JP2007015650A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To ensure compatibility between ensuring of the maximum cooling performance and miniaturizing of an air conditioner in the air conditioner wherein hot water circulates in a heat exchanger for heating even in the maximum cooling operation. <P>SOLUTION: An opening part 19 is disposed so as to directly oppose to the heat exchanger 14 for heating, and the main stream of cold air stream j from a cold air passage 15 is inclined to the heat exchanger 14 side for heating toward the opening part 19. A film part 21d of a film door 21 opening/closing the opening part 19 is directly opposed to the heat exchanger 14 for heating in a bi-level mode, and a partition plate 23 partitioning a area 24 of the cold air passage 15 side, the cold air passage 15, and the area 25 of the opposite side is disposed at the downstream side of an air stream of the heat exchanger 14 for heating. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a structure for guaranteeing the maximum cooling performance in an air conditioner that adjusts the blown air temperature based on the air volume ratio between cold air and hot air, and a structure for improving control characteristics of the blown air temperature.

  Conventionally, in an air conditioner for a vehicle, an airmic system in which the air volume ratio between cold air and hot air is adjusted by an air mix door to adjust the blown air temperature is representative. (For example, refer to Patent Document 1).

  In this prior art, as shown in FIG. 9, in the upper part of the heating heat exchanger 14, a cold air passage 15 is formed that bypasses the heating heat exchanger 14 and through which the cold air flows. The hot air passage 40 through which the hot air that has passed is formed so as to rise from the rear side of the heating heat exchanger 14 toward the upper portion of the heating heat exchanger 14.

  And the air mixing part 41 which mixes the cold air from the said cool air channel | path 15 and the warm air from the said warm air channel | path 40 in the upper part of the heat exchanger 14 for heating is formed, and it mixed by this air mixing unit 41 The conditioned air at a desired temperature is distributed toward the face blowing opening 20, the foot blowing opening 19, and the defroster blowing opening 42.

  Moreover, in the said prior art, the butterfly door which has the 1st door part 43a, the 2nd door part 43b, and the rotating shaft 43c arrange | positioned in the middle of both these door parts 43a and 43b is used as the air mix door 43. .

  The cold air passage 15 and the inlet air passage 16 of the heating heat exchanger 14 are opened and closed by the first door portion 43a, and the outlet portion of the hot air passage 40 is opened and closed by the second door portion 43b. During maximum cooling, the cold air passage 15 is fully opened by the first door portion 43a and the inlet ventilation passage 16 of the heating heat exchanger 14 is fully closed. At the same time, the outlet portion of the hot air passage 40 is fully closed by the second door portion 43b. To do.

  Thereby, it can prevent by the 2nd door part 43b that the warm air heated with the heat exchanger 14 for a heating at the time of maximum cooling mixes in a cold wind flow by natural convection. For this reason, it is possible to prevent the temperature of the air blown into the passenger compartment from rising due to the mixing of warm air during maximum cooling, and the maximum cooling performance can be guaranteed. Therefore, the hot water valve that interrupts the hot water flow to the heat exchanger 14 for heating can be eliminated.

  However, according to the above prior art, the long hot air passage 40 extending from the rear side of the heating heat exchanger 14 to the upper portion of the heating heat exchanger 14 and the foot blowing passage 44 extending downward from the air mixing portion 41 are provided. This is necessary, causing problems such as an increase in the size of the air conditioner and an increase in the pressure loss of the foot blowing air.

  As another temperature adjustment method for a vehicle air conditioner, a hot water flow rate adjustment method is known in which the hot water flow rate to the heating heat exchanger 14 is adjusted by the opening degree of the hot water valve to adjust the blown air temperature. With this hot water flow rate adjustment method, the air mix door 43 and the air mixing unit 41 can be eliminated, which is advantageous for downsizing the air conditioner.

  However, with this warm water flow rate adjustment method, the entire amount of the blown air always passes through both the cooling heat exchanger 13 and the heating heat exchanger 14, so there is a problem that the ventilation resistance is high. Further, since warm water having a large specific heat is built in the heat exchanger 14 for heating, the heat capacity of the heat exchanger 14 as a whole is very large. For this reason, in the hot water flow rate adjustment method, there is a problem that the temperature followability of the blown air with respect to the change in the opening degree of the hot water valve is poor as compared with the airmic method.

  Therefore, the present inventors have attempted to realize downsizing of the air conditioner in an airmic system that is excellent in terms of ventilation resistance, temperature followability, and the like.

  FIGS. 10 and 11 are air conditioners examined by the inventors as prototypes, and are arranged so that the foot blowing opening 19 as the first blowing opening is directly opposed immediately after the blowing side of the heat exchanger 14 for heating. is doing. On the other hand, a face blowing opening (second blowing opening) 20 disposed adjacent to the foot blowing opening 19 is arranged so as to directly face the cold air passage 15.

  Both the blowout openings 19 and 20 are opened and closed by a film door 21 constituting a blowout mode door. Both ends of the film door 21 are connected to the winding shafts 21b and 21c so as to be rewound and rewound, and an opening window portion 21a or film film portions 21d and 21e provided in the middle of the film door 21 in the longitudinal direction are both blown out. By overlapping with the openings 19 and 20, both the blowout openings 19 and 20 are opened and closed.

According to such an air conditioning unit configuration, the space immediately after blowing out the heat exchanger 14 for heating and the space occupied by the outlet side space of the cold air passage 15 can be reduced to the same level as in the hot water flow rate adjustment method. Therefore, in the prototypes of FIGS. 10 and 11, the physique can be greatly reduced as compared with the conventional representative airmic air conditioning unit configuration shown in FIG.
JP 2004-42687 A

  By the way, the prototypes of FIGS. 10 and 11 are so-called water valveless systems in which no hot water valve is provided in the hot water passage of the heating heat exchanger 14, so hot water is added to the heating heat exchanger 14 even during maximum cooling. Will circulate.

  Since such a water valveless system is employed, when the air conditioning unit configuration shown in FIGS. 10 and 11 is adopted, it becomes a major problem that the temperature of the air blown into the vehicle interior is increased during the maximum cooling and the maximum cooling performance is lowered.

  It has been found that the decrease in the maximum cooling performance is caused by the following two phenomena.

  FIG. 10 is a diagram for explaining a first factor of the maximum cooling performance deterioration, and the opening window 21a of the film door 21 is superposed simultaneously with the blowout openings 19 and 20, and the blowout openings 19 and 20 are both superposed. The state of the bilevel mode which opens simultaneously is shown in figure. Further, since the cold air side air mix door 18 fully opens the cold air passage 15 and the hot air side air mix door 17 fully closes the inlet air passage 16 of the heating heat exchanger 14, the maximum cooling state of the temperature control is achieved. Show.

  Here, the size of the opening window 21a of the film door 21 is designed to be large enough to open one of the blowout openings 19 and 20, so the air conditioning unit of the blowout openings 19 and 20 By opening only about half of the center opening, the remaining half of the outlet openings 19 and 20 (about half of the air conditioning unit outer side) is closed by the film film portions 21d and 21e of the film door 21.

  In the bi-level mode, the opening window 21 a of the film door 21 is not located immediately after the cold air passage 15 but at a position biased to the downstream side of the heating heat exchanger 14 when viewed from the cold air passage 15. Since the inflow of air to the heating heat exchanger 14 is blocked in the maximum cooling state, the main flow of the cold air flow j from the cold air passage 15 toward the opening window 21a (foot outlet opening 19) of the film door 21 is heated. It will incline toward the heat exchanger 14 side.

  FIG. 12 is a schematic cross-sectional view for explaining the inclination of the main flow of the cold air flow. Arrow a indicates the main flow direction of the cold air flow in the maximum cooling state of the bi-level mode, and θ is the inclination angle of the main flow of the cold air flow. is there. The inclination angle θ is an angle formed by the main flow direction a and the straight air flow direction b in the cold air passage 15.

  In FIG. 10, the film film portion 21 d on the foot outlet opening 19 side of the film door 21 acts as a wall portion that blocks the air flow, so that the region between the film film portion 21 d and the heat exchanger 14 for heating is used. A becomes a dead-end space for airflow. For this reason, in the region A, a part of the cold air flows and the static pressure becomes high.

  On the other hand, in the region C between the opening window portion 21a of the film door 21 and the heat exchanger 14 for heating, the main flow of the cold air flow passes, so the dynamic pressure component becomes high and the static pressure is correspondingly increased. Lower.

  And the area | region (area | region of the inlet ventilation path 16) B between the heat exchanger 14 for heating and the warm air side air mix door 17 is interrupted | blocked by the warm air side air mix door 17 with the upstream part of the cool air path 15; And it is connected with both the area | regions A and C through the space | gap part of the core part of the heat exchanger 14 for a heating. For this reason, the static pressure in the region B is an intermediate value between the regions A and C.

  That is, the relationship of static pressure in region A> static pressure in region B> static pressure in region C is established. As a result, a reverse flow circulation flow from the region A through the region B to the region C occurs between the regions A, B, and C as shown by the arrow c in FIG.

  With this backflow circulation flow c, air is heated in the core portion of the heat exchanger 14 for heating even in the maximum cooling state, and the warm air (heated air) is mixed into the cold air flow j toward the foot blowout opening 19 to cause the foot blowout. It turned out that the problem of raising the blowing air temperature by the side of the opening part 19 arises. That is, the generation of the air flow c passing through the core portion of the heat exchanger 14 for heating is the first factor of the maximum cooling performance deterioration.

  During the maximum cooling in the face mode in which the face blowing opening 20 is fully opened and the foot blowing opening 19 is fully closed at the opening window 21a of the film door 21 (see FIG. 2 described later), the cold air passage 15 The cold air flows so as to go straight toward the face blowout opening 20 and the entire regions A and C become dead-end spaces for the air flow, so that the static pressure difference between the regions A, B and C becomes small.

  As a result, in the face mode, the air flow c passing through the core portion of the heat exchanger 14 for heating is also small, so the reduction in the maximum cooling performance due to the air flow c is slight and does not cause a problem in practice.

  Next, FIG. 11 is a diagram for explaining the second factor of the maximum cooling performance deterioration, and in the same manner as in FIG. 10 described above, both the blowout openings 19 and 20 are formed at the opening window 21a of the film door 21. The maximum cooling state in the bi-level mode that opens simultaneously is shown.

  On the upper side of the heat exchanger 14 for heating, the warm air heated by the core portion is stopped by natural convection as indicated by an arrow d. Here, if the main flow of the cold air flow j is in a direction substantially orthogonal to the core surface of the heat exchanger 14 for heating as in the face mode, even if the warm air obscures due to natural convection, The degree to which this warm air is mixed with the cold air flow j is minimal. For this reason, the decrease in the maximum cooling performance is slight and does not cause a problem in practice.

  On the other hand, in the bi-level mode, as described with reference to FIG. 12, the main flow of the cold air flow j from the cold air passage 15 toward the opening window 21a (foot outlet opening 19) of the film door 21 is the heat for heating. Since it is inclined toward the exchanger 14, the warm air mist tends to be mixed into the main flow of the cold air flow.

  Further, since the region A in FIG. 10 forms a dead end space for the air flow, an air flow e that disturbs the downstream side of the core surface of the heating heat exchanger 14 including the region A is likely to be generated.

  Combined with these phenomena, warm air d due to natural convection from the core surface of the heat exchanger 14 for heating is mixed with the cold air flow j toward the foot blowing opening 19 to increase the foot blowing air temperature. This is the second factor that reduces the maximum cooling performance in the bi-level mode.

  By the way, if a hot water valve is provided in the hot water passage of the heating heat exchanger 14 and the hot water valve is operated to be closed during maximum cooling to shut off the hot water circulation to the heating heat exchanger 14, the above-mentioned “maximum cooling” is performed. The problem of “decrease in performance” can be solved.

  However, such measures not only increase the cost associated with the installation of the hot water valve, but also have another problem that the temperature control characteristic of the air blown into the passenger compartment is poor.

  This failure will be explained with reference to FIG. 13. FIG. 13 shows the blowout temperature control characteristic in the bilevel mode, and the broken line (1) in the figure is the foot blowout temperature in the bilevel mode in the prototypes of FIGS. The thin line (2) is the face blowing temperature in the bilevel mode. A thick solid line (3) is a foot blowing temperature in the bilevel mode according to the present invention described later. The horizontal axis in FIG. 13 is the air mix door opening degree (%) when the maximum cooling position is 0% and the maximum heating position is 100%.

  Even if a hot water valve is provided in the hot water passage of the heat exchanger 14 for heating, the hot water valve remains open at times other than during maximum cooling. Therefore, in the temperature control region on the maximum cooling side, the first and second factors described above are used. As a result, the foot blowing air temperature becomes considerably higher than the face blowing temperature of the thin line (2) as shown by the broken line (1).

  When the air mix doors 17 and 18 reach the maximum cooling state, the hot water valve shifts to the closed state and shuts off the hot water flow to the heating heat exchanger 14, so that the foot blown air temperature is at the level of the broken line (1). To a level of the face blowing temperature (2) at a stroke as indicated by an arrow z. On the contrary, when the air mix doors 17 and 18 shift from the maximum cooling state to the temperature control region, the foot blown air temperature rapidly rises from the level of the face blowout temperature (2) to the level of the broken line (1) immediately after the shift.

  Thus, if only the measure of installing the hot water valve is used, there arises a problem that the foot blown air temperature fluctuates suddenly near the maximum cooling state and the air conditioning feeling is deteriorated.

  In view of the above-described points, the present invention achieves both ensuring of maximum cooling performance and downsizing of an air conditioner in an air conditioner in which a high-temperature heat source fluid such as warm water circulates to a heating heat exchanger even during maximum cooling. The first purpose.

  In the air conditioner that stops the circulation of the high-temperature heat source fluid such as hot water to the heating heat exchanger at the maximum cooling, the present invention achieves both improvement of the control characteristic of the blown air temperature and the miniaturization of the air conditioner. This is the second purpose.

The present invention has been devised in order to achieve the above-mentioned object. The air flow rate ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) is adjusted by temperature adjusting means ( 17, 18, 30) to adjust the temperature in the passenger compartment,
In the vehicle air conditioner in which the high-temperature heat source fluid is circulated to the heating heat exchanger (14) even when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position.
An opening (19) that directly faces the heat exchanger for heating (14) is disposed in the air flow downstream side space of the heat exchanger for heating (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19),
Door means (21) for opening and closing the opening (19);
A wall portion (21d) that directly faces the heat exchanger (14) for heating is disposed in a portion of the opening portion (19) that is opposite to the cold air passage (15),
The wall (21d) is constituted by door means (21),
Further, the temperature from the heating heat exchanger (14) when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the space on the downstream side of the air flow of the heating heat exchanger (14). A partition plate (23) is arranged along the wind blowing direction,
The partition plate (23) has a first feature that the space portion on the downstream side of the air flow is divided into a region (24) on the cold air passage (15) side and a region (25) on the opposite side of the cold air passage (15). .

  According to the first feature of the present invention, in the vehicle air conditioner in which the high-temperature heat source fluid circulates in the heating heat exchanger (14) even at the maximum cooling, from the core surface of the heating heat exchanger 14 at the maximum cooling. It can suppress that the warm air by a natural convection mixes with the cool air flow which goes to an opening part (19).

  That is, the partition plate (23) separates the space portion on the downstream side of the air flow of the heat exchanger (14) for heating into the region (24) on the cold air passage (15) side and the region (25) on the opposite side of the cold air passage (15). Therefore, the cold air can be prevented from flowing into the region (25) on the side of the anti-cool air passage, and the cold air can be guided to the opening (19) side along the plate surface of the partition plate (23).

  As a result, it is possible to prevent the cool air flow (the flow indicated by the arrow e in FIG. 11) flowing into the region (25) on the anti-cool air passage (15) side along the air flow downstream core surface of the heat exchanger for heating (14). The air in the vicinity of the core surface on the downstream side of the air flow of the heat exchanger for heating (14) can be reliably prevented from being disturbed.

For this reason, at the time of maximum cooling, it can suppress that the warm air by the natural convection from the core surface of the heat exchanger 14 for a heating mixes with a cold wind flow, and can suppress the raise of the blowing air temperature from an opening part (19).
Further, the partitioning action of the partition plate (23) increases the static pressure in the region (25) on the anti-cooling air passage (15) side downstream of the heating heat exchanger (14), that is, the region A in FIG. Can be suppressed. For this reason, generation | occurrence | production of the backflow circulation flow c of FIG. 10 can also be suppressed.

  Therefore, even in a vehicle air conditioner that does not have a valve means for shutting off the flow of the high-temperature heat source fluid at the maximum cooling, the above-described action can be combined to ensure a satisfactory maximum cooling performance.

  Moreover, since the opening (19) is arranged in the air flow downstream space of the heating heat exchanger (14) so as to face the heating heat exchanger (14) directly, the heating heat exchanger By reducing the distance between (14) and the opening (19), the air conditioner can be downsized.

  Further, according to the first feature of the present invention, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position, the hot air is blown out from the heating heat exchanger (14). Since the partition plate (23) is arrange | positioned, it can suppress that a partition plate (23) becomes ventilation resistance at the time of maximum heating.

  Moreover, since the wall (21d) directly facing the heating heat exchanger (14) is constituted by the opening (19) opening / closing door means (21), the door means (21) is moved during maximum heating. The wall (21d) can be moved to a position not directly facing the heating heat exchanger (14).

  For this reason, the trouble that the warm air flow which passes a heat exchanger (14) for a heating by a wall part (21d) at the time of maximum heating can be avoided. As described above, the maximum heating performance can be satisfactorily exhibited without hindrance despite the presence of the partition plate (23) and the wall (21d).

  In the present invention, a specific example of the high temperature heat source fluid of the heating heat exchanger (14) is typically hot water (cooling water) of a vehicle engine, but oil or the like is used as the high temperature heat source fluid in addition to the hot water. May be. The low-temperature heat source fluid of the cooling heat exchanger (13) may be not only low-temperature refrigerant of the refrigeration cycle but also cold water cooled by the low-temperature refrigerant of the refrigeration cycle.

Next, in the present invention, the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) is adjusted by the temperature adjusting means (17, 18, 30). Adjust the indoor blowout temperature,
In the vehicle air conditioner in which the high-temperature heat source fluid is circulated to the heating heat exchanger (14) even when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position.
Openings (19, 27) directly facing the heating heat exchanger (14) are arranged in the space on the air flow downstream side of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heat exchanger (14) for heating toward the opening (19, 27),
Wall parts (21d, 29) directly facing the heat exchanger for heating (14) are arranged in a part of the openings (19, 27) opposite to the cold air passage (15),
Furthermore, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger (14) A partition plate (22) is arranged along the flow direction of the air flowing into the
The partition plate (22) partitions the air flow upstream space (16) into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side of the cold air passage (15). It is a feature.

  The second feature of the present invention differs from the first feature in that a partition plate (22) is disposed in the air flow upstream space (16) of the heat exchanger for heating (14). Yes.

  According to the second feature of the present invention, the partition (22) causes the space (16) on the upstream side of the air flow of the heat exchanger (14) for heating to the region (16a) on the cold air passage (15) side and the cold air passage. (15) and the region (16b) on the opposite side, the static pressure in the region (16b) on the side of the anti-cooling air passage (static pressure in region B in FIG. 10) is converted to the downstream side of the heat exchanger (14) for heating. It can be brought close to the static pressure in the region (25) on the anti-cool air passage side, that is, the dead end region A in FIG.

  For this reason, the static pressure difference between the upstream side and the downstream side of the heat exchanger for heating (14) can be reduced. In addition to this, the partition plate (22) serves to partition the upstream space (16), so that the backflow circulation flow c in FIG. 10 can be suppressed. Accordingly, it is possible to suppress a decrease in the maximum cooling performance due to the backflow circulation flow c.

  According to the second feature of the present invention, as in the first feature, it is possible to satisfactorily achieve the maximum cooling performance and the miniaturization of the vehicle air conditioner.

  Moreover, since the partition plate (22) is arranged in the air flow upstream space (16) of the heat exchanger (14) for heating, the wall (21d, 21) directly facing the heat exchanger (14) for heating. The maximum heating performance by the heat exchanger for heating (14) can be satisfactorily exhibited without any trouble even if the door means (21) is not configured to be movable by 29).

Next, in the present invention, the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) is adjusted by the temperature adjusting means (17, 18, 30). Adjust the indoor blowout temperature,
On the other hand, when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position, the heating heat exchanger (31) is provided by the valve means (31) provided in the high-temperature heat source fluid passage of the heating heat exchanger (14). 14) in a vehicle air conditioner that interrupts the circulation of the high-temperature heat source fluid to
An opening (19) that directly faces the heat exchanger for heating (14) is disposed in the air flow downstream side space of the heat exchanger for heating (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19),
Door means (21) for opening and closing the opening (19);
A wall portion (21d) that directly faces the heat exchanger (14) for heating is disposed in a portion of the opening portion (19) that is opposite to the cold air passage (15),
The wall (21d) is constituted by door means (21),
Further, the temperature from the heating heat exchanger (14) when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the space on the downstream side of the air flow of the heating heat exchanger (14). A partition plate (23) is arranged along the wind blowing direction,
A third feature of the partition plate (23) is that the space portion on the downstream side of the air flow is divided into a region (24) on the cold air passage (15) side and a region (25) on the opposite side of the cold air passage (15). .

  The third feature of the present invention is that, with respect to the first feature, a valve means (31) is provided in the high-temperature heat source fluid passage of the heating heat exchanger (14), and heating is performed by this valve means (31) during maximum cooling. The difference is that the circulation of the high-temperature heat source fluid to the industrial heat exchanger (14) is interrupted.

  According to the third feature of the present invention, the air heating action of the heating heat exchanger (14) can be stopped by interrupting the circulation of the high-temperature heat source fluid to the heating heat exchanger (14) during maximum cooling. Therefore, the maximum cooling performance can be demonstrated reliably.

  In addition, in the temperature control region near the maximum cooling state, warm air from the heating heat exchanger (14) is generated by the partition plate (23) arranged in the space portion on the downstream side of the air flow of the heating heat exchanger (14). Since excessive mixing with the cold air flow can be suppressed, it is possible to suppress a sudden change in the temperature of the blown air before and after the high temperature heat source fluid flow is interrupted by the valve means (31), that is, before and after switching to the maximum cooling state (described later). 13 foot blowing air temperature (see (3)). Thereby, the control characteristic of the blowing air temperature can be improved.

  Moreover, it is the same as the first and second features that the distance between the heating heat exchanger (14) and the opening (19) can be reduced to reduce the size of the air conditioner.

Next, in the present invention, the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) is adjusted by the temperature adjusting means (17, 18, 30). Adjust the indoor blowout temperature,
On the other hand, when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position, the heating heat exchanger (31) is provided by the valve means (31) provided in the high-temperature heat source fluid passage of the heating heat exchanger (14). 14) in a vehicle air conditioner that interrupts the circulation of the high-temperature heat source fluid to
Openings (19, 27) directly facing the heating heat exchanger (14) are arranged in the space on the air flow downstream side of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heat exchanger (14) for heating toward the opening (19, 27),
Wall parts (21d, 29) directly facing the heat exchanger for heating (14) are arranged in a part of the openings (19, 27) opposite to the cold air passage (15),
Furthermore, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger (14) A partition plate (22) is arranged along the flow direction of the air flowing into the
The partition plate (22) partitions the air flow upstream space (16) into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side of the cold air passage (15). It is a feature.

  The fourth feature of the present invention is that, with respect to the second feature, valve means (31) is provided in the high-temperature heat source fluid passage of the heating heat exchanger (14), and heating is performed by this valve means (31) during maximum cooling. The difference is that the circulation of the high-temperature heat source fluid to the industrial heat exchanger (14) is interrupted.

  According to the fourth feature of the present invention, the air heating action of the heating heat exchanger (14) can be stopped by interrupting the circulation of the high-temperature heat source fluid to the heating heat exchanger (14) during maximum cooling. Therefore, the maximum cooling performance can be demonstrated reliably.

  In addition, in the temperature control region near the maximum cooling state, the partition plate (22) arranged in the air flow upstream space (16) of the heating heat exchanger (14) is separated from the heating heat exchanger (14). Therefore, it is possible to suppress the sudden change in the temperature of the blown air before and after the high-temperature heat source fluid flow is interrupted by the valve means (31), that is, before and after switching to the maximum cooling state. Thereby, the control characteristic of the blowing air temperature can be improved.

  Moreover, it is the same as the first to third features that the distance between the heating heat exchanger (14) and the opening (19) can be reduced to reduce the size of the air conditioner.

  Next, in the present invention, specifically, the region (25) opposite to the cold air passage (15) is made into the cold air passage (15) by the combination of the partition plate (23) and the wall (21d) on the downstream side of the air flow. It may be cut off from the cold air flow from 15).

  According to this, the anti-cold air passage side region (25) on the downstream side of the air flow of the heat exchanger for heating (14) can be reliably cut off from the cold air flow, so that it is possible to more reliably suppress the warm air from mixing with the cold air flow. .

Further, in the present invention, as described above, the partition plate (23) is arranged in the air flow downstream space portion of the heating heat exchanger (14).
When the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger (14) Arranging the partition plate (22) on the upstream side of the air flow along the flow direction of the inflowing air,
The partition plate (22) on the upstream side of the air flow partitions the upstream space portion (16) into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side of the cold air passage (15). You may do it.

  That is, the partition plate (23) on the downstream side of the air flow and the partition plate (22) on the upstream side of the air flow may be combined. According to this, the effect can be further improved in terms of ensuring the maximum cooling state and improving the control characteristic of the blown air temperature.

Further, in the present invention, the partition plate (22) on the upstream side of the air flow and the partition plate (23) on the downstream side of the air flow are disposed to be inclined with respect to the heat exchanger (14) for heating,
Arrangement direction of a plurality of regions (16a, 16b, 24, 25) with the partition plate (22) on the upstream side of the air flow and the partition plate (23) on the downstream side of the air flow sandwiching the heat exchanger for heating (14) ( You may make it partially wrap in the (X direction of FIG. 1).

  In other words, when combining the two partition plates (22, 23) on the upstream side and the downstream side of the air flow, the lap portion of the two partition plates (22, 23) is changed in the dimension variation of the partition plates (22, 23). Design in advance so that it can be maintained without being affected. Thereby, it can suppress that air passes through the site | part between two partition plates (22, 23) among the heat exchangers for heating (14), and the partition effect | action of two partition plates (22, 23) can be carried out. It can be improved.

Moreover, in this invention, the air flow upstream space part (16) of the heat exchanger for heating (14), specifically, the air flow upstream core surface of the heat exchanger for heating (14) and the maximum cooling. A space formed between the temperature adjusting means (17, 18, 30) at the position,
The partition plate (22) on the upstream side of the air flow is sandwiched between the core surface on the upstream side of the air flow of the heat exchanger (14) for heating and the temperature adjusting means (17, 18, 30) at the maximum cooling position. May be arranged.

Further, in the present invention, specifically, it has a hot air side air mix door (17) constituted by a plate-like door that can rotate as a temperature adjusting means,
The partition plate (22) on the upstream side of the air flow may be arranged along the back surface of the hot air side air mix door (17) in the maximum heating position.

In the present invention, more specifically, the heat exchanger for heating (14) has a number of tubes (14a) through which a high-temperature heat source fluid flows,
The longitudinal direction of the tube (14a) and the direction of the plate surfaces of the partition plates (22, 23) are the same direction.

  According to this, since the plate | board surface of a partition plate (22, 23) extends along the longitudinal direction of a tube (14a), space partition effect | action is carried out by the joint action of a tube (14a) and a partition plate (22, 23). It can be done more reliably.

  Further, in the present invention, specifically, the cold air flow from the cold air passage (15) is opened near the end on the cold air passage (15) side in the downstream portion of the air flow of the heating heat exchanger (14). You may arrange | position the air guide plate (26) guided so that it may go to a part (19) side.

  According to this, since the cold air flow can be guided by the air guide plate (26) in the direction away from the core surface on the downstream side of the air flow of the heating heat exchanger (14), the warm air from the heating heat exchanger (14) Mixing with the cold air flow can be further suppressed.

  Further, in the present invention, in the second and fourth features described above, it is needless to say that door means (21) for opening and closing the opening (19) may be provided.

  In the present invention, the door means is specifically constituted by a slide door (21) that moves in a direction orthogonal to the air flow toward the opening (19), and the wall (21d) is formed by the slide door (21). You may comprise by.

  According to this, since the slide door (21) moves in the direction orthogonal to the air flow toward the opening (19), the slide door (21) is moved along the core surface of the heat exchanger for heating (14). be able to.

  For this reason, the working space of the slide door (21) can be greatly reduced as compared with the rotary plate door. As a result, the slide door (21) can be arranged close to the downstream side of the heating heat exchanger (14) along the core surface of the heating heat exchanger (14), and the size of the indoor air conditioning unit is small. It is advantageous to make.

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

(First embodiment)
FIG. 1A is a cross-sectional view showing the indoor air conditioning unit 10 of the vehicle air conditioner according to the first embodiment, and the up and down arrows in FIG. 1A indicate directions in the vehicle mounted state. FIG. 1B is a front view of the heating heat exchanger alone. The indoor air conditioning unit 10 is for air conditioning the rear seat side of the vehicle interior. The indoor air conditioning unit 10 on the rear seat side is mounted, for example, on the left and right vehicle body side wall portions in the rear seat side region of the vehicle interior in a wagon type vehicle.

  The indoor air-conditioning unit 10 includes a resin air-conditioning case 11 that forms a passage for air flowing toward the passenger compartment. The air-conditioning case 11 is actually formed as a plurality of divided case bodies for convenience in resin molding, assembly of built-in components, and the like. And the air-conditioning case 11 is comprised by fastening this some division | segmentation case body integrally by fastening means, such as a screw and a clip. In this example, the air-conditioning case 11 includes a left-side divided case body and a right-side divided case body that are divided in the vehicle left-right direction (the direction perpendicular to the plane of FIG. 1A).

  In the air conditioning case 11, the blower unit 12 is integrally disposed at an upper part on the front side of the vehicle. The blower unit 12 includes a centrifugal blower fan 12a that is rotationally driven by a motor (not shown), and a scroll casing 12b that houses the blower fan 12a.

  The blower unit 12 sucks the vehicle interior air (inside air) and blows it toward the lower space of the cooling heat exchanger 13 as indicated by an arrow f. Specifically, the cooling heat exchanger 13 includes an evaporator that evaporates the low-pressure refrigerant in the refrigeration cycle, and cools the blown air by absorbing the low-pressure refrigerant from the blown air and evaporating it.

  The cooling heat exchanger 13 is disposed in a lower portion of the internal space of the air conditioning case 11 in a state inclined at a predetermined angle from the horizontal plane. The cooling heat exchanger 13 has a heat exchange core portion 13a composed of a well-known tube and fin, and the blown air passes through the heat exchange core portion 13a from below to above as indicated by an arrow g.

  In the air conditioning case 11, a heating heat exchanger 14 is disposed on the downstream side (upper side) of the cooling heat exchanger 13 and on the front side of the vehicle. The heating heat exchanger 14 heats the air (cold air) after passing through the cooling heat exchanger 13 with hot water (engine cooling water). Similarly to the cooling heat exchanger 13, the heating heat exchanger 14 is also arranged in a state inclined at a predetermined angle from the horizontal plane.

  As shown in FIG. 1 (b), the heating heat exchanger 14 has a rectangular shape in which the longitudinal direction X of the vehicle is the longitudinal direction, and a large number of flat tubes 14a and corrugated fins 14b forming a hot water passage are arranged in the longitudinal direction of the vehicle. The layers are alternately stacked and bonded in the direction X. The flat tube 14a and the corrugated fin 14b constitute a heat exchange core portion 14c.

  Accordingly, in the present embodiment, the longitudinal direction of the tube 14a (the direction of the arrow h in FIG. 1B) is directed to the left-right direction of the vehicle (the direction perpendicular to the plane of FIG. 1A). One end of the tube 14a is joined to the hot water inlet tank 14d and communicates with the hot water inlet tank 14d. The other end of the tube 14a is joined to the hot water outlet tank 14e and communicates with the inside of the hot water outlet tank 14e.

  Thus, the heating heat exchanger 14 is configured as a one-way flow type (all-pass type) in which the hot water in the hot water inlet tank 14d passes through all the tubes 14a and goes to the hot water outlet tank 14e. In a state other than the maximum cooling, the blown air passes from the lower side to the upper side as shown by the broken line arrow i in FIG.

  Both the inlet pipe 14f of the hot water inlet tank 14d and the outlet pipe 14g of the hot water outlet tank 14e protrude to the outside of the air conditioning case 11 (the vehicle front side) and are connected to the hot water passage of the vehicle engine. Here, since a hot water valve that interrupts the flow of hot water is not installed in the hot water passage of the heat exchanger 14 for heating, the hot water (cooling water) of the vehicle engine is heated for heating when the vehicle engine (not shown) is operated. It always circulates in the exchanger 14.

  And in the air-conditioning case 11, the cold wind path 15 is formed in parallel in the side part of the one end side (vehicle rear side) of the heat exchanger 14 for a heating. Therefore, the arrangement (arrangement) direction of the heat exchanger 14 for heating and the cool air passage 15 is also the vehicle longitudinal direction X. The cold air passage 15 is a passage through which air (cold air) that has passed through the cooling heat exchanger 13 flows bypassing the heating heat exchanger 14.

  In the air conditioning case 11, an inlet ventilation path of the heating heat exchanger 14, that is, an upstream space portion 16 is formed on the upstream side (lower side) of the heating heat exchanger 14. A warm air side air mix door 17 is disposed in the upstream space 16 so as to be rotatable about a rotation shaft 17a.

  The warm air side air mix door 17 is a butterfly door in which a rotating shaft 17a is arranged at the center of the plate-like door shape, and is heated by the heating heat exchanger 14 by adjusting the opening degree of the upstream space portion 16. Adjust the air volume of warm air i.

  A cold air side air mix door 18 is disposed in the cold air passage 15 so as to be rotatable about a rotation shaft 18a. The cold air side air mix door 18 is also a butterfly door in which a rotating shaft 18a is arranged at the center of the plate-like door shape, and the amount of the cold air j passing through the cold air passage 15 is adjusted by adjusting the opening degree of the cold air passage 15. adjust.

  It should be noted that the air mix doors 17 and 18 have one air flow so that the air volume of the cold air j decreases as the air volume of the hot air i increases, and conversely, the air volume of the hot air i decreases as the air volume of the cold air j3 increases. The interlocking operation is performed by a common door drive mechanism (not shown).

  A rear seat side foot outlet opening 19 and a rear seat side face outlet opening 20 are arranged on the upper surface of the air conditioning case 11 side by side in the vehicle front-rear direction. Here, the opening shape of both the blowing openings 19 and 20 is rectangular.

  The rear-seat-side foot blowout opening 19 is disposed at a portion immediately after blowout of the heating heat exchanger 14 (above the heating heat exchanger 14) so as to directly face the core surface of the heating heat exchanger 14. The On the other hand, the rear-seat-side face blowout opening 20 is disposed so as to directly face the cold air passage 15 at a portion (upper part of the cold air passage 15) immediately downstream of the cold air passage 15.

  A rear-seat-side foot outlet duct (not shown) is connected to the rear-seat-side foot outlet opening 19, and air is blown out from the front end outlet of the rear-seat-side foot outlet duct to the passenger's feet on the rear seat side in the vehicle interior. A rear seat face blowout duct (not shown) is connected to the rear seat face blowout opening 20, and air is blown out from the front outlet of the rear seat face blowout duct to the passenger head side on the vehicle rear seat side. In the present embodiment, the rear seat side foot outlet 19 corresponds to the opening of the present invention.

  In the present embodiment, the blowing mode switching door for switching the air flow to the rear seat side foot blowing opening 19 and the rear seat side face blowing opening 20 is provided along the inner wall surface of the upper surface portion of the air conditioning case 11. It is constituted by a sliding door that moves in the arrangement direction (vehicle longitudinal direction) X of the parts 19 and 20.

  Specifically, this slide door is constituted by a film door 21. This film door 21 itself is a well-known thing comprised with the resin-made thin film-like film material which has flexibility. An opening window portion 21 a for passing air is opened at an intermediate position in the longitudinal direction of the film door 21.

  And the winding shafts 21b and 21c of the film door 21 are rotatably arrange | positioned by the inner side of the upper surface part of the air-conditioning case 11 and the both ends vicinity of the arrangement direction (vehicle front-back direction) X of both the blowing openings 19 and 20. Yes. Both end portions of the film door 21 in the longitudinal direction are connected to the take-up shafts 21b and 21c so as to be rewound and rewound. The take-up shafts 21b and 21c are rotated in conjunction with each other by a common door drive mechanism (not shown) (not shown).

  By rotating the take-up shafts 21b and 21c, both ends in the longitudinal direction of the film door 21 are taken up or rewound onto the take-up shafts 21b and 21c. Thereby, the position of the opening window part 21a moves to the arrow X direction, and both the blowing opening parts 19 and 20 are opened and closed.

  Here, the opening window portion 21a has a rectangular opening shape corresponding to the opening shape of both the blowing opening portions 19 and 20, and the opening area of the opening window portion 21a is the opening area of both the blowing opening portions 19 and 20. It is set slightly larger than. Thereby, the opening window part 21a can be entirely overlapped on the rear seat side foot outlet opening part 19 or the rear seat side face outlet opening part 20, and the rear seat side foot outlet opening part 19 or the rear seat side face outlet. The opening 20 can be fully opened.

  In addition, the film portions 21d and 21e formed on both front and rear sides of the opening window portion 21a of the film door 21 are superposed on the rear seat side foot outlet opening 19 or the rear seat side face outlet opening 20 as a whole. The rear seat side foot outlet opening 19 or the rear seat side face outlet opening 20 can be fully closed.

  1A shows a state of the bi-level mode in which the opening window portion 21a of the film door 21 is overlapped with a portion closer to the center of both the blowing openings 19 and 20, and both the blowing openings 19 and 20 are simultaneously opened. It is shown.

  Next, the first and second partition plates 22 and 23 for ensuring the maximum cooling performance in the present embodiment will be described. The first partition plate 22 is a plate-like member disposed on the upstream side (lower side) of the heating heat exchanger 14, and the upstream partition 16 of the heating heat exchanger 14 is an area on the cold air passage 15 side. It partitions into 16a and the area | region 16b on the opposite side to the cold wind channel | path 15. As shown in FIG.

  In other words, the first partition plate 22 partitions the upstream space portion 16 into two regions 16a and 16b in the arrangement direction (vehicle longitudinal direction) X of the heat exchanger 14 for heating and the cool air passage 15. For this reason, the first partition plate 22 has a plate shape extending in the direction perpendicular to the plane of FIG.

  The solid line position in FIG. 1A of the hot air side air mix door 17 is the maximum cooling position where the upstream space portion 16 is fully closed, and one end (lower end) of the first partition plate 22 is the maximum cooling position. Is located near the plate surface of the hot air side air mix door 17 and the other end portion (upper end portion) of the first partition plate 22 is located near the upstream core surface of the heat exchanger 14 for heating. A partition plate 22 is disposed.

  1 (a) is a center line in the longitudinal direction (vehicle longitudinal direction) of the heating heat exchanger 14, and the other end (upper end) of the first partition plate 22 is more specific. Is positioned slightly ahead of the center line Y by a certain amount.

  The position of the two-dot chain line in FIG. 1A of the hot air side air mix door 17 is the maximum heating position at which the upstream space portion 16 is fully opened, and the main stream of the air flow in the upstream space portion 16 during this maximum heating. On the other hand, the first partition plate 22 is arranged on the back side of the maximum heating position of the hot air side air mix door 17 along the plate surface of the hot air side air mix door 17 so that the first partition plate 22 does not become a ventilation resistance. Has been. Thereby, the 1st partition plate 22 is inclinedly arrange | positioned with respect to the upstream core surface of the heat exchanger 14 for a heating.

  A gap S is set between the plate surface of the hot air side air mix door 17 and the first partition plate 22 at the maximum heating position of the hot air side air mix door 17. The gap S prevents the noise from being generated when the plate surface of the hot air side air mix door 17 contacts the first partition plate 22.

  Next, the 2nd partition plate 23 is a plate-shaped member arrange | positioned in the downstream (upper side) of the heat exchanger 14 for heating, Comprising: The downstream space (space immediately after blowing) of the heat exchanger 14 for heating Is divided into a region 24 on the cold air passage 15 side and a region 25 on the opposite side of the cold air passage 15.

  In other words, the second partition plate 23 partitions the downstream space of the heating heat exchanger 14 into two regions 24 and 25 in the arrangement direction (vehicle longitudinal direction) X of the heating heat exchanger 14 and the cold air passage 15. is there. For this reason, the second partition plate 23 has a plate shape extending in the direction perpendicular to the plane of FIG.

  The second partition plate 23 is placed on the downstream core surface along the main flow of the hot air flow immediately after the heat exchanger 14 for heating at the time of maximum heating so that the second partition plate 23 does not become a ventilation resistance at the time of maximum heating. It is inclined with respect to it.

  The operation position of the film door 21 in FIG. 1A is the bi-level mode position as described above, and the film portion 21d on the vehicle front side of the opening window portion 21a is located on the downstream core surface of the heat exchanger 14 for heating. Since the wall faces directly opposite each other, the region 24 becomes a dead end space for the air flow due to the presence of the film portion 21d.

  Therefore, one end portion (upper end portion) of the second partition plate 23 is located in the vicinity of the opening window portion 21a in the film portion 21d on the vehicle front side of the film door 21 in the bi-level mode position, and the second partition plate 23. The 2nd partition plate 23 is arrange | positioned so that the other end part (lower end part) of this may be located in the downstream core surface vicinity of the heat exchanger 14 for a heating.

  More specifically, the other end portion (lower end portion) of the second partition plate 23 is positioned on the vehicle rear side by a slight amount from the center line Y of the heat exchanger 14 for heating. Thus, the second partition plate 23 and the first partition plate 22 are wrapped by a predetermined amount in the arrangement direction (vehicle longitudinal direction) X of the plurality of regions 16a, 16b, 24, 25 with the heat exchanger 14 for heating interposed therebetween. Inclined arrangement in relation.

  Next, the air guide plate 26 is a plate-like member disposed in the vicinity of the end on the cold air passage 15 side in the downstream portion of the air flow of the heat exchanger 14 for heating, and is the paper surface of FIG. It has a plate shape extending in the vertical direction (vehicle left-right direction).

  The air guide plate 26 is inclined from the vicinity of the end of the heating heat exchanger 14 on the cold air passage 15 side to the side away from the downstream core surface of the heating heat exchanger 14 (upper side in FIG. 1A). Then, the cool air flow j from the cool air passage 15 is guided toward the foot blowing opening 19 side.

  The first partition plate 22, the second partition plate 23, and the air guide plate 26 described above can be formed as separate parts from the air conditioning case 11, or can be integrally formed with the air conditioning case 11.

  In the case of separate parts, there is a problem in assembling such that each separate part is sandwiched at a predetermined position inside the air conditioning case 11 or fixed by bonding or the like. For this purpose, it is preferable that the first partition plate 22, the second partition plate 23, and the air guide plate 26 are all integrally formed with the air conditioning case 11.

  In the present embodiment, as described above, the air conditioning case 11 is composed of the left-side divided case body and the right-side divided case body that are divided in the vehicle left-right direction, so the first partition plate 22, the second partition plate 23, and the air guide. Both plates 26 are divided in the left-right direction of the vehicle, and are integrally molded with the left divided case body and the right divided case body with resin.

  When the left and right divided case bodies are fastened together by fastening means such as screws and clips, the front end portions of the left and right divided first partition plate 22, second partition plate 23, and air guide plate 26 are brought into contact with each other. You can do it.

  However, since the left and right divided case bodies, which are resin molded products, have considerably large dimensional variations compared to the metal molded products, it is difficult to accurately abut and fit the tip portions to each other. Therefore, the dimensions of the first partition plate 22, the second partition plate 23, and the air guide plate 26 of the left and right divisions are set so that a slight amount of gap is generated between the tip portions. It is practical to have a design that prevents abnormal noise caused by the generated minute gap.

  Next, the operation of this embodiment in the above configuration will be described. FIG. 1A shows the bi-level mode, in which the blowing mode switching film door 21 is operated to the bi-level mode position where both the blowing openings 19 and 20 are simultaneously opened. Further, the air mix doors 17 and 18 are respectively operated to the maximum cooling position indicated by solid lines, the upstream space portion 16 of the heating heat exchanger 14 is fully closed, and the cold air passage 15 is fully opened.

  Therefore, when the blower fan 12a of the blower unit 12 and the compressor of the refrigeration cycle (not shown) are operated, the blown air of the blower fan 12a is cooled by the cooling heat exchanger 13 and becomes cold air. The total amount of the cold air passes through the cold air passage 15 (bypassing the heat exchanger 14 for heating) and travels to both the blowing openings 19 and 20.

  Here, in this embodiment, since the hot water valve is not provided in the hot water passage of the heating heat exchanger 14, the hot water circulates in the heating heat exchanger 14 even during maximum cooling. Moreover, since the foot outlet opening 19 is directly disposed immediately after the heating heat exchanger 14 is blown out, there is a concern that the maximum cooling performance is reduced due to warm air heated by the heating heat exchanger 14. According to the embodiment, the maximum cooling performance can be satisfactorily secured by the device described below.

  That is, the downstream space immediately after the heating heat exchanger 14 is blown off is divided into a region 24 on the cold air passage 15 side and a region 25 on the anti-cool air passage 15 side by the second partition plate 23, and the region 25 is The two partition plates 23 and the film portion 21 d of the film door 21 are substantially cut off from the cold air flow j toward the foot blowing opening 19.

  For this reason, the phenomenon that the cold air flows into the region 25 forming the dead end space and the static pressure in the region 25 is increased does not occur. Thereby, the static pressure difference between the region 25 and the region 24 is reduced.

  In addition to this, the first partition plate 22 and the second partition plate 23 respectively heat the upstream space portion 16 of the heating heat exchanger 14 and the downstream space immediately after the heating heat exchanger 14 is blown out. And the cold air passage 15 are partitioned into two regions 16a, 16b, 24, and 25 in the arrangement direction X. Therefore, the air flow c circulating between the regions A, B, and C described with reference to FIG. Can be suppressed.

  On the other hand, in the downstream space immediately after the heating heat exchanger 14 blows, in the region 24 on the cold air passage 15 side, the phenomenon that the warm air heated by the core portion 12c is disturbed by natural convection (the arrow in FIG. 11). However, according to the present embodiment, the partitioning action of the second partition plate 23 prevents the cool air from flowing into the region 25 on the anti-cool air passage 15 side, and at the same time, the air guide plate 26 removes the cool air from the cool air passage 15. The cool air is guided away from the downstream side of the core surface of the heat exchanger 14 for heating and toward the foot blowout opening 19 side.

  Thereby, generation | occurrence | production of the air flow e (refer FIG. 11) which disturbs the core surface downstream of the heat exchanger 14 for heating can be suppressed. Therefore, it is possible to effectively suppress the dullness of warm air d due to natural convection from mixing with the cold air from the cold air passage 15.

  As described above, in the present embodiment, the circulating air flow (warm air flow) due to the static pressure difference between the upstream and downstream spaces of the heat exchanger 14 for heating can be suppressed, and the mixing of warm air due to natural convection is prevented. Since it can suppress, the increase in foot blowing temperature in the maximum cooling state in the bi-level mode can be suppressed to ensure the maximum cooling performance.

  In FIG. 13, a thick solid line (3) indicates the foot blowing temperature according to the present embodiment. As can be understood from the thick solid line (3), according to the present embodiment, the foot blowing temperature can be lowered to the vicinity of the face blowing temperature indicated by the thin line (2) in the maximum cooling state, whereby the maximum cooling performance can be satisfactorily exhibited. .

  An air flow may circulate between the region 16a on the cold air passage 15 side partitioned by the first partition plate 22 and the region 24 on the cold air passage 15 side partitioned by the second partition plate 23. Since this air flow is much smaller than the air flow c in FIG. 10, it does not become a major obstacle to the maximum cooling performance.

  By the way, in this embodiment, since the longitudinal direction of the tube 14a of the heating heat exchanger 14 is set to a direction (vehicle left-right direction) orthogonal to the arrangement direction X of the heating heat exchanger 14 and the cold air passage 15, the first The plate-shaped tip portions of the partition plate 22 and the second partition plate 23 can be disposed along the longitudinal surface of the tube 14a.

  Thereby, the space on the upstream side and the downstream side of the heating heat exchanger 14 can be partitioned well by the joint action of the plate shape of the first partition plate 22 and the second partition plate 23 and the longitudinal shape of the tube 14a. .

  Further, in the present embodiment, the other end portion (upper end portion) of the first partition plate 22 is positioned slightly toward the front side of the vehicle by the center line Y in the longitudinal direction (vehicle longitudinal direction) of the heat exchanger 14 for heating. In contrast, the other end portion (lower end portion) of the second partition plate 23 is positioned slightly behind the center line Y of the heating heat exchanger 14 on the vehicle rear side.

  Thereby, the 2nd partition plate 23 and the 1st partition plate 22 have the arrangement relationship which wrapped the predetermined amount in the longitudinal direction of the heat exchanger 14 for heating on both sides of the heat exchanger 14 for heating.

  According to this, even if the dimensional variation of the two partition plates 22 and 23 occurs to some extent, if the dimensional variation is within a predetermined amount, the lap arrangement state between the end portions of the two partition plates 22 and 23 can be maintained. . As a result, it is possible to reliably partition the upstream and downstream spaces of the heating heat exchanger 14 without being affected by dimensional variations.

  Incidentally, when both the upper end part of the 1st partition plate 22 and the lower end part of the 2nd partition plate 23 are set so that it may arrange | position on the centerline Y, and the above wrap arrangement | positioning is not employ | adopted, both partition plates 22 are used. Under the influence of the dimensional variation of, 23, it is easy to generate a region where air can flow between the tip portions of the two partition plates 22, 23 (near the center line Y), thereby deteriorating the partitioning action.

  Next, FIG. 2 shows the time of maximum cooling in the face mode, where the opening window 21a of the film door 21 for switching the blowing mode is operated to a position where it completely overlaps with the face blowing opening 20, and the face blowing opening 20 is moved. Fully open. On the other hand, the foot blowing opening 19 is fully closed by the film part 21d of the film door 21.

  On the other hand, the air mix doors 17 and 18 are operated to the maximum cooling position where the upstream space 16 of the heating heat exchanger 14 is fully closed and the cold air passage 15 is fully opened, as in the bi-level mode. Yes.

  During the maximum cooling in the face mode, the cool air from the cold air passage 15 flows almost straight toward the face blowing opening 20. In other words, the cold air does not flow inclined toward the outlet downstream side of the heating heat exchanger 14.

  As a result, even in a system in which hot water is constantly circulated through the heating heat exchanger 14 even during maximum cooling (a system in which a hot water valve is not installed in the hot water passage of the heating heat exchanger 14), the heating heat exchanger 14 is heated. The degree to which the warm air is mixed into the cold air flow becomes small. Therefore, in the face mode, the problem that the maximum cooling performance cannot be ensured does not naturally occur.

  Next, FIG. 3 shows the time of maximum heating in the foot mode, where the opening window portion 21a of the film door 21 for switching the blowing mode is operated to a position where it completely overlaps with the foot blowing opening portion 19, and the foot blowing opening portion 19 is opened. Fully open. On the other hand, the face blowing opening 20 is fully closed by the film part 21e of the film door 21.

  On the other hand, the air mix doors 17 and 18 are operated to a maximum heating position where the upstream space portion 16 of the heating heat exchanger 14 is fully opened and the cold air passage 15 is fully closed. As a result, the entire amount of air (cold air) that has passed through the cooling heat exchanger 13 flows from the upstream space portion 16 into the core portion 14c of the heating heat exchanger 14 and is heated to become hot air.

  This warm air passes through the foot outlet opening 19 and blows out to the passenger's feet in the passenger compartment to heat the passenger compartment. At this time, since the first partition plate 22 is disposed substantially parallel to the maximum heating position of the hot air side air mix door 17, the ventilation resistance of the upstream space portion 16 hardly increases. Moreover, since the 2nd partition plate 23 is arrange | positioned substantially parallel to the warm air flow which goes to the foot blowing opening part 19 from the blowing side of the heat exchanger 14 for heating, the ventilation resistance of the blowing side of the heat exchanger 14 for heating There is little increase.

  And since the opening window part 21a of the film door 21 opens the foot blowing opening part 19 entirely at the time of maximum heating, the area | region 25 also becomes a flow path of a warm air flow. In other words, the region 25 is not a dead end space. Therefore, air can be heated using the whole core part 14c of the heat exchanger 14 for heating, and the heated air (warm air) can be fed into the foot outlet opening 19 with a small ventilation resistance.

  As described above, even if the first and second partition plates 22 and 23 are installed, the maximum heating performance can be satisfactorily exhibited without any trouble.

  In the face mode and the bi-level mode, the region 25 is blocked by the joint action of the film part 21e of the film door 21 and the second partition plate 23, and the region 25 becomes a dead end space. Of the 14 core portions 14c, the portion on the region 25 side does not substantially act as an air heating portion, and only the portion on the region 24 side acts as an air heating portion.

  However, since the face mode and the bi-level mode are basically used under conditions where the necessity of heating is low, it is not necessary to exhibit the maximum heating performance. Therefore, there is no practical problem even if the area 25 becomes a dead end space in the face mode and the bi-level mode.

(Second Embodiment)
In 1st Embodiment, although the partition plates 22 and 23 are installed in both the air flow upstream and downstream of the heat exchanger 14 for heating, in 2nd Embodiment, as shown in FIG. The partition plate 22 on the upstream side of the air flow of the exchanger 14 is eliminated, and the partition plate 23 is installed only on the downstream side of the air flow of the heat exchanger 14 for heating. FIG. 4 shows the maximum and maximum cooling state in the bi-level mode as in FIG.

  According to the second embodiment, the second factor of the maximum cooling performance decrease described in FIG. 11 can be mainly suppressed. That is, in 2nd Embodiment, the partition plate 23 is installed only in the air flow downstream of the heat exchanger 14 for heating, and the downstream space immediately after blowing of the heat exchanger 14 is made into the area | region 24 by the side of the cold air passage 15 Since it divides | segments into the area | region 25 by the side of the anti-cold air channel | path 15, it is prevented that a cold wind flows into the area | region 25 by the side of this anti-cold air channel | path 15. At the same time, the air guide plate 26 guides the cold air from the cold air passage 15 away from the core surface downstream side of the heating heat exchanger 14 toward the foot outlet opening 19.

  Thereby, generation | occurrence | production of the air flow e (refer FIG. 11) which disturbs the core surface downstream of the heat exchanger 14 for heating can be suppressed. Therefore, it is possible to effectively suppress mixing of the dampness d of warm air due to natural convection with the cold air flow j from the cold air passage 15 toward the foot outlet opening 19. That is, the 2nd factor that warm air by natural convection mixes with a cold wind flow and raises foot blowing air temperature can be controlled.

  Further, according to the second embodiment, the partitioning action of the partition plate 23 prevents the cool air from flowing into the region 25 on the anti-cool air passage 15 side, so the region 25 on the anti-cool air passage 15 side (in region A in FIG. 10). Equivalent) is suppressed from increasing.

  For this reason, since the static pressure difference between the region 25 on the anti-cold air passage 15 side and the region 24 on the cold air passage 15 side can be reduced, the partition plate 22 on the upstream side of the air flow of the heating heat exchanger 14 can be eliminated. Ten circulating air flows c can be suppressed.

  Therefore, in 2nd Embodiment, the 1st factor of the largest cooling performance fall based on the circulating airflow c of FIG. 10 resulting from the static pressure difference before and behind the airflow of the heat exchanger 14 for heating can also be suppressed to some extent.

(Third embodiment)
In 1st Embodiment, although the partition plates 22 and 23 are installed in both the air flow upstream and downstream of the heat exchanger 14 for heating, in 3rd Embodiment, as shown in FIG. The partition plate 23 on the downstream side of the air flow of the exchanger 14 is eliminated, and the partition plate 22 is installed only on the upstream side of the air flow of the heat exchanger 14 for heating.

  According to the third embodiment, it is possible to suppress the first factor of the decrease in the maximum cooling performance described with reference to FIG. That is, in the third embodiment, the partition plate 22 is installed on the upstream side of the air flow of the heating heat exchanger 14, and the upstream space portion 16 of the heating heat exchanger 14 is connected to the region 16 a on the cold air passage 15 side and the anti-cooling air. Since it is partitioned into a region 16b on the passage 15 side, a region 16b on the anti-cold air passage 15 side in the upstream space portion 16 and a region 24 on the cold air passage 15 side in the downstream space on the heating heat exchanger 14 Is disconnected.

  For this reason, the static pressure in the region 16b on the anti-cooling air passage 15 side in the upstream space portion 16 approaches the static pressure in the region 25 on the anti-cooling air passage 15 side in the space immediately after the heating heat exchanger 14 is blown out. The static pressure difference between the two regions 16b and 25 is reduced as compared with the air conditioner of FIG.

  Therefore, the flow of air (warm air) from the region 25 due to the static pressure difference to the region 16b side through the core portion 14c of the heating heat exchanger 14 is reduced. The flow of air (warm air) from the region 16 b through the region 16 a and the core portion 14 c of the heating heat exchanger 14 toward the region 24 is also reduced by the partitioning action of the partition plate 22.

  Further, the air guide plate 26 guides the cold air from the cold air passage 15 away from the downstream side of the core surface of the heating heat exchanger 14 toward the foot outlet opening 19.

  As described above, the first factor that the air (warm air) flow resulting from the static pressure difference between the upstream and downstream air flows of the heating heat exchanger 14 is mixed with the cold air flow to increase the foot blowing air temperature can be suppressed. .

(Fourth embodiment)
FIG. 6 shows a fourth embodiment, and a part of the third embodiment is changed. In the fourth embodiment, the film door 21 is not installed in the downstream space immediately after the heating heat exchanger 14 is blown, and one blowout corresponding to the opening range of the opening window portion 21a in the bi-level mode of the film door 21 is provided. An opening 27 is provided.

  A plurality of blowout openings (not shown) corresponding to the blowout openings 19 and 20 are provided on the downstream side of the blowout opening 27, and the blowout modes corresponding to the film door 21 are provided in the blowout openings. It is opened and closed by switching door means (not shown). Specifically, the door means is preferably a slide door such as a film door for downsizing the apparatus.

  The blowout opening 27 is disposed at a position closer to the center in the arrangement direction X of the cold air passage 15 and the heating heat exchanger 14, and fixed walls 28 are provided on both sides of the blowout opening 27, that is, on both sides of the arrangement direction X. 29 are arranged. The fixed walls 28 and 29 are formed integrally with the air conditioning case 11.

  One (vehicle rear side) fixed wall 28 faces the cold air passage 15, and the other (vehicle front side) fixed wall 29 is on the portion of the downstream core surface of the heating heat exchanger 14 on the anti-cool air passage 15 side. opposite. By forming the fixed wall 29, the region 25 on the anti-cool air passage 15 side in the downstream space immediately after the heating heat exchanger 14 is blown becomes a dead end space. Further, the main flow of the cold air flow j from the cold air passage 15 toward the blowout opening 27 flows in a state of being inclined toward the heat exchanger 14 for heating.

  For this reason, also in the air conditioner of the fourth embodiment, at the time of maximum cooling, the warm air from the heating heat exchanger 14 is mixed with the cold air flow j from the cold air passage 15 toward the blowout opening 27 to increase the blown air temperature. However, there is a problem of reducing the maximum cooling performance.

  Therefore, in the fourth embodiment, as in the third embodiment, the partition plate 22 is provided in the upstream space 16 of the heating heat exchanger 14 and the cold air passage 15 in the downstream portion of the heating heat exchanger 14 is provided. An air guide plate 26 is provided in the vicinity of the end on the side to suppress a decrease in the maximum cooling performance.

(Fifth embodiment)
In the first embodiment, two doors of a hot air side air mix door 17 and a cold air side air mix door 18 are used as air mix doors for adjusting the blown air temperature. In the fifth embodiment, FIG. As shown in FIG. 7, a single flat air mix door 30 is used as an air mix door for adjusting the blown air temperature. The air mix door 30 is constituted by a cantilever door having a rotating shaft 30a at the door end.

  Also in the fifth embodiment, by providing the first and second partition plates 22 and 23 and the air guide 26, it is possible to suppress a decrease in the maximum cooling performance in the bi-level mode as in the first embodiment.

(Sixth embodiment)
In the first to fifth embodiments, since the hot water valve is not installed in the hot water passage of the heat exchanger 14 for heating, the hot water (cooling water) of the vehicle engine is heated for heating when the vehicle engine (not shown) is operated. It always circulates in the exchanger 14. Therefore, in 1st-5th embodiment, warm water circulates to the heat exchanger 14 for heating also at the time of maximum cooling.

  On the other hand, 6th Embodiment is related with the air conditioner which installs the warm water valve which interrupts a warm water flow in the warm water channel | path of the heat exchanger 14 for a heating. FIG. 8 shows a sixth embodiment, which is different from the first embodiment in that the hot water valve 31 is installed in the hot water passage of the heating heat exchanger 14 as shown in FIG. 8B. In addition, the air-conditioning unit part 10 of 6th Embodiment is the same structure as the air-conditioning unit part 10 of 1st Embodiment, as shown to Fig.8 (a).

  The hot water valve 31 is installed in the inlet-side hot water passage of the heating heat exchanger 14, and includes a valve mechanism 31a that opens and closes the inlet-side hot water passage, and a valve drive mechanism 31b that drives the valve mechanism 31a. Specifically, the valve drive mechanism 31 b is configured by an electric actuator such as a servo motor, and is controlled by the air conditioning control device 32.

  Both air mix doors 17 and 18 have a common door drive mechanism 33 as shown in FIG. 8B, and this door drive mechanism 33 is connected to the rotary shafts 17a and 18a via a link mechanism or the like to drive the door. The mechanism 33 rotates both the air mix doors 17 and 18 in conjunction with each other. The door drive mechanism 33 is also composed of an electric actuator such as a servo motor.

  The door drive mechanism 33 of both the air mix doors 17 and 18 and the valve drive mechanism 31b of the hot water valve 31 are both controlled by the air conditioning control device 32. Here, the air-conditioning control device 32 is a well-known device using a microcomputer, and calculates the target blowing temperature TAO of the air blown into the vehicle interior, the target opening degree SW of both the air mix doors 17 and 18, and the like of various air-conditioning equipment. Control the operation.

  In the sixth embodiment, when the air mix doors 17 and 18 are rotated to positions other than the maximum cooling position (temperature control region and maximum heating position) by the control output of the air conditioning control device 32, the air conditioning control device 32. The valve mechanism 31a of the hot water valve 31 is maintained in the open state by the control output. Therefore, hot water circulates through the heat exchanger 14 for heating, and the heat exchanger 14 for heating heats the air using the hot water as a heat source.

  On the other hand, when both the air mix doors 17 and 18 are rotated to the maximum cooling position by the control output of the air conditioning control device 32, the valve mechanism 31a of the hot water valve 31 is interlocked with the control output of the air conditioning control device 32. Shifts to a closed state.

  As a result, the hot water flow to the heating heat exchanger 14 is interrupted at the time of maximum cooling, so that the air heating action of the heating heat exchanger 14 is stopped. As a result, it is possible to reliably exhibit the maximum cooling performance by preventing the reheating of the cold air.

  Moreover, even in the temperature control range near the maximum cooling state, it is possible to suppress an excessive increase in the mixing ratio of the hot air to the cold air by the installation of the first and second partition plates 22 and 23, so that the temperature near the maximum cooling state The foot blowing temperature can be smoothly changed in the control region without sudden change (see foot blowing temperature of thick solid line (3) in FIG. 13).

  In addition, although the example which combined the hot water valve 31 with the structure of 1st Embodiment was demonstrated in 6th Embodiment, it is needless to say that the hot water valve 31 may be combined with the structure of 2nd-5th embodiment.

  In the sixth embodiment, the hot water valve 31 is closed during maximum cooling by the control output of the air conditioning control device 32. However, the hot water valve 31 is connected to the air mix doors 17 and 18 via a mechanical interlocking mechanism. Thus, the hot water valve 31 may be closed during maximum cooling.

(Other embodiments)
The present invention is not limited to the above-described embodiments, and various modifications can be made as exemplified below.

  (1) In the above-described embodiment, the rear-seat-side indoor air conditioning unit 10 having the foot outlet opening 19 and the face outlet opening 20 as the outlet opening has been described. However, as the outlet opening, the foot outlet opening and You may apply this invention to the indoor air-conditioning unit part (refer FIG. 9) of the front seat side which has a defroster blowing opening part other than a face blowing opening part.

  (2) In the above-described embodiment, the film door 21 having both ends connected to the take-up shafts 21b and 21c is used as the blowing mode door that opens and closes the plurality of blowing openings 19 and 20. Instead of this, a flexible sliding door described in JP-A-2002-079819 may be used.

  This flexible sliding door transmits a door driving force to a part of a flexible film member and guides and moves the film member by a guide portion provided on the air conditioning case side.

  In addition, as the blowout mode door, a stacked slide door proposed in Japanese Patent Application No. 2004-265325 filed earlier by the present inventor may be used. In this laminated slide door, a plurality of thin plate members are stacked in the direction of the air flow flowing toward the plurality of outlet openings, and the plurality of thin plate members are provided with an air passage opening and the opening. Passage shielding portions are provided on both sides in the door movement direction, and the plurality of blowout openings are opened and closed by movement of the openings and passage shielding portions in the plurality of thin plate members.

  (3) In the above-described embodiment, each of the warm air side air mix door 17, the cool air side air mix door 18, and the single air mix door 30 for controlling the flow of the cool and warm air is configured as a flat door. However, you may comprise an air mix door by the slide door which consists of a film door, a flexible slide door, a laminated slide door etc. similarly to the blowing mode door.

  (4) In the above-described embodiment, one each of the first and second partition plates 22 and 23 is provided. However, a plurality of first and second partition plates 22 and 23 may be provided. According to this, the volume of the partition space becomes smaller, and the effect of suppressing the decrease in the maximum cooling performance can be further improved.

  (5) In the above-described embodiment, the example in which the heating heat exchanger 14 is arranged in the substantially horizontal direction has been described. However, the present invention is similarly applied to the case where the heating heat exchanger 14 is arranged in the substantially vertical direction. Can be implemented.

(A) is sectional drawing of the indoor air-conditioning unit part which shows 1st Embodiment of this invention, and shows the maximum cooling state of bilevel mode. (B) is a front view of the heat exchanger for heating of a 1st embodiment. It is sectional drawing which shows the maximum cooling state of the face mode of 1st Embodiment. It is sectional drawing which shows the maximum heating state of the foot mode of 1st Embodiment. It is sectional drawing of the indoor air-conditioning unit part which shows 2nd Embodiment. It is sectional drawing of the indoor air-conditioning unit part which shows 3rd Embodiment. It is sectional drawing of the indoor air-conditioning unit part which shows 4th Embodiment. It is a schematic sectional drawing of the indoor air-conditioning unit part which shows 5th Embodiment. (A) is sectional drawing of the indoor air-conditioning unit part which shows 6th Embodiment of this invention, and shows the maximum cooling state of bilevel mode. (B) is a front view of the heat exchanger for heating of a 6th embodiment. It is sectional drawing which shows the conventional indoor air-conditioning unit part. It is sectional drawing explaining the 1st factor of the largest cooling performance fall in this inventor's prototype. It is sectional drawing explaining the 2nd factor of the maximum cooling performance fall in this inventor's prototype. It is a schematic sectional drawing explaining the cold wind flow form at the time of bilevel mode in a prototype of this inventor. It is a control characteristic figure of the blowing temperature at the time of bilevel mode.

Explanation of symbols

13 ... Heat exchanger for cooling, 14 ... Heat exchanger for heating, 15 ... Cool air passage,
16 ... Air flow upstream space part, 17, 18, 30 ... Air mix door (temperature adjusting means), 19 ... Foot blowout opening part, 21 ... Film door (door means), 21a ... Opening window part,
21d ... Film part (wall part), 22, 23 ... Partition plate, 16a, 16b, 24, 25 ... area.

Claims (13)

An air conditioning case (11) that constitutes an air passage through which air flows toward the passenger compartment;
A cooling heat exchanger (13) disposed in the air conditioning case (11) for cooling air;
A heating heat exchanger (14) that is disposed in the air conditioning case (11) at a downstream portion of the cooling heat exchanger (13) and heats the air;
A cold air passage (15) formed in parallel with the heating heat exchanger (14) in the air conditioning case (11) and through which the cold air after passing through the cooling heat exchanger (13) flows;
Temperature adjusting means (17, 18, 30) that adjusts the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) to adjust the temperature in the passenger compartment. And
In the vehicle air conditioner in which the high-temperature heat source fluid is circulated to the heating heat exchanger (14) even when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position.
An opening (19) that directly faces the heating heat exchanger (14) is disposed in the air flow downstream side space of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19),
Door means (21) for opening and closing the opening (19);
A wall portion (21d) that directly faces the heating heat exchanger (14) is disposed in a portion of the opening portion (19) that is opposite to the cold air passage (15),
The wall (21d) is constituted by the door means (21);
Furthermore, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow downstream space of the heating heat exchanger (14), the heating heat exchanger (14) A partition plate (23) is arranged along the hot air blowing direction from
The partition plate (23) partitions the air flow downstream space into a region (24) on the cold air passage (15) side and a region (25) on the opposite side of the cold air passage (15). Vehicle air conditioner. An air conditioning case (11) that constitutes an air passage through which air flows toward the passenger compartment;
A cooling heat exchanger (13) disposed in the air conditioning case (11) for cooling air;
A heating heat exchanger (14) that is disposed in the air conditioning case (11) at a downstream portion of the cooling heat exchanger (13) and heats the air;
A cold air passage (15) formed in parallel with the heating heat exchanger (14) in the air conditioning case (11) and through which the cold air after passing through the cooling heat exchanger (13) flows;
Temperature adjusting means (17, 18, 30) that adjusts the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) to adjust the temperature in the passenger compartment. And
In the vehicle air conditioner in which the high-temperature heat source fluid is circulated to the heating heat exchanger (14) even when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position.
Openings (19, 27) that directly face the heating heat exchanger (14) are disposed in the air flow downstream space of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19, 27),
Wall portions (21d, 29) directly facing the heat exchanger for heating (14) are arranged in a portion of the openings (19, 27) opposite to the cold air passage (15),
Further, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger The partition plate (22) is arranged along the flow direction of the air flowing into (14),
The partition plate (22) partitions the air flow upstream space (16) into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side of the cold air passage (15). A vehicle air conditioner. An air conditioning case (11) that constitutes an air passage through which air flows toward the passenger compartment;
A cooling heat exchanger (13) disposed in the air conditioning case (11) for cooling air;
A heating heat exchanger (14) that is disposed in the air conditioning case (11) at a downstream portion of the cooling heat exchanger (13) and heats the air;
A cold air passage (15) formed in parallel with the heating heat exchanger (14) in the air conditioning case (11) and through which the cold air after passing through the cooling heat exchanger (13) flows;
Temperature adjusting means (17, 18, 30) that adjusts the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) to adjust the temperature in the passenger compartment. When,
A valve means (31) provided in a passage of the high-temperature heat source fluid circulating to the heating heat exchanger (14), and interrupting the flow of the high-temperature heat source fluid;
When the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position, the valve means (31) cuts off the circulation of the high-temperature heat source fluid to the heating heat exchanger (14). Air conditioner for
An opening (19) that directly faces the heating heat exchanger (14) is disposed in the air flow downstream side space of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19),
Door means (21) for opening and closing the opening (19);
A wall portion (21d) that directly faces the heating heat exchanger (14) is disposed in a portion of the opening portion (19) that is opposite to the cold air passage (15),
The wall (21d) is constituted by the door means (21);
Furthermore, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow downstream space of the heating heat exchanger (14), the heating heat exchanger (14) A partition plate (23) is arranged along the hot air blowing direction from
The partition plate (23) partitions the air flow downstream space into a region (24) on the cold air passage (15) side and a region (25) on the opposite side of the cold air passage (15). Vehicle air conditioner. An air conditioning case (11) that constitutes an air passage through which air flows toward the passenger compartment;
A cooling heat exchanger (13) disposed in the air conditioning case (11) for cooling air;
A heating heat exchanger (14) that is disposed in the air conditioning case (11) at a downstream portion of the cooling heat exchanger (13) and heats the air;
A cold air passage (15) formed in parallel with the heating heat exchanger (14) in the air conditioning case (11) and through which the cold air after passing through the cooling heat exchanger (13) flows;
Temperature adjusting means (17, 18, 30) that adjusts the air volume ratio between the hot air passing through the heat exchanger for heating (14) and the cold air passing through the cold air passage (15) to adjust the temperature in the passenger compartment. When,
A valve means (31) provided in a passage of the high-temperature heat source fluid circulating to the heating heat exchanger (14), and interrupting the flow of the high-temperature heat source fluid;
When the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position, the valve means (31) cuts off the circulation of the high-temperature heat source fluid to the heating heat exchanger (14). Air conditioner for
In the vehicle air conditioner in which the high-temperature heat source fluid is circulated to the heating heat exchanger (14) even when the temperature adjusting means (17, 18, 30) is operated to the maximum cooling position.
Openings (19, 27) that directly face the heating heat exchanger (14) are disposed in the air flow downstream space of the heating heat exchanger (14),
The main flow of the cold air flow from the cold air passage (15) is inclined toward the heating heat exchanger (14) toward the opening (19, 27),
Wall portions (21d, 29) directly facing the heat exchanger for heating (14) are arranged in a portion of the openings (19, 27) opposite to the cold air passage (15),
Further, when the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger The partition plate (22) is arranged along the flow direction of the air flowing into (14),
The partition plate (22) partitions the air flow upstream space (16) into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side of the cold air passage (15). A vehicle air conditioner. By combining the partition plate (23) on the downstream side of the air flow and the wall portion (21d), the region (25) opposite to the cold air passage (15) is blocked from the cold air flow from the cold air passage (15). The vehicle air conditioner according to claim 1 or 3, wherein When the temperature adjusting means (17, 18, 30) is operated to the maximum heating position in the air flow upstream space (16) of the heating heat exchanger (14), the heating heat exchanger (14 The partition plate (22) on the upstream side of the air flow is arranged along the flow direction of the air flowing into the
By the partition plate (22) on the upstream side of the air flow, the space portion (16) on the upstream side of the air flow is divided into a region (16a) on the cold air passage (15) side and a region (16b) on the opposite side to the cold air passage (15). The vehicle air conditioner according to claim 1, wherein the vehicle air conditioner is divided into two parts. The partition plate (22) on the upstream side of the air flow and the partition plate (23) on the downstream side of the air flow are disposed to be inclined with respect to the heating heat exchanger (14),
The partition plate (22) on the upstream side of the air flow and the partition plate (23) on the downstream side of the air flow include the plurality of regions (16a, 16b, 24, 25) across the heating heat exchanger (14). The vehicle air conditioner according to claim 6, wherein the vehicle air conditioner is partially wrapped in the arrangement direction. The air flow upstream space (16) is between the air flow upstream core surface of the heating heat exchanger (14) and the temperature adjusting means (17, 18, 30) at the maximum cooling position. A space to be formed,
The partition plate (22) on the upstream side of the air flow is between the air flow upstream side core surface of the heating heat exchanger (14) and the temperature adjusting means (17, 18, 30) at the maximum cooling position. The vehicle air conditioner according to any one of claims 2, 4, 6, and 7, wherein the vehicle air conditioner is disposed so as to be sandwiched between the two. A hot air side air mix door (17) composed of a rotatable plate door as the temperature adjusting means;
The partition plate (22) on the upstream side of the air flow is disposed along a back surface of the hot air side air mix door (17) at the maximum heating position. The vehicle air conditioner according to any one of 8 and 8. The heating heat exchanger (14) has a plurality of tubes (14a) through which the high-temperature heat source fluid flows,
The vehicle air conditioner according to any one of claims 1 to 9, wherein a longitudinal direction of the tube (14a) and a plate surface direction of the partition plate (22, 23) are the same direction. . The cool air flow from the cold air passage (15) is directed toward the opening (19) near the end on the cold air passage (15) side in the downstream portion of the air flow of the heat exchanger for heating (14). The air conditioner for vehicles according to any one of claims 1 to 10, wherein an air guide plate (26) for guiding is arranged. The vehicle air conditioner according to claim 2 or 4, further comprising door means (21) for opening and closing the opening (19). The door means is a sliding door (21) that moves in a direction orthogonal to the air flow toward the opening (19),
The said wall part (21d) is comprised by the said slide door (21), The vehicle air conditioner as described in any one of Claim 1, 3, 5, 6, 7, 12 characterized by the above-mentioned.

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