JP5609635B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner including a heating heat exchanger that heats air blown into a passenger compartment.

  There exists a thing of patent documents 1, 2 as such a vehicle air conditioner.

  In the thing of patent document 1, there exist a cylinder head side flow path which cools a cylinder head as a cooling water flow path inside an engine, and a cylinder block side flow path which cools a cylinder block, and it passed the cylinder head side flow path. The cooling water is configured to flow into one heating heat exchanger.

  Moreover, in the thing of patent document 2, two heat exchangers for heating for heating air are provided, the cooling water flowing out from one cooling water outlet provided in the engine is divided, and each heating is performed. Is flowing into the heat exchanger.

US Pat. No. 5,337,704 European Patent Application No. 1008471

  By the way, in recent years, there is a demand for an engine mounted on a vehicle to ensure a required output and to make it smaller than before. In order to realize this, knocking may occur when the compression ratio is increased or when the supercharging pressure is increased in an engine with a supercharger. Therefore, it is necessary to improve anti-knocking performance. Therefore, it is conceivable to positively cool the cylinder head in order to improve the knocking resistance.

  However, the cylinder block needs to be maintained at a predetermined temperature or higher in order to suppress an increase in friction inside the engine. Therefore, a cylinder head side flow path and a cylinder block side flow path are provided as cooling water flow paths inside the engine, and the cooling water flow rate of the cylinder head side flow path is made larger than the cooling water flow rate of the cylinder block side flow path. It is possible.

  However, in this case, the cooling water temperature after cooling the cylinder head becomes lower than the minimum temperature required for heating, and as in the technique described in Patent Document 1, only the cooling water that has cooled the cylinder head is used as a heat source. When the air blown into the room is heated, there arises a problem that the air temperature cannot be raised sufficiently. Incidentally, conventionally, the cooling water temperature after cooling the cylinder head is about 80 to 90 ° C., which exceeds the minimum temperature required for heating, and thus such a problem does not occur.

  Therefore, as a heat exchanger for heating, the first heat exchange unit that exchanges heat between the cooling water that has cooled the cylinder head and the blown air, and the blown air that is heated by the cooling water that has cooled the cylinder block and the first heat exchange unit And a second heat exchanging part that exchanges heat with each other.

  According to this, in the first heat exchanging unit, the cooling air that has cooled the cylinder block is used as a heat source, and the blown air is heated, and then in the second heat exchanging unit, the cylinder that is hotter than the cooling water after cooling the cylinder head Since the blown air heated by the first heat exchange unit is further heated using the cooling water after block cooling as a heat source, the air temperature after passing through the heating heat exchanger can be sufficiently increased.

  However, in this case, since the cooling water flow rate in the cylinder block side flow path is smaller than the cooling water flow rate in the cylinder head side flow path, the cooling water flowing into the second heat exchange unit is cooled into the first heat exchange unit. The flow rate is smaller than that of water.

  For this reason, when the cooling water flows from one side of the second heat exchange unit to the other side inside the second heat exchange unit, the cooling water temperature on one side is high and the cooling water temperature on the other side is low. A temperature distribution in which the one side is high and the other side is low occurs in the conditioned air after passing through the second heat exchange unit. As a result, a temperature distribution is generated in which the one side is high and the other side is low in the conditioned air after passing through the heat exchanger for heating. Incidentally, if the flow rate of the cooling water flowing into the second heat exchange unit is large, the difference between the cooling water temperature on one side and the cooling water temperature on the other side is small, so the conditioned air after passing through the second heat exchange unit The temperature distribution that occurs is small.

  In view of the above, an object of the present invention is to provide a vehicle air conditioner that can effectively use a temperature distribution in which one side is high and the other side is low in the conditioned air after passing through the heat exchanger for heating.

In order to achieve the above object, in the invention described in claim 1,
An air-conditioning case (51) that forms an air flow path for the blast air toward the passenger compartment;
A heating heat exchanger (2) for heating the blown air using the first liquid and the second liquid having a higher temperature and a lower flow rate than the first liquid as a heat source, and being housed in the air conditioning case (51),
The heating heat exchanger (2) includes a first heat exchange section (10) for exchanging heat between the first liquid and the blown air, and a blown air heated by the second liquid and the first heat exchange section (10). the a second heat exchange unit for heat exchange and (20),
The second heat exchange section (20) has a second liquid flowing inside the second heat exchange section (20) from one side which is the second liquid flow upstream side of the second heat exchange section (20) to the other side which is the second liquid flow downstream side. And
The wind speed distribution of the blown air passing through the heating heat exchanger (2) is a wind speed distribution in which the wind speed on the other side is high and the wind speed on one side is low, and one side of the heat exchanger (2) for heating The blown air after passing through the region is blown out from the foot outlet, and the blown air after passing through the region on the other side of the heating heat exchanger (2) is blown out from the outlet other than the foot outlet. It is characterized by that.

  In the present invention, since the second liquid having a small flow rate flows from one side of the second heat exchange unit to the other side in the second heat exchange unit, the second heat exchange unit has passed through the region on one side. The temperature of the blown air is high and the temperature of the blown air after passing through the other region is low.

  And according to this invention, the blowing air after passing the area | region of one side is blown out from the foot blower outlet which requires high blowing air temperature, and the blowing air with the low temperature after passing the area | region of the other side is blown out high Since it blows off from air outlets other than the foot air outlet which does not require air temperature, the temperature distribution which arises in the conditioned air after passing the heat exchanger for heating can be used effectively.

  Furthermore, in the present invention, a configuration is adopted in which the blown air passing through one side of the heat exchanger for heating has a lower wind speed than the blown air passing through the other side.

  Here, generally, the lower the wind speed of the blown air passing through the heat exchange unit, the higher the temperature efficiency in the heat exchange unit, so the temperature of the blown air that passed through the heat exchange unit (exit air temperature) is higher. Become.

  For this reason, according to this invention, compared with the case where the wind speed of the ventilation air which is passing through the heat exchanger for heating is uniform, the temperature of the ventilation air after passing the area | region of one side of the heat exchanger for heating Can be raised, the temperature of the air blown from the foot outlet can be raised, and the warmth of the passenger's feet can be improved. Further, according to the present invention, it is possible to increase the temperature of air blown from the foot outlet without increasing the amount of heat input to the heating.

  As a configuration in which the wind speed distribution of the blown air passing through the heat exchanger for heating in the invention according to claim 1 is a wind speed distribution in which the wind speed on the other side is high and the wind speed on the one side is low, The inventions described in claims 2 to 5 can be adopted.

  In the second aspect of the present invention, the air conditioning case (51) is an air flow path for the blown air flowing into one area of the heat exchanger (2) for heating, and has a flow path cross-sectional area that expands in the middle. An increasing air flow path (52) is formed.

  In the invention according to claim 3, the air conditioning case (51) is narrowed in the middle as the air flow path of the blast air flowing into the other side of the heating heat exchanger (2), and the flow path cross-sectional area is reduced. It is characterized in that a decreasing air flow path (53) is formed.

  In the invention according to claim 4, the heat transfer fins (14, 24) have a small fin pitch (fp1) in one region of the heat exchanger (2) for heating, and fins in the other region. The pitch (fp2) is increased.

  According to this, since the fins exist in a sparse state in the region on the other side of the heat exchanger for heating, the ventilation resistance is small, and in the region on one side of the heat exchanger for heating, the fins are in a dense state. Because it exists, ventilation resistance is high. Therefore, according to the present invention, the wind speed distribution of the blown air passing through the heating heat exchanger can be set to a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side.

  In the invention according to claim 5, the air conditioning case (51) includes an air flow path on the downstream side of the air flow of the heat exchanger (2) for heating, and an air flow path (56) on one side positioned on one side. A downstream partition wall (58) for partitioning with the other air flow channel (57) located on the other side is provided, and an obstruction member (72) that obstructs the air flow in the one air flow channel (56). ) Is provided.

  According to this, since the obstruction member becomes ventilation resistance, the wind speed of the blown air passing through the region on one side of the heat exchanger for heating becomes low. Therefore, according to the present invention, the wind speed distribution of the blown air passing through the heating heat exchanger can be set to a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side.

  Moreover, in invention of Claim 6, in the invention of Claims 1-5, when a blower outlet mode is the bilevel mode which blows off an air-conditioning wind from both a foot blower outlet and a face blower outlet, a foot blower outlet The other air outlet is a face air outlet.

  According to this, in the bi-level mode, since the difference between the air temperature from the foot outlet and the air temperature from the face outlet is large, passenger comfort is improved.

  Moreover, in invention of Claim 7, in the invention of Claims 1-6, as for the 2nd heat exchange part (20), the inlet side tank part (22) is located in the lower side, and the outlet side tank part (23) is held in the air conditioning case (51) so as to be positioned on the upper side, and the liquid inlet (20a) of the inlet side tank part (22) is in the vehicle left-right direction of the inlet side tank part (22). It is arranged on the driver's seat side.

  Here, the second liquid flowing into the second heat exchange unit has a smaller flow rate than the first liquid flowing into the first heat exchange unit. In this case, when the flow rate of the second liquid is lower than that of the first liquid, if the inlet side tank unit is positioned on the lower side, most of the second liquid that has flowed into the inlet side tank unit is not connected to the liquid inlet. It will flow.

  Therefore, according to the present invention, since the liquid inlet is arranged on the driver's seat side of the inlet side tank section, the temperature of the air on the driver's seat side, which is frequently boarded, is increased from the temperature of the air on the passenger's seat side. be able to.

  Moreover, in invention of Claim 8, in the invention of Claims 1-7, it is passing the heat exchanger (2) for a heating at the time of the maximum heating by which an air mix door is made into the position which closes a bypass air passage. The air velocity distribution of the blast air is characterized in that the wind velocity distribution on the other side is high and the wind velocity distribution on the one side is low. Thus, it is preferable that such a wind speed distribution is formed at the time of the maximum heating which requires a high blowing air temperature.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a schematic block diagram of the vehicle air conditioner in 1st Embodiment. It is a side view of the heat exchanger for a heating in FIG. 1 of the state hold | maintained at the air-conditioning case. It is a front view of the heat exchanger for heating in FIG. It is a figure which shows distribution of the exit air temperature of the heat exchanger for heating in 1st Embodiment. It is a figure which shows distribution of the exit air temperature of the heat exchanger for a heating in the comparative example 1. It is a figure which shows the temperature distribution of the inlet air and cooling water in the 2nd heater core of 1st Embodiment. It is a figure which shows the temperature distribution of the inlet air and cooling water in the 2nd heater core of the comparative example 2. It is a side view of the heat exchanger for a heating of the state hold | maintained at the air-conditioning case in 2nd Embodiment. It is a side view of the heat exchanger for a heating of the state hold | maintained at the air-conditioning case in 3rd Embodiment. It is a front view of the heat exchanger for heating in 4th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other are given the same reference numerals in the drawings in order to simplify the description.

(First embodiment)
FIG. 1 shows a schematic configuration of a vehicle air conditioner in the present embodiment. The vehicle air conditioner of the present embodiment is mounted on a hybrid vehicle that obtains driving force for vehicle travel from an engine (internal combustion engine) and a travel electric motor.

  The vehicle air conditioner 1 according to the present embodiment includes a heating heat exchanger 2 that heats the air blown into the vehicle interior by exchanging heat between the cooling water of the engine 30 and the air blown into the vehicle interior. . The cooling water is water or water containing additive components.

  The heat exchanger 2 for heating has the 1st heater core 10 and the 2nd heater core 20, and both are integrated. The 1st heater core 10 and the 2nd heater core 20 are equivalent to the 1st heat exchange part and the 2nd heat exchange part of the heat exchanger for heating in the present invention, respectively.

  Cooling water that has cooled the cylinder head 31 of the engine 30 flows into the first heater core 10, and cooling water that has cooled the cylinder block 32 of the engine 30 flows into the second heater core 20. The first heater core 10 is located on the upstream side of the air flow, and the second heater core 20 is located on the downstream side of the air flow.

  Here, in the engine 30, the cylinder block 32 is a block body that constitutes a cylinder bore (columnar hole) in which a piston reciprocates. The cylinder head 31 is a block body that closes the top dead center side opening of the cylinder bore and constitutes a combustion chamber.

  A first cooling water inlet 31 a and a first cooling water outlet 31 b as a first outlet portion are provided on the cylinder head 31 side of the engine 30, and cooling water for cooling the cylinder head 31 flows inside the cylinder head 31. A cooling water passage on the cylinder head side is formed. The cooling water flowing in from the first cooling water inlet 31a flows through the cylinder head 31 and then flows out from the first cooling water outlet 31b.

  Similarly, a second cooling water inlet 32 a and a second cooling water outlet 32 b as a second outlet are provided on the cylinder block 32 side of the engine 30, and cooling for cooling the cylinder block 32 is provided inside the cylinder block 32. A cooling water passage on the cylinder block side through which water flows is formed. The cooling water flowing in from the second cooling water inlet 32a flows through the cylinder block 32 and then flows out from the second cooling water outlet 32b. Thus, in this embodiment, the cooling water which cooled the cylinder block 32 flows out from the 2nd cooling water exit 32b, without joining the cooling water which cooled the cylinder head 31. FIG.

  As described above, the engine 30 of the present embodiment has two cooling systems, and the cooling water flow rate of the cooling water passage on the cylinder head side is set to the cooling water passage on the cylinder block side during the steady operation of the engine 30. More than the water flow rate, the cylinder head 31 is more actively cooled than the cylinder block 32. This is because the cylinder head 31 is kept at a low temperature to improve the anti-knocking performance, and the cylinder block 32 is kept at a high temperature, thereby suppressing the decrease in the viscosity of the engine oil and increasing the friction inside the engine. It is for suppressing.

  In the heat exchanger 2 for heating, the cooling water inlet 10a of the first heater core 10 is connected to a first cooling water outlet 31b on the cylinder head 31 side of the engine 30 via a pipe, and the first cooling water outlet The cooling water flowing out from 31 b flows into the first heater core 10. On the other hand, the cooling water inlet 20a of the second heater core 20 is connected to a second cooling water outlet 32b on the cylinder block 32 side of the engine 30 via a pipe, and the cooling water flowing out from the second cooling water outlet 32b It flows into the second heater core 20.

  Therefore, in this embodiment, low temperature and large flow rate cooling water flows into the first heater core 10, and high temperature and small flow rate cooling water flows into the second heater core 20. Specifically, the temperature and flow rate of the cooling water flowing into the first heater core 10 are in the range of 30 to 60 ° C. and 5 to 15 L / min, and the temperature and flow rate of the cooling water flowing into the second heater core 20 are It is the range of 40-90 degreeC and 0.2-2 L / min.

  As will be described later, each of the first heater core 10 and the second heater core 20 has an independent heat exchange core portion. Therefore, the cooling water flowing into the first heater core 10 exchanges heat with air at the heat exchange core portion of the first heater core 10 without being mixed with the cooling water flowing into the second heater core 20. Similarly, the cooling water flowing into the second heater core 20 exchanges heat with air at the heat exchange core portion of the second heater core 20 without being mixed with the cooling water flowing into the first heater core 10. And the cooling water which passed each heat exchange core part flows out from the common cooling water exit 2b provided in the heat exchanger 2 for heating, after joining.

  The cooling water flowing out from the cooling water outlet 2b of the heat exchanger 2 for heating branches at the branching portion 41 and flows into the first cooling water inlet 31a and the second cooling water outlet 32a of the engine 30, respectively.

  Further, as shown in FIG. 1, the water pump 42 is disposed in the middle of the cooling water flow path between the cooling water outlet 2 b of the heating heat exchanger 2 and the branch portion 41. The water pump 42 is an adjusting unit that forms a cooling water flow and adjusts the cooling water flow rate. The water pump 42 is an electric pump, and controls the coolant flow rate by controlling the rotation speed by a control device (not shown).

  The engine 30 communicates with a radiator (not shown), and the cooling water flowing out from the cylinder head 31 radiates heat with the radiator, and the cooling water after heat radiation can flow into the cylinder head 32 and the cooling water flowing out from the cylinder block 32. Radiates heat with the radiator, and the cooling water after heat radiation can flow into the cylinder block 32.

  Next, the heat exchanger 2 for heating and the air conditioning case 51 that houses the heat exchanger 2 will be described in detail. FIG. 2 shows a side view of the heating heat exchanger 2 held in the air conditioning case 51, and FIG. 3 shows a front view of the heating heat exchanger 2.

  The heat exchanger 2 for heating is accommodated in an air conditioning case 51 that forms an air flow path of the blown air together with a blower (not shown) that forms blown air toward the vehicle interior. Specifically, as shown in FIG. 2, the heat exchanger 2 for heating is in a state where the air inflow / outflow surface is parallel to the vertical direction, and the second heater core 20 is downstream of the first heater core 10 in the air flow direction. It is hold | maintained at the air-conditioning case 51 so that it may be located in.

  As shown in FIGS. 2 and 3, the first and second heater cores 10 and 20 are each composed of a plurality of laminated flat tubes 11 and 21 and one end in the longitudinal direction of the plurality of tubes 11 and 21. The inlet side tank portions 12 and 22 that are on the cooling water inlet side, and the outlet side tank portions 13 and 23 that are on the other end side in the longitudinal direction of the plurality of tubes 11 and 21 and that are on the cooling water outlet side. And.

  The inlet side tank portions 12 and 22 of the first and second heater cores 10 and 20 are configured by dividing the inside of one inlet side tank 61 into two by a partition wall 62, and each of them has a cooling water inlet 10a. , 20a are provided. The cooling water inlets 10a and 20a are both arranged on the driver's seat side, which is one end side in the vehicle left-right direction (left-right direction in FIG. 3) of the inlet-side tank portions 12 and 22.

  The outlet side tank portions 13 and 23 of the first and second heater cores 10 and 20 are shared by a single outlet side tank 63. The outlet side tank 63 is provided with one cooling water outlet 2b. For this reason, the cooling water that has flowed into the first heater core 10 and the cooling water that has flowed into the second heater core 20 merge inside the outlet-side tank 63, and the merged cooling water flows out from one cooling water outlet 2b. . The cooling water outlet 2b is disposed on one end side in the vehicle left-right direction, which is the same as the cooling water inlets 10a and 20a.

  As described above, in this embodiment, the outlet side tank portions of the first and second heater cores 10 and 20 are made common and the cooling water outlet 2b of the heating heat exchanger 2 is made one. You may provide an exit side tank part and a cooling water exit in each of the 2nd heater cores 10 and 20. FIG. However, this embodiment is preferable from the viewpoint of reducing the number of pipes connected between the heat exchanger 2 for heating and the engine 30 or reducing the number of water pumps described later.

  The inlet side tank portions 12 and 22 of the first and second heater cores 10 and 20 are located on the lower side, and the outlet side tank portions 13 and 23 of the first and second heater cores 10 and 20 are located on the upper side. ing. For this reason, in both the first heater core 10 and the second heater core 20, the cooling water flows from the bottom to the top.

  In both the first and second heater cores 10 and 20, the plurality of tubes 11 and 21 extend in the up-down direction, which is one direction, and are arranged in a line in the vehicle left-right direction, which is a direction perpendicular to the one direction. Are stacked. The inlet side tank parts 12 and 22 and the outlet side tank parts 13 and 23 are elongated in the stacking direction of the tubes 11 and 21. Therefore, the vehicle left-right direction corresponds to the stacking direction of the tubes 11, 21 and the longitudinal direction of the inlet-side tank portions 12, 22.

  Further, as shown in FIG. 3, the first and second heater cores 10, 20 include corrugated heat transfer fins 14, 24 joined to the outer surfaces of the tubes 11, 21. In the first and second heater cores 10 and 20, the first and second heat exchange core portions 15 of the all-pass type, that is, the unidirectional flow type, are formed by the laminated structures of the tubes 11 and 21 and the heat transfer fins 14 and 24, respectively. , 25 are configured.

  As shown in FIG. 3, the first heater core 10 and the second heater core 20 have the same size in the horizontal and vertical directions when viewed in the air flow direction. Thereby, all of the air after passing through the first heater core 10 passes through the second heater core 20.

  Further, as shown in FIG. 2, the first heater core 10 and the second heater core 20 have different thicknesses in the air flow direction. Specifically, when the widths of the tubes 11 and 21 and the heat transfer fins 14 and 24 in the air flow direction are compared, the first heater core 10 is longer than the second heater core 20. For this reason, the heat exchange area between the air and the cooling water is larger in the first heater core 10 than in the second heater core 20.

  Further, the flow passage cross-sectional area of the tube 11 of the first heater core 10 is larger than the flow passage cross-sectional area of the tube 21 of the second heater core 20, and the flowing water resistance in the first heater core 10 is in the second heater core 20. It is lower than the running water resistance. For this reason, the flow rate of the cooling water flowing through the first heater core 10 is larger than that of the second heater core 20.

  In the air conditioning case 51, as shown in FIG. 2, the air flow path is arranged on the upstream side of the air flow of the heat exchanger 2 for heating and the lower air flow on the air flow path of the heat exchanger 2 for heating. An upstream partition wall 54 and a plate-like door 55 are provided to partition the passage 52 and the upper air flow path 53.

  The door 55 is a passage width changing means that is located between the upstream partition wall 54 and the heating heat exchanger 2 and changes the passage width of the lower air passage 52 and the upper air passage 53. is there. Specifically, the door 55 widens the lower air flow path 52 in the middle and narrows the upper air flow path 53 in the middle, the lower air flow path 52, and the upper air flow path. The position of each flow path 53 is switched to a position where the air flow direction is constant.

  When the position of the door 55 is a position where the lower air flow path 52 is expanded in the middle and the upper air flow path 53 is narrowed in the middle, the lower air flow path 52 immediately before the heat exchanger 2 for heating is located. The flow passage cross-sectional area A11 is larger than the flow passage cross-sectional area A10 on the upstream side of the door 55, and the flow passage cross-sectional area A21 of the upper air flow passage 53 just before the heating heat exchanger 2 is the door 55. It becomes smaller than the channel cross-sectional area A20 on the upstream side.

  For this reason, when the air flow rate Q1 of the lower air flow path 52 is the same as the air flow rate Q2 of the upper air flow path 53 and the air volumes are the same at V0, the wind speed is V0 in the lower air flow path 52. Decreases from V1 to V1, and the wind speed increases from V0 to V2 in the upper air flow path 53. As a result, the wind speed distribution of the blown air passing through the heat exchanger 2 for heating becomes a wind speed distribution with a high wind speed on the upper side and a low wind speed on the lower side.

  Even if the air flow rate Q1 of the lower air flow path 52 is different from the air flow rate Q2 of the upper air flow path 53, the air in the lower air flow path 52 and the upper air flow path 53 is different. The relationship between the flow rates Q1 and Q2 and the air flow path cross-sectional areas A21 and A22 immediately before the heating heat exchanger 2 may be Q1 / A11 <Q2 / A21. Thereby, the wind speed distribution of the blown air passing through the heat exchanger 2 for heating becomes a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side.

  A downstream partition wall 58 that partitions the air flow path into a lower air flow path 56 and an upper air flow path 57 is provided on the downstream side of the air flow of the heating heat exchanger 2. The lower air flow path 56 is connected to a foot (FOOT) outlet, and blown air that has passed through the lower region of the heat exchanger 2 for heating flows therethrough. The upper air flow path 57 is connected to the defroster (DEF) outlet and the face (FACE) outlet, so that the blown air that has passed through the upper region of the heat exchanger 2 for heating flows.

  Although not shown in the air conditioning case 51, a bypass air passage through which the blast air bypasses the heat exchanger 2 for heating and the blast air from the bypass air passage and the air flow downstream of the heat exchanger 2 for heating An air mix door for adjusting the mixing ratio with the blown air from the upper air flow path 57 is provided.

  Next, the operation of the vehicle air conditioner 1 of the present embodiment will be described.

  A control device (not shown) of the vehicle air conditioner 1 controls the blower so as to obtain an air flow amount corresponding to the target blown air temperature TAO during heating, and controls the air mix door so as to be in a desired position. The target blown air temperature TAO is calculated according to the air conditioning heat load determined by the set temperature and the environmental conditions, and is the target temperature of the air blown out from the outlet to the vehicle interior.

  Thereby, in the 1st heater core 10, blowing air is heated by heat exchange with the cooling water after cylinder head 31 cooling. The cooling water after cooling the cylinder head 31 actively cools the cylinder head 31, and thus is cooler than the minimum temperature required for heating, but has a larger flow rate than the cooling water after cooling the cylinder block 32. It has a lot of heat. Therefore, in the present embodiment, in order to extract as much heat as possible of the cooling water after cooling the cylinder head 31, as compared with the second heater core 20, the cooling water flow rate inside the first heater core 10 is increased, and the air and the cooling water. The heat exchange area is increased. For this reason, in the 1st heater core 10, much calorie | heat amount can be supplied to ventilation air from the cooling water of the large flow volume after the cylinder head 31 cooling. As a result, the temperature of the air after passing through the first heater core 10 is close to the cooling water temperature before flowing into the first heater core 10 (the inlet water temperature of the first heater core).

  And in the 2nd heater core 20, the ventilation air after the 1st heater core 10 passage is heated by heat exchange with the cooling water after cylinder block 32 cooling. Since the cooling water after cooling the cylinder block 32 is hotter than the cooling water after cooling the cylinder head 31, the temperature of the blown air after passing through the second heater core 20 is higher than the blown air after passing through the first heater core 10. Can be raised.

  By the way, unlike this embodiment, if the air is heated using only the cooling water that has cooled the cylinder head 31 as the heat source, as in the technique described in Patent Document 1, the air temperature cannot be sufficiently increased, and the heating is not performed. Not satisfied. Further, when the cooling water after cooling the cylinder head 31 that has flowed out of the engine and the cooling water after cooling the cylinder block 32 are all mixed, the temperature of the cooling water after mixing becomes lower than the minimum temperature required for heating. For this reason, since the energy transfer efficiency from cooling water to air becomes low, even if the air is heated using the mixed cooling water as a heat source, the air temperature cannot be sufficiently increased and heating is not established.

  In contrast, in the present embodiment, the engine 30 is provided with the first cooling water outlet 31b and the second cooling water outlet 32b, and the low-temperature side cooling water after cooling the cylinder head 31 is caused to flow out from the first cooling water outlet 31b. The high-temperature side cooling water after cooling the cylinder block 32 is allowed to flow out from the second cooling water outlet 32b. Then, the low temperature side cooling water flowing out from the first cooling water outlet 31b is caused to flow into the first heater core 10 without mixing both cooling waters, and the high temperature side cooling water flowing out from the second cooling water outlet 32b is supplied to the second cooling water. It flows into the heater core 20.

  Thus, in this embodiment, since the 2nd heater core 20 heats the blowing air to the vehicle interior by using the high temperature side cooling water flowing out from the second cooling water outlet 32b as a heat source, the first cooling water outlet 31b Compared with the case where only the cooling water on the low temperature side of the outflow is used as the heat source, or the case where the mixed water obtained by mixing the low temperature side cooling water and the high temperature side cooling water is used as the heat source, the air temperature after being heated by the second heater core 20 Can be high.

  Further, in the present embodiment, the first heater core 10 heats the blown air using the low-temperature side cooling water as the heat source, and then heats the heated air using the second heater core 20 as the high-temperature side cooling water as the heat source. The amount of heat of both the cooling water on the low temperature side and the cooling water on the high temperature side can be used effectively.

  That is, according to the present embodiment, the air blown into the vehicle interior is heated with one heater core using a mixture of the entire cooling water flowing out from both the first and second cooling water outlet portions 31b and 32b as a heat source. Compared with the case, the energy transmission efficiency from the cooling water to the air in the whole cooling water in the heater core can be increased. As a result, even when the amount of air blown by the blower is large, the air can be raised to a sufficiently high temperature, and heating can be established.

  Further, in the present embodiment, at the maximum heating (MAX HOT) at which the target blown air temperature TAO becomes maximum, as shown in FIG. 2, the position of the door 55 on the upstream side of the heating heat exchanger 2 is set to the lower side. The air flow path 52 is expanded in the middle and the upper air flow path 53 is narrowed in the middle. Note that, during maximum heating, the air mix door is positioned to close the bypass air passage, and the foot mode is selected as the air outlet mode.

  Thereby, the wind speed distribution of the blown air passing through the heat exchanger 2 for heating becomes a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side. Then, the blown air that has passed through the lower region of the heating heat exchanger 2 is blown out from the foot outlet, and the blown air that has passed through the upper region of the heating heat exchanger 2 is blown out from the defroster outlet.

  Next, main features of the present embodiment will be described.

  (1) FIG. 4 shows the distribution of the outlet air temperature of the heating heat exchanger 2 in this embodiment, and FIG. 5 shows the distribution of the outlet air temperature of the heating heat exchanger 2 in Comparative Example 1. In the first comparative example, the upstream partition wall 54 and the door 55 in FIG. 2 are omitted from the present embodiment, and the air velocity of the blown air passing through the heating heat exchanger 2 is made uniform.

  As shown in FIG. 5, in Comparative Example 1 as well, a small flow rate of cooling water flows from the lower side of the second heater core 20 to the upper side in the second heater core 20. The temperature of the blown air after passing through is high, and the temperature of the blown air after passing through the upper region becomes low.

  On the other hand, as shown in FIG. 4, in the present embodiment, the temperature of the blown air after passing through the lower region of the second heater core 20 is higher than that of the first comparative example, and the upper region. The temperature of the blown air after passing through is lower.

In this embodiment, the wind speed distribution of the blown air passing through the heat exchanger 2 for heating is a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side, and is below the second heater core 20. This is because the temperature efficiency φ in the side region is increased. The temperature efficiency φ is expressed by the following equation. φ = (Outlet air temperature−Inlet air temperature) / (Water temperature−Inlet air temperature)
For this reason, according to this embodiment, compared with the comparative example 1, the blowing air temperature from a foot blower outlet can be raised, and the feeling of warmth of a passenger | crew's feet can be improved. Moreover, according to this embodiment, it becomes possible to raise the temperature of the air blown from the foot outlet without increasing the amount of heat input to the heating.

  Further, according to the present embodiment, blown air having a high temperature after passing through the lower region of the second heater core 20 is blown out from a foot outlet that requires a high blown air temperature, and after passing through the upper region. It can be said that the temperature distribution generated in the conditioned air after passing through the heat exchanger 2 for heating is effectively utilized because the blown air having a low temperature is blown out from the defroster blower outlet that does not require a high blown air temperature.

  Note that the wind speed ratio is set to 1 from the viewpoint of positively forming a wind speed distribution that is high on the upper side and low on the lower side in the blown air passing through the heat exchanger 2 for heating. When the maximum wind speed is preferably 1.43 or more.

  Further, in the present embodiment, the position of the upstream door 55 of the heating heat exchanger 2 is set to a position where the lower air flow path 52 is expanded in the middle and the upper air flow path 53 is narrowed in the middle. Was during maximum heating, that is, when the foot mode was selected as the outlet mode, but the bi-level mode that blows conditioned air from both the foot outlet and the face outlet was selected as the outlet mode. It is also good when it is.

  In this case, since the difference between the temperature of the air blown from the foot outlet and the temperature of the air blown from the face outlet is large, passenger comfort is improved.

  Also in this case, the blower air having a high temperature after passing through the lower region of the second heater core 20 is blown out from the foot outlet, and the blown air having a low temperature after passing through the upper region is blown out with low blown air. Since it blows out from the face blower outlet which requires temperature, it can be said that the temperature distribution produced in the conditioned air after passing through the heat exchanger 2 for heating is effectively used.

  (2) In the present embodiment, as shown in FIG. 3, the cooling water inlets 10 a and 20 a of the first and second heater cores 10 and 20 are on the driver seat side in the vehicle left-right direction of the inlet side tank parts 12 and 22. Has been placed.

  Here, as described above, the second heater core 20 is configured such that a small flow rate of cooling water flows from the bottom to the top. Generally, in a liquid, when a high temperature part exists under the liquid, the high temperature part rises by buoyancy. In the second heater core 20, the cooling water flows through the tube 21 while exchanging heat with the air. Therefore, the temperature of the cooling water flowing into the inlet side tank unit 22 is higher than that of the cooling water in the outlet side tank unit 23. high. Therefore, the high-temperature cooling water that has flowed into the inlet side tank unit 22 is affected by buoyancy. At this time, when the cooling water flowing into the second heater core 20 has a smaller flow rate than the cooling water flowing into the first heater core 10 and has a low flow rate, the influence of this buoyancy becomes large.

  For this reason, most of the cooling water flowing into the inlet side tank unit 22 flows through the tube 21 close to the cooling water inlet 20a, and the blown air after passing through the second heater core 20 is closer to the driver's seat than to the passenger seat. The temperature becomes higher.

  Therefore, in the case where the blast air after passing through the second heater core 20 branches to one side and the other side in the vehicle left-right direction, and the conditioned air is blown out from the air outlet on the driver seat side and the air outlet on the passenger seat side, The blowing air temperature on the driver's seat side where the boarding frequency is high can be made higher than the blowing air temperature on the passenger seat side.

  The cooling water inlet 10a of the first heater core 10 may be arranged on the passenger seat side. This is because the cooling water flowing into the first heater core 10 has a large flow rate, and the temperature distribution in the vehicle left-right direction as in the second heater core 20 does not occur.

  (3) In this embodiment, as shown in FIG. 2, the cooling water inlets 10a and 20a of the first and second heater cores 10 and 20 are both arranged on the same lower side.

  Here, FIG. 6 shows the temperature distribution of the inlet air and the temperature distribution of the cooling water in the second heater core 20 of the present embodiment. FIG. 7 shows the temperature distribution of the inlet air and the temperature distribution of the cooling water in the second heater core 20 of Comparative Example 2. The comparative example 2 changes the cooling water inlet 10a of the 1st heater core 10 to the upper side with respect to this embodiment.

  As shown in FIG. 7, in Comparative Example 2, the temperature difference ΔT between the inlet air temperature and the water temperature on the upper side of the second heater core 20 is small. In contrast, as shown in FIG. 6, in the present embodiment, the temperature difference ΔT between the inlet air temperature and the water temperature is large in the entire vertical direction of the second heater core 20.

  From this, according to this embodiment, compared with the case where the cooling water inlets 10a and 20a of the first and second heater cores 10 and 20 are arranged on different sides as in the comparative example 2, the second heater core 20 Thus, the amount of heat taken from the cooling water is improved, and the heat exchange performance of the second heater core is improved.

(Second Embodiment)
In FIG. 8, the side view of the heat exchanger 2 for a heating of the state hold | maintained at the air-conditioning case 51 in this embodiment is shown. In the present embodiment, the upstream partition wall 54 and the door 55 in FIG. 2 described in the first embodiment are changed to a fixed upstream partition wall 59.

  The upstream partition wall 54 of the first embodiment is provided at a position where the air flow rate Q1 of the lower air flow path 52 and the air flow rate Q2 of the upper air flow path 53 are the same. The upstream partition wall 59 is provided at a position where the air flow rate Q2 of the upper air flow channel 53 is larger than the air flow rate Q1 of the lower air flow channel 52.

  In the present embodiment, the lower air flow path 52 is expanded in the middle and the upper air flow path 53 is narrowed in the middle by the upstream partition wall 59. Thereby, also in the present embodiment, as in the first embodiment, the air flow rates Q1 and Q2 in the lower air flow path 52 and the upper air flow path 53 and the air flow immediately before the heating heat exchanger 2 are the same. The relationship between the road cross-sectional areas A21 and A22 only needs to be Q1 / A11 <Q2 / A21. As a result, the wind speed distribution of the blown air passing through the heating heat exchanger 2 becomes a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side. Therefore, the present embodiment is the same as the first embodiment. The effect is obtained.

(Third embodiment)
In FIG. 9, the side view of the heat exchanger 2 for a heating of the state hold | maintained at the air-conditioning case 51 in this embodiment is shown. In the present embodiment, the upstream partition wall 54 and the door 55 in FIG. 2 described in the first embodiment are changed to a fixed upstream partition wall 71, and the air flow downstream of the heating heat exchanger 2 is changed. In the lower air flow path 56, an inhibiting member 72 that inhibits the air flow is arranged.

  The obstruction member 72 is plate-shaped, and is fixed so that the plate surface is substantially orthogonal to the air flow.

  In the present embodiment, the pressure in the lower air flow path 56 is increased by the inhibition member 72 provided in the lower air flow path 56 as compared with the case where the inhibition member 72 is not provided. The flow rate of the blown air passing through the lower region of the heat exchanger 2 decreases, and the wind speed decreases.

  As a result, also in the present embodiment, the wind speed distribution of the blown air passing through the heating heat exchanger 2 becomes a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side, so that it is the same as in the first embodiment. The effect is obtained.

  In the present embodiment, the blocking member 72 is fixed, but the blocking member 72 may be configured as a cantilever door so that the position can be changed. Thereby, you may switch the position of the inhibiting member 72 to the position which inhibits the air flow of the lower air flow path 56, and the position which does not inhibit. For example, if the cooling water temperature flowing into the first heater core 10 is relatively high, the temperature of the air blown from the foot outlet becomes high. In such a case, the position of the inhibition member 72 is set to the lower air. It can be set as the position which does not inhibit the air flow of channel 56.

(Fourth embodiment)
In FIG. 10, the front view of the heat exchanger 2 for a heating in this embodiment is shown. This embodiment changes the fin pitch of the corrugated fins 14 and 24 which the 1st, 2nd heater cores 10 and 20 of the heat exchanger 2 for a heating have with respect to 1st Embodiment. The fin pitch is an interval between adjacent fin ridges. In this embodiment, there is no upstream partition wall on the upstream side of the air flow of the heat exchanger 2 for heating, and a downstream partition is provided on the downstream side of the air flow of the heat exchanger 2 for heating as in the first embodiment. A wall 58 is provided.

  Specifically, as shown in FIG. 10, the fin pitch fp1 in the lower region of the heat exchanger 2 for heating is small, and the fin pitch fp2 in the upper region is large. For this reason, the fins 14 and 24 are dense in the lower region of the heat exchanger 2 for heating, and the fins 14 and 24 are sparse in the upper region. As a result, since the ventilation resistance is large in the lower region of the heat exchanger 2 for heating, the wind speed of the blown air passing through the lower region is small. On the other hand, in the upper region of the heat exchanger 2 for heating, since the ventilation resistance is small, the wind speed of the blown air passing through the lower region is increased.

  Thus, also in the present embodiment, the wind speed distribution of the blown air passing through the heat exchanger 2 for heating is a wind speed distribution in which the wind speed is high on the upper side and the wind speed is low on the lower side. Similar effects can be obtained.

(Other embodiments)
(1) In the first embodiment, the lower air flow path 52 expands in the middle and the flow cross-sectional area increases, and the upper air flow path 53 narrows in the middle and the flow cross-sectional area decreases. Both are adopted, but either one may be adopted. Even if either one is adopted, it is possible to give a wind speed distribution to the blown air passing through the heating heat exchanger 2 with a high wind speed on the upper side and a low wind speed on the lower side.

  (2) In the first, second, and fourth embodiments, the upper air flow channel 57 and the lower air flow channel 56 are partitioned by the downstream partition wall 58 on the downstream side of the heating heat exchanger 2. However, the downstream partition wall 58 may be omitted. Most of the blown air after passing through the upper region of the heating heat exchanger 2 is guided to the defroster outlet and the face outlet, and much of the blown air after passing through the lower region of the heating heat exchanger 2 It only needs to be guided to the foot outlet.

  (3) In the third embodiment, on the upstream side of the heat exchanger 2 for heating, the upper air flow channel 53 and the lower air flow channel 52 are partitioned by the upstream partition wall 71. The wall 71 may be omitted.

  (4) In each of the above-described embodiments, the cooling water flows through the second heater core 20 from the lower side to the upper side. For example, the cooling water may flow from the upper side to the lower side. In short, in the present invention, it is sufficient that the cooling water flows in one direction from one side of the second heater core 20 to the other side. In this case, the lower region and the upper region of the heating heat exchanger are the one region and the other region, respectively.

  (5) In the above-described embodiments, the first heater core 10 and the second heater core 20 are integrated. However, the first heater core 10 and the second heater core 20 may be separated.

  Further, in each of the above-described embodiments, the direction of the cooling water flow in the first heater core 10 is the same direction from the bottom to the top as the second heater core 20, but from the top to the bottom opposite to the second heater core 20. It may be in the direction.

  (6) In each of the embodiments described above, the cooling water flowing out from the first cooling water outlet 31b of the engine 30 was only the cooling water that cooled the cylinder head 31, but the cooling water that cooled the cylinder head 31 The cooling water in which a part of the cooling water for cooling the cylinder block 32 is mixed may be used. In short, it is only necessary that the cooling water mainly cooling the cylinder head 31 flows out from the first cooling water outlet 31b of the engine 30.

  Similarly, the cooling water flowing out from the second cooling water outlet 32b of the engine 30 was only the cooling water that cooled the cylinder block 32, but the cylinder head 31 was cooled with respect to the cooling water that cooled the cylinder block 32. Cooling water mixed with a part of the cooling water may be used. In short, the cooling water mainly cooling the cylinder block 32 flows out from the second cooling water outlet 32b of the engine 30, and the cooling water flowing out from the second cooling water outlet 32b rather than the cooling water flowing out from the first cooling water outlet 31b. As long as the temperature is higher.

  However, the cooling water flowing out from the second cooling water outlet 32b of the engine 30 has a higher temperature than when all of the cooling water after cooling the cylinder head 31 and the cooling water after cooling the cylinder block 32 are mixed. To do. Thereby, it is because a high temperature cooling water can be made to flow out from the engine 30 compared with the case where both cooling water is mixed together.

  (7) In each of the above-described embodiments, the cooling water flowing into the second heater core 20 is only the cooling water flowing out from the second cooling water outlet 32b of the engine 30, but the cooling water flowing out from the first cooling water outlet 31b. A part of the cooling water may be mixed.

  In short, it is only necessary that the cooling water mainly flows out from the second cooling water outlet 32 b and has a higher temperature than the cooling water flowing into the first heater core 10 and flows into the second heater core 20. However, the cooling water flowing into the second heater core 20 has a temperature higher than the average temperature when the cooling water flowing out from the second cooling water outlet 32b and the cooling water flowing out from the first cooling water outlet 31b are all mixed. . This is because the air temperature after heating by the second heater core 20 can be increased as compared with the case where both the cooling waters are all mixed.

  (8) In each of the embodiments described above, the first heater core 10 uses the cooling water after cooling the cylinder head as a heat source, and the second heater core 20 uses the cooling water after cooling the cylinder block as a heat source. The two heater core 20 may use another liquid as a heat source. The present invention can be applied when the first heater core 10 uses the first liquid as a heat source and the second heater core 20 uses the second liquid having a higher temperature and a lower flow rate than the first liquid as a heat source.

  For example, in a vehicle air conditioner mounted on a hybrid vehicle, engine coolant can be used as the first liquid, and coolant of an electric device such as an inverter can be used as the second liquid. Further, for example, in a vehicle air conditioner mounted on an electric vehicle, a cooling liquid of an electric device such as an inverter is used as the first liquid, and a high-temperature liquid heated by heating means such as an electric heater is used as the second liquid. Can do.

  (9) You may combine each above-mentioned embodiment in the range which can be implemented.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 2 Heating heat exchanger 10 1st heater core (1st heat exchange part)
20 2nd heater core (2nd heat exchange part)
20a Cooling water inlet 21 Tube 22 Inlet side tank part 23 Outlet side tank part 24 Heat transfer fin 51 Air conditioning case 52 Air flow of heating heat exchanger Lower air flow path on upstream side 53 Air flow of heating heat exchanger Upper air flow path at upstream side 72 Inhibiting member

Claims (8)

An air-conditioning case (51) that forms an air flow path for the blast air toward the passenger compartment;
A heat exchanger (2) for heating that heats the blown air using a first liquid and a second liquid having a higher temperature and a lower flow rate than the first liquid as a heat source; ,
The heating heat exchanger (2) is heated by the first heat exchange unit (10) for exchanging heat between the first liquid and the blown air, and the second liquid and the first heat exchange unit (10). has been the blower second heat exchange unit and an air to heat exchange and a (20),
The second heat exchanging part (20) has an inside on the other side in which the second liquid is located on the second liquid flow upstream side of the second heat exchanging part (20) from the one side on the second liquid flow downstream side. To flow to
The wind speed distribution of the blown air passing through the heating heat exchanger (2) is a wind speed distribution in which the wind speed on the other side is high and the wind speed on the one side is low, and the heating heat exchanger (2 ), The blown air after passing through the region on the one side is blown out from the foot outlet, and the blown air after passing through the region on the other side of the heat exchanger for heating (2) other than the foot outlet. The vehicle air conditioner is configured to blow out from the air outlet.   The air-conditioning case (51) is an air flow path that expands in the middle and increases the cross-sectional area of the air flow as the air flow path of the blown air flowing into the region on the one side of the heat exchanger (2) for heating. The vehicle air conditioner according to claim 1, wherein (52) is formed.   The air-conditioning case (51) is an air flow path that narrows in the middle and decreases the cross-sectional area as the air flow path of the blown air that flows into the other region of the heat exchanger (2) for heating. (53) is formed, The vehicle air conditioner of Claim 1 or 2 characterized by the above-mentioned. The first heat exchanging part (10) and the second heat exchanging part (20) are both joined to the laminated tubes (11, 21) and the outer surface of the tubes (11, 21). Corrugated heat transfer fins (14, 24),
The heat transfer fins (14, 24) have a small fin pitch (fp1) in the region on the one side of the heat exchanger (2) for heating, and a fin pitch (fp2) in the region on the other side. The vehicular air conditioner according to claim 1, wherein the vehicular air conditioner is larger. In the air conditioning case (51), the air flow path on the downstream side of the air flow of the heat exchanger for heating (2) is positioned on one side of the air flow path (56) on the one side and on the other side. A downstream partition wall (58) is provided for partitioning with the other air flow path (57);
The vehicle air conditioner according to claim 1, wherein an obstruction member (72) for obstructing an air flow is provided in the one air flow path (56).   The air outlets other than the foot air outlets are the face air outlets when the air outlet mode is a bi-level mode in which conditioned air is blown from both the foot air outlets and the face air outlets. The vehicle air conditioner according to any one of 5. The second heat exchanging section (20) communicates with a plurality of stacked tubes (21) and one end side in the longitudinal direction of the plurality of tubes (21), and forms an inlet side tank section (22) serving as a liquid inlet side. ), And an outlet side tank portion (23) that communicates with the other end in the longitudinal direction of the plurality of tubes (21) and serves as a liquid outlet side,
The second heat exchange part (20) is held in the air conditioning case (51) so that the inlet side tank part (22) is located on the lower side and the outlet side tank part (23) is located on the upper side. Has been
The liquid inlet (20a) of the inlet side tank part (22) is arranged on the driver's seat side in the vehicle left-right direction of the inlet side tank part (22). The vehicle air conditioner according to claim 1. The air conditioning case (51) bypasses the heating heat exchanger (2), the bypass air passage through which the blown air flows, the blown air from the bypass air passage, and the heating heat exchanger (2). And an air mix door for adjusting the mixing ratio with the blown air after passing through,
During maximum heating in which the air mix door is positioned to close the bypass air passage, the wind speed distribution of the blown air passing through the heat exchanger for heating (2) has a higher wind speed on the other side, The vehicle air conditioner according to any one of claims 1 to 7, characterized in that the wind speed distribution on the side is a low wind speed distribution.

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