air conditioning electronic control unit 5 is connected to the engine electronic control unit 38, and the engine air conditioning electronic control unit 5 sends the air conditioning electronic control unit 5 a rotation speed signal, a vehicle speed signal, and the like of the vehicle engine 4. Is entered.

As is well known, the engine electronic control unit 38 integrates a fuel injection amount, an ignition timing, and the like to the vehicle engine 4 based on a signal from a sensor group (not shown) for detecting an operation state of the vehicle engine 4 and the like. It is to control it. Further, in an eco-run vehicle and a hybrid vehicle to which the present invention is applied, a rotation speed signal of the vehicle engine 4, a vehicle speed signal,
When the stop state is determined based on a brake signal or the like, the engine electronic control unit 38 automatically stops the vehicle engine 4 by shutting off the power supply of the ignition device, stopping the fuel injection, and the like.

When the vehicle is shifted from the stopped state to the start state by the driver's driving operation after the engine is stopped, the engine electronic control unit 38 determines the start state of the vehicle based on an accelerator signal or the like, and the vehicle engine is controlled. Start 4 automatically. The air-conditioning electronic control unit 5 outputs an engine restart request signal based on, for example, an increase in the regenerator outlet temperature Tc after the vehicle engine 4 is stopped.

The air-conditioning electronic control unit 5 and the engine electronic control unit 24 are constituted by a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof. The air-conditioning electronic control unit 5 includes an engine control signal output unit that outputs a stop permission / stop prohibition signal of the vehicle engine 4 and a signal of a restart request after the engine is stopped, a compressor intermittent control unit using the electromagnetic clutch 2, and inside / outside air. Inside / outside air suction control unit by switching door 14a, air volume control unit of blower 11, temperature control unit by air mix door 19, outlet 2
It has a blowout mode control unit by switching between 5, 27, and 29, and the like.

Next, the specific structure of the regenerator 40 will be described. The regenerator 40 has the same front surface area as the evaporator 9 as shown in FIG. (The total amount of air flow in the air-conditioning case 10). Thereby, the regenerator 40 can have a thin structure with a small thickness dimension in the air flow direction A in the air conditioning case 10.

FIG. 2 exemplifies a specific heat exchanger configuration of the regenerator 40. The two heat transfer plates 41 and 42 are provided with the convex portions 4 alternately along the air (cool air) flow direction A, respectively.
1a and 42a are formed, and these convex portions 41a and 42a are brought into contact with and joined to each other (such as brazing) with the flat portions of the heat transfer plates 41 and 42 on the other side. Thereby, the convex portion 41
a, a tube 45 having a closed space 43 inside 42a
Is formed, and the cold storage material 44 is stored in the closed space 43.

In FIG. 2, the direction perpendicular to the paper is the vertical direction in the state where the regenerator 40 is disposed in the air-conditioning case 10, and therefore, the convex portions 4 of the heat transfer plates 41 and 42
1a, 42a and the enclosed space 43 inside thereof also have a shape extending in the vertical direction in the air conditioning case 10. Therefore, the condensed water generated on the surfaces of the heat transfer plates 41 and 42 can fall downward by gravity along the convex portions 41a and 42a.

Although only two sets of tubes 45 are shown in FIG. 2, actually, since the regenerator 40 has the same front area as the evaporator 9, the tubes 45 are not shown in FIG.
Are stacked in the arrow B direction (the direction orthogonal to the air flow direction A).

At the upper and lower ends of the large number of tubes 45, abutting portions are provided between the tubes 45 so as to hold air passages 46 at predetermined intervals between the tubes 45. Then, the heat transfer plates 41, 42 of each tube 45
By integrally joining (brazing) the contact portions and the like between the tubes and between the tubes 45, the entire regenerator 40 is reduced to one.
It can be integrated as one heat exchanger structure. A large number of sealed spaces 43 are provided at both upper and lower ends of the tube 45.
A tank part (not shown) for communicating the above-mentioned parts is integrally formed, and the tank part can constitute the contact part.

The heat transfer plates 41 and 42 are preferably formed of a thin aluminum plate material in consideration of heat transfer properties and weight reduction. The brazing temperature of aluminum is 60
Since the temperature is high around 0 ° C., the cold storage material 44 is sealed in the closed space 43 after the brazing step of the regenerator 40 is completed. A part of the closed space 43 (for example,
One or more filling ports are provided in the above-mentioned tank portion, etc., and the cold storage material 44 is filled into the closed space 43 from the filling ports, and after the filling operation is completed, the filling ports are replaced with an appropriate sealing material (for example, O-ring etc.) and seal with a lid member.

The specific material of the cold storage material 44 is as follows.
In order to prevent the frost of the evaporator 9, a material having a melting point of about 6 to 8 ° C. and a high anticorrosion effect on the regenerator material (aluminum) is preferable, and such a condition can be satisfied by paraffin. . Paraffin is superior to molten salts and other inorganic substances in terms of chemical stability, toxicity, and cost.

The air passage 46 is provided with the convex portions 41a, 4a,
A meandering passage is formed by alternately protruding 2a. That is, in the air passage 46, the cool air is in direct contact with the surfaces of the heat transfer plates 41 and 42 of each tube 45 while meandering. This meandering form prevents the straight flow of the air flow and disturbs the air flow, so that the heat transfer coefficient on the air side can be significantly improved. Thermal performance can be ensured.

Next, the operation of the first embodiment in the above configuration will be described. In the vehicle air conditioner, the refrigeration cycle R is operated by driving the compressor 1 by the vehicle engine 4, and the temperature of the evaporator 9 is set to a temperature around 3 ° C. to 5 ° C. by intermittent control of the operation of the compressor 1. To prevent the frost of the evaporator 9.

Here, in the evaporator 9, the low-temperature and low-pressure gas-liquid two-phase refrigerant, which has been depressurized by the expansion valve 8, absorbs heat from the air blown by the blower 11 and evaporates, thereby cooling the blown air. Become. And this cold air is next to regenerator 4
A plurality of sets of tubes 45 pass through air passages 46 at predetermined intervals formed between the tubes 45.

Here, the meandering form of the air passage 46 disturbs the flow of the cool air and dramatically improves the heat transfer coefficient on the air side. The cold storage material (paraffin) 44 can be effectively cooled via 42. As a result, the regenerative material 44 is cooled, solidified from a liquid state at room temperature to a solid state, and can be stored in the form of latent heat of fusion.

For this reason, in a vehicle such as an eco-run vehicle that automatically stops the engine 4 when stopping at a traffic light or the like (when engine power is not required), the compressor 1 of the refrigeration cycle R is stopped when the vehicle stops. However, the temperature of the air blown into the vehicle compartment can be maintained at a relatively low temperature by using the cold storage amount of the cold storage material (paraffin) 44. Therefore, during summer cooling, a sudden increase in the temperature of the air blown into the vehicle compartment due to the stoppage of the compressor 1 can be suppressed, and deterioration of the cooling feeling can be prevented.

According to the first embodiment, since the regenerator 40 is arranged downstream of the evaporator 9 and upstream of the air mix door 19, it depends on the rotational position of the air mix door 19. Therefore, the regenerator 40 can always be satisfactorily cooled by the cool air after passing through the evaporator 9.

In particular, since the regenerator 40 is configured to be cooled by the cool air and the regenerator 40 has a finless structure, the regenerator 40 can have a simple heat exchanger structure. When the regenerator 40 has a finless structure,
Since the air side fins are not provided, the space for accommodating the cold storage material in the same physique can be expanded and the cold storage capacity can be increased.

As a specific example of the cold storage material 44, a melting point = 8
After passing through the evaporator 9 using 300 cc of paraffin of 300 ° C.
When the regenerator material 44 in the regenerator 40 shown in FIG. 2 is cooled by cold air of 5 ° C. to 5 ° C., the regenerator material (solidification) of the regenerator material 44 can be completed in about one minute, and the regenerator material of 300 cc of the regenerator is completed. 44, it was found that even in the stop state of the engine 4 (compressor 1), the interior of the vehicle can be properly cooled for about one minute.

(Second Embodiment) In the first embodiment, the regenerator 40 has a finless structure, but in the second embodiment, the regenerator 40 has a fin-and-tube type heat exchanger structure as shown in FIG. .

In FIG. 3, two heat transfer plates 41
Tubes 430 are formed by joining the two heat transfer plates 410 and 420 in the middle in the shape of bulging outward in a bowl shape. Then, corrugated fins 440 and tubes 430 bent in a wave shape are alternately stacked and arranged in the up-down direction in FIG. 3, and between the heat transfer plates 410 and 420 of the tubes 430, the fins 440 and the tubes 430 The space is joined by integral brazing of aluminum. After brazing, the internal space of the tube 430 is filled with the cold storage material 44 and sealed.

In the first and second embodiments, the case where the heat transfer plates 41, 42, 410, and 420 are each formed by a separate thin plate is shown. The thin sheet material is bent into a U-shape at the center thereof to form a tube 45 of the first embodiment or a tube 430 of the second embodiment.
May be formed.

(Third Embodiment) In the second embodiment,
A heat transfer plate 410 made of a press-formed thin plate material,
The tube 430 is formed by joining the tubes 420, but in the third embodiment, as shown in FIG. 4, the tube 430 is formed of an extruded product having a multi-hole cross-sectional shape. Are joined to the corrugated fins 440. The cold storage material 44 is a tube 43
Fill inside the multi-hole of No. 0 and seal.

(Fourth Embodiment) In the first embodiment described above, the regenerator 40 separate from the evaporator 9 is disposed downstream of the evaporator 9, but in the fourth embodiment, as shown in FIG. The regenerator 40 is integrated with the evaporator 9. FIG. 6 shows this evaporator 9.
And a specific example of integration of the regenerator 40 with the evaporator 9.
And the regenerator 40 are integrated in a finless heat exchanger structure.

In FIG. 6, a convex portion 41 similar to FIG. 2 is provided downstream of the heat transfer plates 41 and 42 in the air flow direction A.
The closed space 43 for accommodating the cold storage material 44 is formed by molding the a and a. Further, of the heat transfer plates 41 and 42, the convex portions 41b and 42 are also provided on the upstream side in the air flow direction A.
b is formed to form a refrigerant passage 47 through which the refrigerant of the evaporator 9 flows inside the convex portions 41b and 42b.

Thus, the evaporator 9 on the upstream side of the air flow and the regenerator 40 on the downstream side of the air flow can be easily manufactured by integral brazing, and the evaporator 9 and the regenerator 40 have a single heat exchanger structure. Therefore, installation into the air-conditioning case 10 becomes easy. In addition, since the cold storage material 44 can be cooled by the cold air cooled by the refrigerant in the refrigerant passage 47, and at the same time, the cold storage material 44 can be cooled by heat conduction through the heat transfer plates 41 and 42, the cooling effect of the cold storage material 44 is improved. Can be improved.

(Fifth Embodiment) In the above-described first embodiment, the air mix door 19 is provided downstream of the evaporator 9.
In the fifth embodiment, the regenerator 40 is arranged on the downstream side of the evaporator 9 and on the upstream side of the heater core 20 as shown in FIG.

That is, in the fifth embodiment, the hot water valve 4 for adjusting the hot water flow rate (or hot water temperature) of the heater core 20 is used.
8 is provided in the hot water circuit, and the heating capability of the heater core 20 can be adjusted by adjusting the flow rate of hot water (or hot water temperature) of the heater core 20 by adjusting the opening of the hot water valve 48.

Therefore, the hot water valve 48 can serve as a temperature adjusting means for adjusting the temperature of the air blown into the vehicle interior, so that the air mix door 19 is not required.

(Sixth Embodiment) In the first embodiment, the front surface area of the regenerator 40 is made the same as that of the evaporator 9 so that the entire amount of cool air after passing through the evaporator 9 passes through the regenerator 40. However, in the sixth embodiment, as shown in FIG.
0 is smaller than the evaporator 9 to form the bypass passage 49 of the regenerator 40. For this reason, the evaporator 9
The whole amount of the cool air after passing does not pass through the regenerator 40, and a part of the cool air bypasses the regenerator 40.

(Seventh Embodiment) In all of the first to sixth embodiments, the front surface area of the evaporator 9 is made equal to the cross-sectional area of the passage in the air-conditioning case 10 so that the total amount of air blown by the blower 11 is reduced. In the seventh embodiment, the evaporator 9 and the regenerator 40 have the same front area as shown in FIG.
A bypass passage 50 for bypassing the bypass passage 50 is formed, and a plate-like bypass door 51 is rotatably disposed at an entrance of the bypass passage 50.

The bypass door 51 is connected to the bypass passage 5
The bypass air flow rate is adjusted by adjusting the opening degree to zero.

According to the seventh embodiment, the compressor driving power can be reduced (power saving effect) for the following reasons. That is, in order to solidify the cold storage material 44 in the cold storage 40,
It is necessary to always lower the temperature of the evaporator 9 to a temperature lower than the melting point of the cold storage material 44. On the other hand, when the cooling load is small as in the middle of spring and autumn, the temperature of the evaporator 9 may not need to be lowered to a temperature lower than the melting point of the cold storage material 44 in some cases.

Therefore, in the seventh embodiment, when it is not necessary to lower the temperature of the evaporator 9 to a temperature equal to or lower than the melting point of the cold storage material 44 as in the intermediate period, the bypass passage 50 is opened by the bypass door 51 and the blower is opened. A part of the blast air 11 flows by bypassing the evaporator 9 and the regenerator 40. As a result, target air is blown out by mixing cold air having a temperature equal to or lower than the melting point of the cold storage material 44, which has passed through the evaporator 9 and the regenerator 40, and high-temperature bypass air (evaporator suction air) which is not cooled by the evaporator 9. Can make temperature.

More specifically, based on the temperature Tc of the air discharged from the regenerator 40 detected by the temperature sensor 33, the temperature of the bypass air (the evaporator suction air) passing through the bypass passage 50, and the target discharge temperature. In this case, the opening degree of the bypass door 51 may be determined. Since the bypass air (evaporator suction air) is the inside air or the outside air, the temperature of the bypass air can be obtained based on the inside temperature Tr or the outside temperature Tam detected by the sensor group 35.

As described above, since the cooling load on the evaporator 9 is reduced by reducing the amount of air passing through the evaporator 9, the operation rate of the compressor 1 is reduced and the compressor driving power can be reduced accordingly. .

(Eighth Embodiment) The eighth embodiment aims at obtaining a regenerator structure capable of reducing the manufacturing cost while maintaining the performance of cold storage and cooling.

First, the regenerator 4 according to the first embodiment of FIG.
The reason why the manufacturing cost of 0 is increased will be described with reference to FIGS. FIG. 10 is a sectional view of a tube 45 corresponding to FIG. 2, and FIG. 11 is an overall sectional view of the regenerator 40 in which the tubes 45 of FIG. Forming portions 45a, 45b,
Filling ports 45c for the cold storage material 44 are provided at both left and right ends of each of the tank portions 45a and 45b, and the filling port 45c is sealed by the lid member 52 after the cold storage material 44 is filled.

With such a configuration, the heat transfer plate 4
The heat transfer plates 41 and 42 are press-formed.
Are stacked and brazed to form the regenerator 40. Therefore, the height H of the regenerator
Each time is changed, it is necessary to change the press forming dimensions of the heat transfer plates 41 and 42, and it is necessary to prepare press dies corresponding to each press forming dimension, and the press die cost per one regenerator is reduced. Expensive.

Also, since a step of brazing the laminated assembly of the heat transfer plates 41 and 42 is required, an assembling jig having various sizes is used as an assembling jig for maintaining the assembled state of the laminated assembly. Required, and furthermore, a brazing furnace is required as a production facility, and the facility cost is also high.

On the other hand, FIG. 12 shows a regenerator structure according to the eighth embodiment, in which the tubes of the regenerator 40 are not formed by stacking the heat transfer plates 41 and 42 formed by press forming. 13 is a bent structure of a tube 60 having various flat cross-sectional shapes.

More specifically, FIG. 13A to FIG.
FIG. 13C shows a tube 60 formed by extruding (or drawing) aluminum.
The tube 60 in FIG. 13A is formed into a flat single-hole shape. The tube 60 in FIG. 13B is formed into a flat multi-hole shape. The tube 60 of FIG. 13C has a cross-sectional shape similar to that of FIG. 10, that is, a flat cross-sectional shape in which the sealed space 43 protrudes from the central wall portion 60a on both front and back sides by extrusion (or drawing) of aluminum. Things.

Next, the tube 60 in FIG. 13D is formed by bending a thin aluminum plate to form a flat single-hole shape similar to that shown in FIG. 13A. The butted end faces are welded.
Numeral 60b is the welded portion. Next, the tube 60 in FIG. 13E is obtained by bending an aluminum thin plate material to form two flat holes, and then welding the butted end surfaces of the aluminum thin plate material. 6
0c is the welded portion. The flat cross-sectional shape of the tube 60 is made parallel to the flow direction of the cool air after passing through the evaporator 9 (the left-right direction in FIG. 13) to suppress the pressure loss on the air side.

In the eighth embodiment, the above various tubes 60 are bent in a meandering shape as shown in FIG. 12 to complete a folded structure (a serpentine structure) of the regenerator 60. Here, FIGS.
In the tube cross-sectional shape of (e), the tube 60 is designed to have a thin thickness of about 0.2 to 0.5 mm, so that the tube 60 can be bent without any trouble.

In the configuration shown in FIG. 12, since one tube 60 is bent to form the entire shape of the regenerator 60, the cold storage material is opened from both ends of the tube 60 (filling port) after bending. 44 is filled in the tube 60, and the openings at both ends of the tube 60 are sealed. The cold storage material 44 also uses paraffin having a melting point of 8 ° C. in this example. Reference numerals 60d denote sealing portions at both ends of the tube 60. Specific examples of the sealing portions 60d are as shown in the following FIGS. 14 (a) to (c).

The sealing portion 60d shown in FIG.
The opening at the end of 0 is bent and sealed. In the sealing part 60d of FIG. 14B, the lid member 52 having a sealing function by an elastic body is press-fitted into the opening at the end of the tube 60 to seal the tube opening. FIG.
The sealing part 60d of (c) seals the opening at the end of the tube 60 with an adhesive 60e.

According to the eighth embodiment, the entire shape of the regenerator 40 having the meandering bent structure can be formed by bending the tube 60 having an arbitrary length a predetermined number of times. Therefore, the width W of the regenerator 40 can be arbitrarily adjusted by the number of times the tube 60 is bent, and the height H of the regenerator 40 can be arbitrarily adjusted by the bending dimension of the tube 60.

Therefore, as in the case of the regenerator 40 shown in FIGS. 10 and 11, it is not necessary to press-mold the heat transfer plates 41 and 42 by a dedicated press die for each size of the regenerator 40, and the brazing process is not required. Is also unnecessary.

The opening at the end of the tube 60 can be used as a filling port for the cold storage material 44 as it is, and after the cold storage material 44 is filled, it is only necessary to seal the opening at this end.

(Ninth Embodiment) FIG. 15 shows a ninth embodiment. In the eighth embodiment, since the entire shape of the regenerator 40 is formed by bending one tube 60, the required length of the tube 60 may be excessive.
In such a case, as in the ninth embodiment, the regenerator 4
In the width W direction of 0, a plurality of meandering bent structures (serpentine structures) of the tube 60 (3 in FIG. 15)
) To form the entire shape of the regenerator 40.

(Tenth Embodiment) FIG. 16 shows a tenth embodiment in which the tube 60 has a meandering bent structure (a serpentine structure) in the thickness D direction of the regenerator 40 (in other words, the air flow direction A). (In FIG. 16, 2
Pieces).

As described above, the thickness D direction (air flow direction A)
In the case where the meandering bent structure of the tube 60 is divided into a plurality in FIG. 17, the tube pitch before and after in the air flow direction is matched as shown in FIG.
The tube pitch may be shifted as in (b). By shifting the tube pitch as in the latter case, the heat exchange efficiency of the tube 60 on the downstream side of the air flow can be improved by the tip effect.

Note that the plurality of tube bending structures in the regenerator width W direction in the ninth embodiment and the tenth
The plurality of tube bending structures before and after the air flow according to the embodiment are all integrally connected by a mounting bracket (not shown), so that the entire regenerator can be incorporated into the air conditioning case 10 as an integrated structure.

(Eleventh Embodiment) FIG. 18 shows an eleventh embodiment in which a corrugated fin 61 similar to the corrugated fin 440 of FIGS. The heat exchange efficiency between the cool air after passing through the evaporator 9 and the regenerator 40 is improved. Note that the corrugated fin 61 of the eleventh embodiment is not brazed, but only presses against the outer surface of the tube 60.

(Twelfth Embodiment) The eighth embodiment shown in FIGS.
In the eleventh embodiment, the regenerator 4 is formed by bending the tube 60 in a meandering shape a predetermined number of times.
However, in the twelfth embodiment, the tube 60 is not bent in a meandering shape as shown in FIG.
The regenerator 40 is constituted by using a straight tube 60.

FIG. 19 shows a regenerator 40 according to the twelfth embodiment.
FIG. 2 is a perspective view of the regenerator 40. The regenerator 40 includes a plurality of tubes 60 that extend straight
And fixing members 62 and 63 for fixing the upper and lower ends of the fixing member.

The tube 60 is similar to the one shown in FIGS.
(E) is a metal tube made of aluminum or the like having various flat cross-sectional shapes, and is cut into a predetermined length from a tube 60 formed into various cross-sectional shapes. The cold storage material 44 is sealed. In addition,
The cold storage material 44 also uses paraffin having a melting point of 8 ° C. in this example. Reference numerals 60d denote sealing portions at both ends of the tube 60. Specific examples of the sealing portions 60d may be the same as the structures shown in FIGS. 14A to 14C described above.

The upper and lower fixing members 62 and 63 are usually formed of resin, and a plurality of grooves 62a and 63a are provided at predetermined intervals in the longitudinal direction of the fixing members 62 and 63, respectively. The upper and lower ends of each tube 60 are fixed to the upper and lower grooves 62a and 63a by means such as press fitting. The upper and lower fixing members 62 and 63 may be formed of a metal such as aluminum.

According to the twelfth embodiment, the height H of the regenerator 40 can be adjusted to an arbitrary length by changing the cutting length of the tube 60. The width W of the regenerator 40 is
By changing the number of stacking layers, the size can be adjusted to an arbitrary size. Therefore, as in the case of the regenerator 40 shown in FIGS. 10 and 11, it is not necessary to press-mold the heat transfer plates 41 and 42 with a dedicated press die for each size of the regenerator 40, and a brazing step is not required. is there. Therefore, the regenerator 40 can be manufactured at low cost.

Further, the opening at the end of the tube 60 can be used as it is as a filling port for the cool storage material 44, and after filling the cool storage material 44, it is only necessary to seal the opening at this end. The structure is also simple.

In the twelfth embodiment, the regenerator 40
Although no fins are provided between the tubes 60, the corrugated fins 61 may be inserted between the tubes 60 as in the eleventh embodiment of FIG. 18 to improve the heat exchange efficiency.

Further, as a modification of the twelfth embodiment,
When the upper and lower fixing members 62 and 63 are molded with resin, the cold storage material 4 is used.
4 may be integrally molded by insert molding. That is, a required number of tubes 60 filled with the cold storage material 44 and sealed at both ends are arranged at a predetermined pitch in the molding die, and then the upper and lower fixing members 6 are arranged.
You may make it resin-mold 2 and 63 integrally with the tube 60.

As another modification of the twelfth embodiment, the upper and lower fixing members 62 and 63 are eliminated, and the cold storage material 44 is used.
May be arranged at a predetermined pitch with an appropriate jig, and both ends of each tube 60 may be connected to each other in an integrated structure with an adhesive or the like.

Further, as another modified example of the twelfth embodiment, a required number of tubes 60 with both ends open are prepared. First, one end of the required number of tubes 60 is sealed.
Thereafter, the cold storage material 4 is inserted into each tube 60 through the opening at the other end.
4, the opening at the other end may be sealed.

Here, the sealing of the end of the tube 60 is shown in FIG.
In this case, the sealing of the ends of the tubes 60 and the connection between the required number of tubes 60 can be performed at once by the above-mentioned three means. You may.

(Thirteenth Embodiment) The thirteenth embodiment aims at reducing the compressor driving power of the refrigeration cycle while ensuring the required cooling amount for the air conditioning heat load.

First, the problem of the thirteenth embodiment will be described. In the case where one kind of cold storage material 44 is sealed in the cold storage unit 40 as in the first to twelfth embodiments, the air conditioner heat load conditions in the summer are different. The specifications such as the melting point and the amount of sealing of the cold storage material 44 are determined so as to satisfy the required cold storage performance. For example, in the summer condition, when the engine 4 (compressor 1) is stopped due to a stop such as a traffic light wait, the cold storage unit 40 cools down the cold storage to maintain the vehicle interior in a predetermined cooling state for one minute. 300cc of paraffin having a melting point of 8 ° C as the material 44
is necessary. In order to solidify (freeze) the paraffin having a melting point of 8 ° C. to perform cold storage, it is necessary to set the blowing temperature of the evaporator 9 to about 3 ° C.

When the air-conditioning heat load decreases as in the middle of spring and autumn, the target temperature of the blow-out temperature of the evaporator 9 may be increased to, for example, about 10 ° C. in view of the air-conditioning heat load.

However, if the regenerator material 44 in the regenerator 40 is only one kind of paraffin having a melting point of 8 ° C., the blowing temperature of the evaporator 9 is kept at 3 ° C. even in the middle of spring and autumn for cold storage.
It is necessary to set the temperature to a low temperature, and as a result, the cooling capacity of the evaporator 9 in the intermediate period is increased more than necessary, which causes an increase in compressor driving power.

In the thirteenth embodiment, in consideration of the above points, FIG.
0, a plurality of regenerators 40 each containing at least two or more types of regenerator materials 44 having different melting points.
a and 40b. Note that the plurality of regenerators 40a and 40b can be of various configurations described up to the twelfth embodiment.

The thirteenth embodiment will be described in more detail. A plurality of regenerators 40a and 40b are arranged in series on the downstream side of the evaporator 9, and the regenerator 40a on the upstream side has a high melting point ( A cold storage material 44 of, for example, 15 ° C. is sealed, and a low melting point (for example, 8
(° C.).

When the air conditioning heat load is large as in summer conditions, the target outlet temperature of the evaporator 9 is set to a temperature (for example, 3 ° C.) lower than the melting points of both the cold storage materials 44, and during the travel of the vehicle. The cold storage material 44 is solidified in both the plurality of regenerators 40a and 40b to perform cold storage. Thus, when the vehicle is stopped, the cooling effect can be maintained by the cooling action of both regenerators 40a and 40b.

On the other hand, when the air-conditioning heat load is small, such as in the middle of spring and autumn, the target outlet temperature of the evaporator 9 required by the air-conditioning heat load is sufficiently higher than the summer conditions. Therefore, the target blowing temperature of the evaporator 9 can be switched to a temperature (for example, 10 ° C.) higher than the melting point of the cold storage material 44 on the low melting point (for example, 8 ° C.) side.

As a result, during traveling of the vehicle, only the high-melting-point (eg, 15 ° C.) regenerator material 44 in the regenerator 40a on the upstream side solidifies and performs cold storage by solidification latent heat. On the other hand, the low melting point (for example, 8
C) does not solidify, and therefore does not perform cold storage by the latent heat of solidification. Therefore, when the vehicle is stopped, the cooling effect is maintained by the cooling operation of the upstream regenerator 40a in which the refrigerating material 44 having a high melting point is sealed. Since the air conditioning heat load is small in the middle period, the required cooling effect can be maintained only by the cooling operation of the upstream regenerator 40a.

Then, in order to switch the target blowing temperature of the evaporator 9 to a temperature (for example, 10 ° C.) higher than the melting point of the cold storage material 44 on the lower melting point (for example, 8 ° C.), the cooling of the evaporator 9 in the middle period The capacity can be reduced, and the compressor drive power can be reduced.

In particular, for the air flow direction A, the evaporator 9
The regenerator 40a in which the regenerator material 44 having a high melting point (for example, 15 ° C.) is encapsulated, and the regenerator 40b in which the regenerator material 44 having a low melting point (for example, 8 ° C.) is encapsulated, are arranged in this order. The cold storage effect of the high-melting-point cold storage material 44 in the vessel 40a can be favorably performed.

That is, conversely to the above, if the evaporator 9 is arranged in the order of the regenerator 40b enclosing the low-melting regenerative material 44 → the regenerator 40a enclosing the refractory material 44 of the high melting point, The cold air of 10 ° C. first flows into the regenerator 40b, where it absorbs heat and rises in temperature. As a result, the regenerator 4
0b, and the temperature difference between the high-melting cold storage material 44 of the regenerator 40a on the downstream side is reduced, and the high-melting cold storage material 44 is reduced.
The cold storage performance is deteriorated.

On the other hand, in the thirteenth embodiment, the evaporator 9
The cold air of 10 ° C. after passing first flows into the regenerator 40a,
Since the high melting point regenerator material 44 in the regenerator 40a is cooled,
Immediately after passing through the evaporator 9, the high-melting-point cold storage material 44 can be cooled by cold air whose temperature has not risen, and the temperature difference between the cold air and the high-melting-point cold storage material 44 is increased to increase the high-melting-point cold storage material. 44
Can improve the cold storage performance.

(Fourteenth Embodiment) In the thirteenth embodiment, the evaporator 9, the upstream regenerator 40a, and the downstream regenerator 40b
Although these three heat exchangers are sequentially arranged in the case 10 with a predetermined interval between them, as in the fourteenth embodiment shown in FIG. 21, these three heat exchangers 9, 40 are provided.
a and 40b may be arranged in the case 10 while being in contact with each other.

(Fifteenth Embodiment) In the thirteenth and fourteenth embodiments, the plurality of regenerators 40a and 40b are configured as physically independent heat exchangers.
As in the embodiment, the plurality of regenerators 40a and 40b were configured as an integrated heat exchanger structure, the inside of the integrated heat exchanger structure was partitioned by an appropriate partition member 40c, and then partitioned by the partition member 40c. The regenerative materials 44 having different melting points may be sealed in a plurality of spaces.

(Sixteenth Embodiment) In the fifteenth embodiment,
A plurality of regenerators 40 configured as an integral heat exchanger structure
a and 40b and the evaporator 9 are separate bodies.
As shown in the sixteenth embodiment, all of the evaporator 9 and the plurality of regenerators 40a and 40b may be configured as an integral heat exchanger structure. In FIG. 23, a partition member 40d partitions a refrigerant passage of the evaporator 9 from a cool storage material-filled space of the cool storage unit 40a on the upstream side.

(Other Embodiments) The regenerator 4 in the fifth to seventh embodiments (FIGS. 7 to 9).
0 is the heat exchanger configuration shown in FIGS.
And the heat exchanger configuration shown in FIG. 19 and the heat exchanger configuration shown in FIG.

In the above-described embodiment, a case has been described where aluminum is used as a material example of the regenerator 40. However, metals such as copper and iron can be used in addition to aluminum. Further, not limited to metal, the regenerator 40 may be made of resin. If the regenerator 40 is made of resin, the heat transfer performance is reduced to some extent, but the regenerator 40 is easily manufactured.
The cost of the regenerator 40 can be reduced.

In the above embodiments, the case where the melting point of the cold storage material 44 is between 6 ° C. and 8 ° C. has been described. However, from the viewpoint of preventing the frost of the evaporator and ensuring the cooling effect by allowing the cold storage material 44 to cool down, Can be set in the range of about 3 ° C to 18 ° C.

In each of the above embodiments, the evaporator 9 and the regenerator 40 are arranged so as to extend in the vertical direction (vertical arrangement). An arrangement form can be adopted.

[Brief description of the drawings]

FIG. 1 is an overall system diagram of a vehicle air conditioner according to a first embodiment of the present invention.

FIG. 2 is a sectional view of a main part of the regenerator of FIG.

FIG. 3 is a sectional view of a main part of a regenerator according to a second embodiment.

FIG. 4 is a sectional view of a main part of a regenerator according to a third embodiment.

FIG. 5 is a sectional view of a main part showing an integrated arrangement of a regenerator and an evaporator according to a fourth embodiment.

FIG. 6 is a sectional view of an integrated structure of a regenerator and an evaporator according to a fourth embodiment.

FIG. 7 is a sectional view showing an arrangement relationship between an evaporator, a heater core, and a regenerator according to a fifth embodiment.

FIG. 8 is a sectional view showing an arrangement relationship between an evaporator, a heater core, and a regenerator according to a sixth embodiment.

FIG. 9 is a sectional view showing an arrangement relationship between an evaporator, a heater core, and a regenerator according to a seventh embodiment.

FIG. 10 is a cross-sectional view of a regenerator according to a comparative example (first embodiment) for explaining the purpose of the eighth embodiment.

FIG. 11 is a schematic sectional view of the entire regenerator according to a comparative example (first embodiment) for explaining the purpose of the eighth embodiment.

FIG. 12 is a front view of the entire regenerator according to an eighth embodiment.

FIG. 13 is a sectional view of a tube constituting a regenerator according to an eighth embodiment.

FIG. 14 is a cross-sectional view showing a sealed structure of a tube end portion constituting a regenerator according to an eighth embodiment.

FIG. 15 is a front view of the entire regenerator according to the ninth embodiment.

FIG. 16 is a perspective view of the entire regenerator according to the tenth embodiment.

FIG. 17 is a sectional view showing an arrangement state of tubes of a regenerator according to a tenth embodiment.

FIG. 18 is a partial front view of a regenerator according to an eleventh embodiment.

FIG. 19 is a perspective view of the entire regenerator according to a twelfth embodiment.

FIG. 20 is an overall system diagram of a vehicle air conditioner according to a thirteenth embodiment.

FIG. 21 is a sectional view showing an arrangement relationship between an evaporator and a regenerator according to a fourteenth embodiment.

FIG. 22 is a sectional view showing an arrangement relationship between an evaporator and a regenerator according to a fifteenth embodiment.

FIG. 23 is a sectional view showing an arrangement relationship between an evaporator and a regenerator according to a sixteenth embodiment.

[Explanation of symbols]

9 evaporator (cooling heat exchanger), 19 air mixing door, 20 heater core (heating heat exchanger), 40, 40
a, 40b: regenerator, 60: tube.

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Koichi Saka 1-1-1, Showa-cho, Kariya-shi, Aichi Pref. Inside Denso Corporation (72) Inventor Koji Yamanaka 1-1-1, Showa-cho, Kariya-shi, Aichi Pref. Inside DENSO (72) Inventor Sadayuki Kamiya 1-1-1, Showa-cho, Kariya-shi, Aichi Pref. Inside DENSO Corporation (72) Inventor Eiichi Torikoshi 1-1-1, Showa-cho, Kariya-shi, Aichi pref.

Claims (15)

[Claims] 1. A cooling heat exchanger (9) for cooling air blown into a vehicle cabin, and a heating heat exchanger (9) disposed downstream of the cooling heat exchanger (9) in an air flow direction to heat the air. A heat exchanger (20); and an air mix door (19) for adjusting an air volume ratio between hot air passing through the heating heat exchanger (20) and cold air bypassing the heating heat exchanger (20). And between the downstream side of the airflow of the cooling heat exchanger (9) and the upstream side of the airflow of the air mixing door (19) by the cold air passing through the cooling heat exchanger (9). An air conditioner for a vehicle, comprising a regenerator (40, 40a, 40b) to be cooled. 2. A cooling heat exchanger (9) for cooling the air blown into the vehicle interior, and a heating heat exchanger disposed downstream of the cooling heat exchanger (9) in the air flow and heating the air. A heat exchanger (20); and a temperature adjusting means (48) for adjusting a heating capacity of the heating heat exchanger (20). An air flow downstream of the cooling heat exchanger (9), A regenerator (40, 40a, 40b) that is cooled by cold air passing through the cooling heat exchanger (9) is arranged between the heating heat exchanger (20) and the air flow upstream side. Vehicle air conditioner. 3. A bypass passage (50) through which air flows bypassing the cooling heat exchanger (9) and the regenerator (40, 40a, 40b), and a bypass passage (5).
The vehicle air conditioner according to claim 1 or 2, further comprising: a bypass door (51) for adjusting a bypass air volume of (0). 4. The vehicle according to claim 1, wherein the regenerator (40, 40a, 40b) is integrally formed with the cooling heat exchanger (9). Air conditioner. 5. The regenerator (40, 40a, 40b)
Is a metal tube (4) cooled by the cold air.
5, 430), and a cold storage material (44) is sealed in the tube (45, 430).
The air conditioner for a vehicle according to any one of claims 1 to 4. 6. The plurality of tubes (45) are stacked and arranged, and an air passage (46) is provided between the plurality of tubes (45) to directly contact the surface of the tubes (45) while the cold air meanders. The vehicle air conditioner according to claim 5, wherein the air conditioner is formed. 7. The regenerator (40, 40a, 40b) is formed of a bent structure obtained by bending a metal tube (60) in a meandering manner a predetermined number of times, and a regenerator (44) is provided in the tube (60). 5. The air conditioner for a vehicle according to claim 1, wherein the air conditioner is sealed. 8. A vehicle air conditioner according to claim 7, wherein fin members (61) are arranged between said tubes (60) in said bent structure. 9. The air conditioner for a vehicle according to claim 7, wherein the bent structure is formed by being divided into a plurality of parts, and the plurality of bent structures are integrally connected. 10. The regenerator (40, 40a, 40b)
Is characterized by comprising a plurality of tubes (60) enclosing a cold storage material (44) therein and fixing members (62, 63) for fixing both ends of the plurality of tubes (60). The vehicle air conditioner according to any one of claims 1 to 4. 11. The tube (60) has a flat cross section along the flow direction of the cold air, and the fixing member (62, 63) is provided with a plurality of grooves (62a, 63a) at predetermined intervals. And the grooves (62a,
The vehicle air conditioner according to claim 10, wherein both ends of the tube (60) are fixed to 63a). 12. The regenerator according to claim 1, further comprising a plurality of regenerators (40a, 40b) in which at least two or more types of regenerator materials having different melting points are independently sealed. The vehicle air conditioner according to one of the preceding claims. 13. The plurality of regenerators (40a, 40b).
14. The vehicle air conditioner according to claim 12, wherein the air conditioner has an integral heat exchanger structure having an internal partition structure capable of independently enclosing at least two or more types of cold storage materials having different melting points. 14. The plurality of regenerators (40a, 40b).
Among them, a regenerator (4) in which a refrigerating material (44) having a high melting point is sealed.
0a) is arranged on the upstream side in the flow direction of the cool air passing through the cooling heat exchanger (9), and the low-melting-point cold storage material (44) among the plurality of regenerators (40a, 40b) is enclosed. 14. The air conditioner for a vehicle according to claim 12, wherein the regenerator (40b) is arranged downstream in a flow direction of the cool air. 15. An air conditioner mounted on a vehicle adapted to stop the vehicle engine (4) when the power of the vehicle engine (4) is unnecessary, wherein the cooling heat exchanger (9). 15. The vehicle according to claim 1, wherein the evaporator is a refrigerating cycle (R) having a compressor (1) driven by the vehicle engine (4). Air conditioner.