JP2009220760A - Heat blocking plate - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat blocking plate capable of suppressing temperature rises of component units of a refrigerating cycle apparatus mounted in an engine room irrespective of the idling state or a vehicle traveling state. <P>SOLUTION: An isolated space 21 isolated from heat generated by an engine 31 for vehicle travel is formed, and slits 20a for exhausting vehicle traveling air flowing into the isolated space 21 from an introduction port 36 to allow the vehicle traveling air to flow in are formed at a heat blocking plate 20 which protects component units 13, 17 of a refrigerating cycle apparatus arranged in the isolated space 21 from heat generated by the engine 31. Thus, the component units 13, 17 of the refrigerating cycle apparatus 10 can be cooled by the vehicle traveling air even in the vehicle traveling state. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a heat shield plate that protects components constituting a refrigeration cycle apparatus mounted in an engine room from heat generated in an engine for vehicle travel.

Conventionally, for example, Patent Document 1 discloses a heat shield plate that protects components (oxygen sensors and the like) mounted in an engine room from heat generated in an engine for vehicle travel. Further, Patent Document 2 discloses that some components of a vapor compression refrigeration cycle apparatus applied to a vehicle air conditioner are mounted in an engine room.
JP 2004-155391 A JP 2007-307936 A

  In order to protect the components of the refrigeration cycle apparatus mounted in the engine room from the heat generated in the engine as in Patent Document 2 from the above-described prior art, as in Patent Document 1, the refrigeration cycle apparatus is protected. It is conceivable to arrange these components in an isolated space that is thermally isolated from the engine by a heat shield plate.

  However, if the components of the refrigeration cycle apparatus are separated by the heat shield plate, the temperature rise of the component devices due to heat from the engine can be suppressed during idling when the vehicle is not traveling, but the vehicle is Since the flow of the traveling wind is interrupted, the components cannot be cooled by the vehicle traveling wind. For this reason, when the vehicle travels, in which the amount of heat generated by the engine is greater than that during idling, the heat is dissipated in the isolation space, and the temperature of the component devices rises.

  In addition, as is well known, the vapor compression refrigeration cycle apparatus uses the phase change of the refrigerant to move the amount of heat on the low-pressure side to the high-pressure side. When it occurs, the refrigerant evaporation pressure and the like are likely to change, and it becomes difficult to exhibit a stable refrigerating capacity.

  In view of the above points, an object of the present invention is to provide a heat shield plate capable of suppressing a temperature rise of components of a refrigeration cycle apparatus mounted in an engine room regardless of idling or traveling in a vehicle.

  In order to achieve the above object, according to the first aspect of the present invention, an isolation space (21) isolated from heat generated in the engine (31) for vehicle travel is formed in the engine room (30), and the isolation is performed. A heat shield plate that protects the components (13, 17) of the refrigeration cycle device (10) disposed in the space (21) from heat generated in the engine (31), and introduces the vehicle running wind A slit hole (20a) for discharging the vehicle traveling wind flowing from (36) into the isolation space (21) is formed.

  According to this, since the slit hole (20a) for discharging the vehicle traveling wind introduced into the isolation space (21) from the introduction port (36) is formed, it is arranged in the isolation space (21) when the vehicle travels. The components (13, 17) of the refrigeration cycle apparatus (10) thus made can be cooled by the vehicle traveling wind. On the other hand, during idling, the components (13, 17) of the refrigeration cycle apparatus (10) can be protected from the heat of the engine (31).

  Therefore, it is possible to suppress an increase in the temperature of the constituent devices (13, 17) of the refrigeration cycle apparatus (10) mounted in the engine room (30) regardless of idling or traveling of the vehicle. In addition, the “isolated space (21) isolated from heat” in this claim does not mean a space completely isolated from heat, that is, an insulated space, but a component device (13, 17). It is meant to include an isolation space (21) that is thermally isolated to such an extent that it can be protected.

  In the invention according to claim 2, in the heat shield plate according to claim 1, the air passage of the slit hole (20 a) receives the vehicle running wind flowing into the isolation space (21) from the introduction port (36). It is formed in a shape that discharges from the lower side toward the upper side.

  According to this, even if the hot air heated by the engine (31) during idling flows from the lower side to the upper side due to the density difference from the low temperature air, the isolation space (21) is provided via the slit hole (20a). It is possible to suppress backflow inward. As a result, the temperature rise of the components (13, 17) of the refrigeration cycle apparatus (10) mounted in the engine room (30) can be reliably suppressed.

  According to a third aspect of the present invention, in the heat shield plate according to the first or second aspect, the component-side opening (20b) that opens to the isolation space (21) side of the slit hole (20a) has a horizontal direction. The engine side opening (20c) that opens toward the engine (31) in the slit hole (20a) is characterized by opening toward the upper side of the vehicle.

  According to this, specifically, since the vehicle traveling wind introduced into the isolation space (21) can be discharged from the lower side toward the upper side, the hot air heated by the engine (31) Even if it flows from the upper side to the upper side, it is possible to suppress backflow into the isolation space (21) through the slit hole (20a).

  According to a fourth aspect of the present invention, in the heat shield plate according to any one of the first to third aspects, the opening area of the component device side opening (20b) of the slit hole (20a) is the slit hole ( 20a) is larger than the opening area of the engine side opening (20c). Thereby, it can further suppress that the hot air heated by the engine (31) flows back into the isolation space (21) through the slit hole (20a).

  According to a fifth aspect of the present invention, in the heat shield plate according to any one of the first to fourth aspects, an engine room is provided at an opening end of the engine side opening (20c) of the slit hole (20a). (30) A protruding portion (20d) protruding inward is provided.

  According to this, since the protrusion (20d) can block the flow of hot air flowing from the lower side to the upper side in the vicinity of the engine side opening (20c) in the hot air heated by the engine (31). It is possible to effectively suppress backflow into the isolation space (21) through the slit hole (20a).

  According to a sixth aspect of the present invention, in the heat shield plate according to any one of the first to fifth aspects, the introduction port (36) is provided on the front side of the vehicle, and the isolation space (21) (31) It arrange | positions ahead of a vehicle, It is characterized by the above-mentioned.

  According to this, since the isolation space (21) and the engine (31) are arranged in the order of the flow direction of the vehicle traveling wind during the traveling of the vehicle, the hot air heated by the engine (31) is converted into the slit hole (20a). Backflow into the isolation space (21) through can be reliably suppressed.

  Further, as in the invention described in claim 7, in the heat shield plate according to any one of claims 1 to 6, the component device separates the gas-liquid of the low-pressure side refrigerant of the refrigeration cycle apparatus (10). And an accumulator (17) for storing surplus refrigerant, or the internal heat for exchanging heat between the refrigerant sucked by the compressor (11) and the refrigerant discharged from the radiator (12) as in the invention according to claim 8. It may be an exchanger (13).

  The invention according to claim 9 is characterized in that, in the heat shield plate according to claim 7 or 8, the refrigerant of the refrigeration cycle apparatus (10) is carbon dioxide.

  Since the critical pressure of carbon dioxide is about 31 ° C., if the temperature changes in the low-pressure cycle component equipment, the refrigerant pressure in the cycle is likely to change. Therefore, it is extremely effective to use the heat shield plate of the present invention to isolate the components of the refrigeration cycle apparatus (10) that employs carbon dioxide as a refrigerant.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of a vapor compression refrigeration cycle apparatus 10 for cooling air blown into a vehicle interior in a vehicle air conditioner to which a heat shield plate 20 of the present invention is applied. The refrigeration cycle apparatus 10 employs carbon dioxide as a refrigerant, and constitutes a supercritical refrigeration cycle in which the pressure of refrigerant discharged from the compressor 11 is equal to or higher than the critical pressure of the refrigerant (supercritical state).

  In the refrigeration cycle apparatus 10, the compressor 11 sucks refrigerant and compresses and discharges the refrigerant until it reaches a critical pressure or higher. The compressor 11 is disposed in the engine room 30. Further, the compressor 11 is rotationally driven by a driving force transmitted from the vehicle running engine 31 via a pulley and a belt.

  The compressor 11 may be a variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or a fixed capacity that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by switching the electromagnetic clutch. Any type compressor may be adopted. Further, if an electric compressor is used as the compressor 11, the refrigerant discharge capacity can be adjusted by adjusting the rotation speed of the electric motor.

  A radiator 12 is connected to the discharge side of the compressor 11. The radiator 12 is disposed on the front side of the vehicle in the engine room 30 and exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the outside air (air outside the passenger compartment) blown by the cooling fan 12a. It is a heat exchanger for heat dissipation that dissipates heat from the refrigerant.

  Note that, in the refrigeration cycle apparatus 10 of the present embodiment, as described above, the supercritical refrigeration cycle is configured. Therefore, the refrigerant passing through the radiator 12 radiates heat in a supercritical state without condensing. The cooling fan 12a is an electric blower in which the number of rotations (the amount of blown air) is controlled by a control voltage output from an air conditioning control device (not shown).

  A high-pressure side refrigerant passage 13 a of the internal heat exchanger 13 is connected to the outlet side of the radiator 12. The internal heat exchanger 13 exchanges heat between the refrigerant flowing out of the radiator 12 passing through the high-pressure side refrigerant passage 13a and the refrigerant sucked into the compressor 11 passing through the low-pressure side refrigerant passage 13b, and radiates the refrigerant flowing out of the radiator 12. Is.

  Thereby, the enthalpy difference of the enthalpy of the refrigerant | coolant inlet side refrigerant | coolant in the evaporator 15 mentioned later and the enthalpy of an outlet side refrigerant | coolant can be increased, and the refrigerating capability exhibited in the evaporator 15 can be increased. In addition, the vehicle mounting state of the internal heat exchanger 13 will be described later.

  On the outlet side of the high-pressure side refrigerant passage 13a of the internal heat exchanger 13, an expansion valve 14 serves as a pressure control valve for controlling the high-pressure side refrigerant pressure of the cycle and serves as a decompression means for decompressing and expanding the refrigerant. Is connected. The expansion valve 14 functions to bring the high-pressure side refrigerant pressure close to the target high pressure at which the coefficient of performance (COP) of the cycle is substantially maximum.

  Specifically, the expansion valve 14 has a temperature sensing part 14a provided between the radiator 12 outlet side and the high-pressure side refrigerant passage 13a inlet side of the internal heat exchanger 13, and the temperature sensing part 14a A pressure corresponding to the temperature of the high-pressure refrigerant on the outlet side of the radiator 12 is generated inside, and the valve opening degree is balanced by the balance between the internal pressure of the temperature sensing portion 14a and the outlet-side refrigerant pressure of the high-pressure side refrigerant passage 13a of the internal heat exchanger 13. Adjust. Therefore, the expansion valve 14 adjusts the high-pressure side refrigerant pressure so as to approach the target high pressure determined by the high-pressure side refrigerant temperature on the outlet side of the radiator 12.

  An evaporator 15 is connected to the outlet side of the expansion valve 14. The evaporator 15 is disposed on the vehicle interior side and causes heat exchange between the low-pressure refrigerant decompressed by the expansion valve 14 and the vehicle interior blown air blown into the vehicle interior from the blower fan 15a to evaporate the low-pressure refrigerant. This is an endothermic heat exchanger that exerts an endothermic effect.

  More specifically, the evaporator 15 is arrange | positioned in the air passage of the vehicle interior ventilation air formed in the indoor air conditioning unit 16 of a vehicle air conditioner. The indoor air conditioning unit 16 is mounted between a dash panel that partitions the engine room 30 and the vehicle interior and an instrument panel (instrument panel) at the forefront of the vehicle interior. The blower fan 15a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.

  Of the air passages formed in the indoor air conditioning unit 16, on the downstream side of the air flow of the evaporator 15, the blast air cooled by the evaporator 15 and the engine cooling water are heat-exchanged to generate the blast air. A heater core (not shown), which is a heating means for reheating, is disposed. As a result, the temperature of the air blown into the passenger compartment that is air-conditioned space is adjusted.

  An accumulator 17 is connected to the refrigerant outlet side of the evaporator 15. The accumulator 17 is a gas-liquid separator that separates the low-pressure refrigerant flowing out of the evaporator 15 into a liquid-phase refrigerant and a gas-phase refrigerant and stores excess liquid-phase refrigerant in the cycle. The accumulator 17 is provided with a gas-phase refrigerant outlet through which the gas-phase refrigerant flows out. The gas-phase refrigerant outlet is connected to the refrigerant of the compressor 11 via the low-pressure side refrigerant passage 13 b of the internal heat exchanger 13. Connected to the suction side.

  Here, FIG. 2 demonstrates the vehicle mounting state of the internal heat exchanger 13 and the accumulator 17 of this embodiment. 2A is a schematic front view of the vehicle for explaining these mounting states, FIG. 2B is a right side view of FIG. 2A, and FIG. It is a top view in the engine room 30 of (a).

  As shown in FIG. 2, the internal heat exchanger 13 and the accumulator 17 of the present embodiment are mounted in an isolation space 21 defined by a heat shield plate 20 in the engine room 30. The heat shield plate 20 has a function of protecting the internal heat exchanger 13 and the accumulator 17 from heat generated in the engine 31. Therefore, the isolation space 21 is configured as a space isolated from the heat generated in the vehicle running engine 31.

  As shown in FIG. 2, the heat shield plate 20 is located in a range from the frontmost part of the vehicle to the front wheel 34 on the lower side of the headlight 32 on the front side of the vehicle and on the side of the radiator 33 that dissipates engine cooling water. It is formed of a plate-like member that extends while being curved. Further, the end portion of the heat shield plate 20 is joined to the vehicle body 35 constituting the outer shell of the engine room 30. Therefore, the isolation space 21 is formed between the heat shield plate 20 and the vehicle body 35.

  Further, since the heat shield plate 20 is formed in a shape extending from the frontmost part of the vehicle as described above, the isolation space 21 is also arranged on the vehicle front side with respect to the engine 31. Further, the isolation space 21 communicates with the outside of the passenger compartment through an introduction port 36 provided on the frontmost side of the vehicle.

  Accordingly, the vehicle traveling wind (outside air) can flow into the isolation space 21 through the inlet 36 as shown by the thick arrow in FIG. A thin arrow in FIG. 2C indicates the flow of the vehicle traveling wind that flows into the engine room 30.

  Further, the introduction port 36 communicates with the engine room 30. Furthermore, as shown in FIG. 2 (a), the vehicle according to the present embodiment has an air volume of the vehicle traveling wind that flows into the radiator 33 described above. A radiator introduction port 37 is also provided for securing.

  In addition, as a material of the heat shielding board 20, not only a metal material (aluminum, stainless steel, etc.) but the resin material excellent in heat insulation and heat resistance is employable. Specifically, the heat shield plate 20 according to the present embodiment can sufficiently prevent the internal heat exchanger 13 and the accumulator 17 from the heat generated in the engine 31 when the engine 31 is operating and the vehicle is not running. It is formed so that it can be protected.

  In other words, the heat shield plate 20 generates less heat from the engine than when the vehicle travels, but sufficiently prevents the internal heat exchanger 13 and the accumulator 17 from being generated by the engine 31 during idling when the vehicle travel wind does not flow into the isolation space 21. It is formed so that it can be protected.

  Further, the heat shield plate 20 of the present embodiment is formed with a slit hole 20 a for discharging the vehicle traveling wind flowing into the isolation space 21 from the introduction port 36 into the engine room 30. The details of the slit hole 20a will be described with reference to FIG. 3A is an enlarged AA sectional view of FIG. 2C, and FIG. 3B is a side view seen from the engine room 30 side of FIG. 3A.

  As shown in FIG. 3, the ventilation path of the slit hole 20a is formed so as to be sandwiched between two plate-like members. And the component side opening part 20b opened to the isolation space 21 side among the slit holes 20a opens toward the substantially horizontal direction, and the engine side opening part 20c opened to the engine room side among the slit holes 20a. It is opened substantially upwards of the vehicle.

  As a result, the vehicle traveling wind flowing into the isolation space 21 from the introduction port 36 flows so as to be bent in a crank shape from the lower side to the upper side from the slit hole 20a, as shown by an arrow B in FIG. The engine room 30 is discharged.

  Next, an outline of the electric control unit of the present embodiment will be described. The air conditioning control device includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. This air conditioning control device performs various calculations and processes based on the control program stored in the ROM, and controls the operation of the above-described various actuators 12a, 15a and the like.

  Further, detection signals from various sensor groups and various operation signals from an air conditioning operation panel provided in the passenger compartment are input to the air conditioning control device. The air conditioning operation panel is provided with an operation switch that outputs an operation request signal for the vehicle air conditioner, a temperature setting switch that sets a target temperature in the vehicle compartment, and the like.

  Next, the operation of the vehicle air conditioner of the present embodiment in the above configuration will be described. When the operation switch of the operation panel is turned on and the rotational driving force of the vehicle running engine is transmitted to the compressor 11, the compressor 11 is activated. The high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12 and is cooled by the outside air blown by the cooling fan 12a.

  The high-pressure refrigerant that has flowed out of the radiator 12 is further cooled by the internal heat exchanger 13 to reduce enthalpy. The refrigerant flowing out from the high-pressure side refrigerant passage 13a of the internal heat exchanger 13 is decompressed and expanded by the expansion valve 14 to become a low-pressure refrigerant. At this time, the expansion valve 14 adjusts the high-pressure side refrigerant pressure so as to approach the target high pressure at which the coefficient of performance of the cycle is substantially maximum.

  The low-pressure refrigerant that has flowed out of the expansion valve 14 flows into the evaporator 15 and absorbs heat from the blown air of the blower fan 15a to evaporate. As a result, the blown air blown into the passenger compartment is cooled. The low-pressure refrigerant that has flowed out of the evaporator 15 flows into the accumulator 17 and is separated into a gas-phase refrigerant and a liquid-phase refrigerant. The gas-phase refrigerant flowing out of the accumulator cools the high-pressure refrigerant in the low-pressure side refrigerant passage 13b of the internal heat exchanger 13, and then is sucked into the compressor 11 and compressed again.

  In the vehicle air conditioner of the present embodiment, when operating as described above, the components of the refrigeration cycle apparatus 10 (specifically, the internal heat exchanger 13 and the accumulator 17) are separated by the heat shield plate 20. Since they are mounted in the space 21, the components 13 and 17 of the refrigeration cycle apparatus 10 can be appropriately protected from the heat generated in the engine 31.

  More specifically, when the amount of heat generated by the engine 31 is smaller than when the vehicle is running, such as when the vehicle is not running, the temperature of the internal heat exchanger 13 and the accumulator 17 is increased by the heat shield plate 20. Can be suppressed. Furthermore, when the vehicle travels in which the amount of heat generated by the engine 31 increases more than when idling, the internal heat exchanger 13 and the accumulator 17 can be cooled by the vehicle travel wind that has flowed into the isolation space 21 from the inlet 36.

  That is, when the vehicle is traveling, vehicle traveling wind (outside air) having a temperature lower than the ambient temperature in the engine room 30 is caused to flow into the isolation space 21 from the introduction port 36, and the inflowing vehicle traveling wind is passed through the slit hole 20a into the engine room 30. Are discharged. Therefore, it is possible to avoid the heat from entering the isolation space 21 and suppress the temperature rise of the internal heat exchanger 13 and the accumulator 17.

  As a result, it is possible to suppress the temperature rise of the components 13 and 17 of the refrigeration cycle apparatus 10 mounted in the engine room 30 regardless of idling or traveling of the vehicle, and to make the refrigeration cycle apparatus 10 exhibit stable refrigeration capacity. Can do.

  In addition, the component-side opening 20b of the slit hole 20a is opened in the horizontal direction, and the engine-side opening 20c of the slit hole 20a is opened upward from the vehicle so as to be isolated from the introduction port 36. The slit hole 20a is formed so that the vehicle traveling wind flowing into the space 21 flows from the lower side to the upper side.

  As a result, even when hot air heated by the engine 31 during idling flows from the lower side to the upper side due to the density difference from the low temperature air, it flows back into the isolation space 21 through the slit hole 20a. Can be suppressed. As a result, the temperature rise of the internal heat exchanger 13 and the accumulator 17 can be reliably suppressed during idling.

  Furthermore, the introduction port 36 for allowing the vehicle running wind to flow into the isolation space 21 is provided on the forefront side of the vehicle, and the isolation space 21 is disposed on the front side of the vehicle with respect to the engine 31. Are arranged in the order of the flow direction of the vehicle traveling wind. Therefore, the hot air heated by the engine 31 during traveling of the vehicle can be reliably prevented from flowing back into the isolation space 21 through the slit hole 20a.

  Further, in the refrigeration cycle apparatus 10 that employs carbon dioxide as a refrigerant and constitutes a supercritical refrigeration cycle as in this embodiment, the critical pressure of carbon dioxide is about 31 ° C. The refrigerant pressure is likely to change.

  Therefore, it is extremely effective that the temperature increase of the components 13 and 17 of the refrigeration cycle apparatus 10 mounted in the engine room 30 can be suppressed by the heat shield plate 20 of the present embodiment regardless of idling and vehicle traveling. is there. In particular, since the temperature rise of the internal heat exchanger 13 and the accumulator 17 through which the low-pressure side refrigerant flows can be suppressed, the change in the refrigerant evaporation pressure in the evaporator 15 can be effectively suppressed. Can be demonstrated.

(Second Embodiment)
In the present embodiment, as shown in FIG. 4, in the first embodiment, the opening end of the engine-side opening 20c in the slit hole 20a is directed toward the engine room 30 and in the horizontal direction. The protrusion part 20d which protrudes is provided. Other configurations are the same as those of the first embodiment.

  FIG. 4 is a drawing corresponding to FIG. 3 of the first embodiment. Moreover, in FIG. 4, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment. The same applies to the following drawings.

  In the present embodiment, not only the same effects as in the first embodiment can be obtained, but also the hot air heated by the engine 31 during idling (arrow C in FIG. 4) Even if it flows from the upper side to the upper side, the flow of hot air can be prevented by the protrusion 20d. Therefore, it is possible to further reliably suppress hot air from flowing back into the isolation space 21 through the slit hole 20a.

  As a result, the temperature rise of the components of the refrigeration cycle apparatus 10 mounted in the engine room 30 can be more reliably suppressed regardless of idling or traveling of the vehicle, and the refrigeration cycle apparatus 10 has a stable refrigeration capacity. It can be demonstrated.

(Third embodiment)
In the present embodiment, as shown in FIG. 5, the opening area of the component device side opening 20b of the slit hole 20a is made larger than the opening area of the engine side opening 20c as compared to the first embodiment. It is. FIG. 5 is a drawing corresponding to FIG. 3 of the first embodiment. Other configurations are the same as those of the second embodiment.

  As a result, the same effect as that of the second embodiment can be obtained, and the hot air heated by the engine 31 can be more reliably suppressed from flowing back into the isolation space 21 through the slit hole 20a. it can.

  As a result, the temperature rise of the components of the refrigeration cycle apparatus 10 mounted in the engine room 30 can be more reliably suppressed regardless of idling or traveling of the vehicle, and the refrigeration cycle apparatus 10 exhibits stable refrigeration capacity. Can be made.

(Fourth embodiment)
In contrast to the above-described embodiment, in this embodiment, a U-shaped cut is formed in the heat shield plate 20 as shown in FIG. 6B, and a portion inside this cut is deformed. A slit hole 20a is formed.

  More specifically, as shown in FIG. 6A, the slit hole 20a is formed by deforming the vehicle running wind from the lower side toward the upper side from the isolation space 21 side toward the engine room 30 side. is doing. FIG. 6 is a drawing corresponding to FIG. 3 of the first embodiment. Other configurations are the same as those of the first embodiment.

  In the heat shield plate 20 of the present embodiment, a backflow suppression effect that suppresses the backflow of hot air in the engine room 30 into the isolation space 21 through the slit hole 20a is provided for each of the above-described embodiments. Although it decreases, it is possible to suppress the temperature rise of the components of the refrigeration cycle apparatus 10 mounted in the engine room 30 regardless of idling or traveling of the vehicle.

  In addition, since the slit hole 20a can be easily formed by pressing or the like, an effect of reducing the manufacturing cost of the heat shield plate 20 can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the above-described embodiment, the example in which the internal heat exchanger 13 and the accumulator 17 are mounted in the isolation space 21 has been described, but the components of the refrigeration cycle apparatus 10 mounted in the isolation space 21 are It is not limited to. Only the internal heat exchanger 13 may be mounted, or only the accumulator 17 may be mounted. Further, the expansion valve 14, a part of connection piping, and the like may be mounted in the isolation space 21.

  (2) In the above-described embodiment, an example in which carbon dioxide is employed as the refrigerant of the refrigeration cycle apparatus 10 has been described. Of course, a fluorocarbon refrigerant, a hydrocarbon refrigerant, or the like may be employed as the refrigerant. Further, the refrigeration cycle apparatus 10 may constitute a subcritical refrigeration cycle in which the compressor 11 discharge refrigerant pressure does not exceed the critical pressure of the refrigerant.

  (3) In the above-described embodiment, the example in which the isolation space 21 is formed on the vehicle front side has been described. However, the position of the isolation space 21 is not limited to this. Further, the vehicle traveling wind flowing from the introduction port 36 may flow into the isolation space 21 through a duct or the like.

  (4) In the above-described embodiment, the expansion valve 14 that adjusts the opening degree of the high-pressure side refrigerant pressure to the target pressure by a mechanical mechanism is used as the pressure reducing means. However, an electric expansion valve may be used. Specifically, the electric expansion valve may be configured by an electric actuator mechanism including a stepping motor and a valve mechanism driven by the electric actuator mechanism.

  (5) In the above-described embodiment, the example in which the heat shield plate 20 of the present invention is applied to a vehicle air conditioner has been described. However, the application of the heat shield plate 20 of the present invention is not limited to this. For example, the present invention can also be applied to a vehicle refrigeration apparatus that freezes and refrigerates on-board luggage.

It is a whole lineblock diagram of the refrigerating cycle device of a 1st embodiment. (A) is a vehicle front view explaining the mounting state of the components of the refrigeration cycle apparatus, (b) is a side view of (a), and (c) is in the engine room of (a). It is a top view. (A) is AA sectional drawing of FIG.2 (c), (b) is a side view of (a). (A) is sectional drawing corresponding to FIG. 3 (a) in 2nd Embodiment, (b) is a side view corresponding to FIG.3 (b) in 2nd Embodiment. (A) is sectional drawing corresponding to FIG. 3 (a) in 3rd Embodiment, (b) is a side view corresponding to FIG.3 (b) in 3rd Embodiment. (A) is sectional drawing corresponding to Fig.3 (a) in 4th Embodiment, (b) is a side view corresponding to FIG.3 (b) in 4th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Refrigeration cycle apparatus 13 Internal heat exchanger 17 Accumulator 20 Heat insulation board 20a Slit hole 20b Component side opening 20c Engine side opening 20d Protrusion 21 Isolation space 30 Engine room 31 Engine 36 Inlet

Claims (9)

In the engine room (30), an isolation space (21) isolated from heat generated in the vehicle traveling engine (31) is formed, and the refrigeration cycle device (10) disposed in the isolation space (21) A heat shield that protects the components (13, 17) from heat generated in the engine (31),
A heat shield plate, wherein a slit hole (20a) for discharging the vehicle traveling wind flowing into the isolation space (21) from the introduction port (36) through which the vehicle traveling wind flows is formed.   The slit hole (20a) is formed in a shape for discharging the vehicle traveling wind flowing into the isolation space (21) from the introduction port (36) from the lower side toward the upper side. The heat shield plate according to claim 1. Of the slit hole (20a), the component device side opening (20b) that opens to the isolation space (21) side opens in the horizontal direction,
The heat shield according to claim 1 or 2, wherein an engine side opening (20c) that opens to the engine (31) side of the slit hole (20a) opens toward a vehicle upper side. Board.   The opening area of the component side opening (20b) in the slit hole (20a) is larger than the opening area of the engine side opening (20c) in the slit hole (20a). The heat insulation board as described in any one of thru | or 3.   The opening part of the engine side opening part (20c) in the slit hole (20a) is provided with a projecting part (20d) projecting into the engine room (30). Item 5. The heat shield plate according to any one of Items 1 to 4. The introduction port (36) is provided on the vehicle frontmost side,
The heat shield plate according to any one of claims 1 to 5, wherein the isolation space (21) is disposed on the vehicle front side of the engine (31).   The heat insulation plate according to any one of claims 1 to 6, wherein the component device is an accumulator (17) that separates the gas-liquid of the low-pressure side refrigerant and stores excess refrigerant.   8. The internal heat exchanger (13) for exchanging heat between the component device, the compressor (11) and the refrigerant sucked from the radiator (12). Heat shield board.   The heat shield plate according to claim 7 or 8, wherein the refrigerant of the refrigeration cycle apparatus (10) is carbon dioxide.

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