JP2012144222A - Vehicular air-conditioning device - Google Patents

Abstract

A vehicle air conditioner capable of reducing a temperature difference in the left-right direction generated in air-conditioned air after passing through a heat exchanger for heating is provided.
A first heater core that exchanges heat between a first liquid and air blown into a vehicle interior; a second liquid that is hotter and has a lower flow rate than the first liquid; and air that is heated by the first heater core. The heating heat exchanger 2 including the second heater core 20 for exchanging heat is air-conditioned so that the inlet side tank portion 22 is at the bottom and the outlet side tank portion 23 is at the top, and the longitudinal direction of the tube 21 is inclined. The case 51 is held. Thereby, the high temperature 2nd liquid which flowed into the 2nd heater core 20 is an area | region above the inlet side edge part 21a of the tube 21 among the inlet side tank parts 22, Comprising: The lamination direction of the some tube 21 The liquid is stored in the liquid storage part 71 over the entire area, and then flows into the plurality of tubes 22.
[Selection] Figure 2

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, it turned out that the temperature distribution with a large temperature difference of the left-right direction will arise in the air-conditioning wind after passing through the heat exchanger for heating as follows.

  That is, the second heat exchanging unit communicates with the stacked tubes, the one end side in the longitudinal direction of the plurality of tubes, and the inlet side tank unit serving as the cooling water inlet side, and the other end side in the longitudinal direction of the plurality of tubes And an outlet side tank portion which is the cooling water outlet side. This second heat exchange part is held in the air conditioning case so that the inlet side tank part is located on the lower side and the outlet side tank part is located on the upper side, and the cooling water is moved from the bottom to the upper part in the second heat exchange part. When flowing, it has been found that a phenomenon occurs in which most of the cooling water flowing into the inlet side tank portion flows through the tube close to the cooling water inlet and the cooling water hardly flows from the cooling water inlet to the tube far from the cooling water inlet.

  This is for the following reason. Generally, in a liquid, when a high temperature part exists under the liquid, the high temperature part rises by buoyancy. And in the 2nd heat exchange part, since cooling water flows while exchanging heat with air in a tube, the temperature of the cooling water which flowed into the entrance side tank part is higher than the cooling water in the exit side tank part. For this reason, the high-temperature cooling water that has flowed into the inlet side tank unit is affected by buoyancy, and the cooling water that flows into the second heat exchange unit is more than the cooling water that flows into the first heat exchange unit. This is because the influence of this buoyancy increases when the flow rate is low and the flow rate is low.

  If temperature distribution with a large temperature difference in the left-right direction occurs in the conditioned air after passing through the heat exchanger for heating, for example, the conditioned air after passing through the heat exchanger for heating branches to one side and the other side in the vehicle left-right direction. Thus, when the conditioned air is blown out from the air outlet on the driver's seat side and the air outlet on the passenger seat side, there is a difference in the air temperature between the driver's seat side and the passenger seat side.

  Such a problem is not limited to the case where the first heat exchange unit uses the cooling water after cooling the cylinder head as a heat source, and the second heat exchange unit uses the cooling water after cooling the cylinder block as a heat source. This is a problem that occurs when the exchange unit uses the first liquid as the heat source, and the second heat exchange unit uses the second liquid having a higher temperature and a lower flow rate than the first liquid as the heat source.

  An object of this invention is to provide the vehicle air conditioner which can reduce the temperature difference of the left-right direction produced in the air-conditioning wind after passing through the heat exchanger for heating in view of the said point.

  In order to achieve the above object, according to the first aspect of the present invention, the second heat exchange section (20) is the second liquid flowing into the inlet side tank section (22), and the outlet side tank section (23). After the liquid having a temperature higher than that in the liquid is stored in the liquid storage sections (71, 72, 73, 74) in the inlet side tank section over the entire stacking direction of the plurality of tubes (21), the liquid is stored in the plurality of tubes (21). It is characterized by an inflowing configuration.

  According to the present invention, since such a configuration is adopted, even if the second liquid flowing through the second heat exchange unit has a lower flow velocity than the first liquid flowing through the first heat exchange unit, The temperature difference of the cooling water flowing through the tube can be reduced, and the temperature difference in the left-right direction generated in the conditioned air after passing through the heat exchanger for heating can be reduced.

  For the liquid storage part, for example, the formation method described in claims 2 to 4 can be adopted.

  That is, as in the invention described in claim 2, by inclining the second heat exchange part (20), the inlet side end part (21a) of the tube (21) in the inlet side tank part (22). A liquid storage part (71) can be formed in the region above the upper side.

  Further, as in the third aspect of the invention, the liquid storage part (72) is formed by inflating a part (91) of the wall constituting the inlet side tank part (22) outside the other part. Can be formed.

  Further, as in the invention described in claim 4, the insertion length (84) of the tube (21) inserted into the inlet side tank portion (22) of the second heat exchange portion (20) is set to the first length. The inlet side tank of the second heat exchange part (10) is made longer than the insertion length (85) of the tube (11) inserted into the inlet side tank part (12) of the heat exchange part (10). In the part (22), the liquid storage part (74) can be formed in the region above the inlet side end part (21a) of the tube (21) in the gravity direction.

  By the way, when the terminal opening (20a) of the liquid introduction path in the inlet side tank section (22) of the second heat exchange section (20) is projected in the longitudinal direction of the inlet side tank section (22), the liquid introduction path When the end opening (20a) is located directly below the inlet of the tube (21), the high-temperature liquid flowing into the inlet-side tank rises due to buoyancy, so the high-temperature liquid flows into the inlet-side tank. At that time, the high-temperature liquid flows into the tube located above the inflowing liquid.

  Therefore, in the invention described in claim 5, in the invention described in claims 1-4, at least a part of the end opening (20a) of the liquid introduction path is directly below the inlet of the tube (21) in the direction of gravity. It is characterized by being in a position excluding.

  According to this, since a part of the end opening of the liquid introduction path is out of the range directly below the tube, a part of the high temperature second liquid flowing in from the end opening of the liquid introduction path is reliably stored. Can be led to the department.

  As a configuration in which at least a part of the terminal opening (20a) of the liquid introduction path is located at a position excluding just below the inlet of the tube (21), for example, as in the invention according to claim 6, Two imaginary lines (81) in which at least a part of the end opening (20a) is drawn in parallel to the direction of gravity from the inner wall (21b) of the tube (21) at the inlet end (21a) of the tube (21). , 82), a configuration located outside can be employed. Further, as in the invention described in claim 7, at least a part of the terminal opening (20a) of the liquid introduction path is more than an imaginary line (83) passing through the inlet side end (21a) of the tube (21). A configuration located on the upper side can be adopted. The configurations described in both claims 6 and 7 can also be employed.

  Further, in the inventions according to claims 5 to 7, as in the invention according to claim 8, 35% or more of the total area of the terminal opening (20a) of the liquid introduction path is formed by the tube (21). It is preferable that it exists in the position except the right under the gravity direction of the entrance of this. Thereby, as shown in FIG. 10 described later, the temperature difference between the left and right blown air from the heating heat exchanger can be particularly reduced.

  Moreover, in invention of Claims 1-7, 2nd heat exchange part (20) is 2nd from the longitudinal direction one end side of an inlet side tank part (22) like invention of Claim 9. While the liquid flows in, the upper wall of the inlet side tank part (22) is inclined so that the other end side in the longitudinal direction is located above the one end side in the longitudinal direction of the inlet side tank part (22). It is preferable to be mounted on a vehicle. This is because it is easier to guide the high-temperature liquid flowing through the liquid storage part to the other end side in the longitudinal direction of the inlet side tank part as compared with the case where the upper wall of the inlet side tank part is horizontal.

  Further, in the inventions according to claims 1 to 9, as in the invention according to claim 10, the inlet side tank is provided inside the inlet side tank part (22) of the second heat exchange part (20). A flow rate increasing means (92) for increasing the flow rate of the second liquid flowing into the portion (22) can be provided.

  According to this, since the flow rate of the second liquid that has flowed into the inlet side tank portion can be increased after the flow rate increasing means (92), the means for increasing the flow rate of the cooling water is not provided. Compared to the case, the cooling water can flow to the side away from the second liquid inlet of the inlet side tank section. Therefore, according to the present invention, the temperature difference between the cooling water flowing through the plurality of tubes can be further reduced as compared with the case where the liquid storage part is formed, and the horizontal direction generated in the conditioned air after passing through the heat exchanger for heating is reduced. A temperature difference can be reduced.

  Moreover, in invention of Claims 1-10, like the invention of Claim 11, the flow-path cross-sectional area of the inlet side tank part (22) of a 2nd heat exchange part (20) is further, The second liquid is introduced into the inlet side tank part (22) of the second heat exchange part (20), or smaller than that of the first heat exchange part (10), or as in the invention of claim 12. It is preferable to make the flow path cross-sectional area of the liquid introduction path smaller than that of the first heat exchange section (10) or to employ both of them.

  In this way, the cooling water can be allowed to flow to the side away from the second liquid inlet of the inlet side tank part also by increasing the flow rate of the second liquid flowing into the inlet side tank part.

  In the invention according to claim 13, the flow velocity for increasing the flow velocity of the second liquid flowing into the inlet side tank portion (22) inside the inlet side tank portion (22) of the second heat exchange portion (20). A rising means (92) is provided.

  According to this, since the flow rate of the second liquid that has flowed into the inlet side tank portion can be increased after the flow rate increasing means (92), the means for increasing the flow rate of the cooling water is not provided. Compared to the case, the cooling water can flow to the side away from the second liquid inlet of the inlet side tank section. Therefore, according to this invention, the temperature difference of the cooling water which flows through a some tube can be reduced, and the temperature difference of the left-right direction produced in the conditioned air after passing through the heat exchanger for heating can be reduced.

  In addition, in invention of Claims 10-13, the flow velocity of the 2nd liquid which flows through the inlet side tank part (22) of a 2nd heat exchange part (20) is the inlet side tank of a 1st heat exchange part (10). It is preferable to be equal to or higher than the flow velocity of the first liquid flowing through the portion (12).

  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 front view of the 2nd heater core which shows the cooling water flow in a 1st embodiment. It is a front view of the 2nd heater core which shows the cooling water flow in comparative example 1. It is sectional drawing of the heat exchanger for heating in 2nd Embodiment. It is sectional drawing of the heat exchanger for heating in 3rd Embodiment. In 3rd Embodiment, it is a side view of the heat exchanger 2 for a heating for demonstrating inclination | tilt angle (theta) 1 of the 2nd heater core. It is a figure which shows the relationship between the temperature difference of the right-and-left blowing air from the heat exchanger 2 for a heating, and inclination | tilt angle (theta) 1 shown in FIG. It is a figure which shows the relationship between the temperature difference of the right-and-left blowing air from the heat exchanger 2 for heating, and the ratio of the area of the part in the position except just under the inlet of the tube 21 with respect to the total area of the cooling water inlet 20a. It is sectional drawing of the heat exchanger for heating in 4th Embodiment. It is sectional drawing of the heat exchanger for heating in 5th Embodiment. It is sectional drawing of the heat exchanger for heating in 6th Embodiment. It is a front view of the heat exchanger for heating in 7th Embodiment. It is a figure which shows the relationship between inclination-angle (theta) 2 of the heat exchanger for heating in 7th Embodiment, and right and left blowing air temperature difference. It is sectional drawing of the heat exchanger for heating in 8th Embodiment. It is sectional drawing of the heat exchanger for heating in 9th Embodiment. (A), (b) is the side view and front view of the heat exchanger for a heating in 10th Embodiment, respectively. It is a side view of the heat exchanger for heating in 11th 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.

  Thus, the engine 30 of this embodiment has two cooling systems. During steady operation of the engine 30, the cooling water flow rate in the cooling water flow path on the cylinder head side is made larger than the cooling water flow rate in the cooling water flow path on the cylinder block side so that the cylinder head 31 is more positive than the cylinder block 32. It is designed to cool down. This is because the anti-knock performance is improved by lowering the temperature of the cylinder head 31, and the low viscosity of the engine oil is maintained by maintaining the cylinder block 32 at a high temperature, thereby 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 0.2-3 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 heating 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 viewed from the downstream side of the air flow. The up and down arrows in the figure indicate the up and down direction parallel to the direction of gravity when mounted on the vehicle, and the same applies to other figures. Further, the vehicle at this time is located on a horizontal surface, not an inclined surface.

  As shown in FIGS. 2 and 3, the first and second heater cores 10 and 20 of the heating heat exchanger 2 are both laminated with a plurality of flat tubes 11 and 21 and a plurality of tubes 11 and 20. 21 is connected to one end side in the longitudinal direction, and is connected to the inlet side tank portions 12 and 22 that are the cooling water inlet side, and the other end side in the longitudinal direction of the plurality of tubes 11 and 21, and is the outlet side that is the cooling water outlet side. Tank portions 13 and 23 are provided.

  The heat exchanger 2 for heating is housed in the air conditioning case 51 together with a blower (not shown) that forms blown air toward the passenger compartment, and is mounted on the vehicle. Specifically, as shown in FIG. 2, the heating heat exchanger 2 is in an inclined state, and the air conditioning case so that the second heater core 20 is located on the downstream side of the air flow with respect to the first heater core 10. 51. The inclined state means a state where the air inflow / outflow surface of the heating heat exchanger 2 is not parallel to both the vertical direction and the horizontal direction, and the angle formed by the air outflow / inflow surface and the vertical direction is an acute angle. . Moreover, the direction of the air inflow / outflow surface of the heat exchanger 2 for heating coincides with the longitudinal direction of the tube 21 when the heat exchanger 2 for heating is viewed from the measuring method. In the present embodiment, the heating heat exchanger 2 is inclined so that the second heater core 20 is positioned above the first heater core 10. For this reason, the air flow direction passing through the first and second heater cores 10 and 20 is an obliquely upward direction.

  In this embodiment, as shown in FIG. 3, when the second heater core 20 is viewed from the front, the upper wall of the inlet side tank portion 22 of the second heater core 20 is parallel to the horizontal direction. A heat exchanger 2 is mounted on the vehicle.

  Although not shown in the air conditioning case 51, a bypass air passage through which the blown air flows around the heat exchanger 2 for heating, air after passing through the bypass air passage, and after passing through the heat exchanger 2 for heating And an air mix door for adjusting the mixing ratio with the air. In addition, the air flow path through which the air after passing through the heat exchanger 2 for heating flows is connected to the foot outlet on the lower side and connected to the defroster outlet and the face outlet on the upper side.

  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 10 a and 20 a are openings formed in the walls constituting the inlet side tank parts 12 and 22, face the inside of the inlet side tank parts 12 and 22, and cool the inlet side tank parts 12 and 22. It is the terminal opening part of the cooling water introduction path which introduces water. These cooling water inlets 10a and 20a are disposed on 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 one direction and are stacked so as to be aligned in a line in the left-right direction of the vehicle, which is a direction perpendicular to the one direction. . 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, the first and second heater cores 10 and 20 include corrugated heat transfer fins 14 and 24 joined to the outer surfaces of the tubes 11 and 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.

  The first heater core 10 and the second heater core 20 have the same size in the left-right and up-down 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.

  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.

  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 transfer coefficient 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, after the blower air is heated with the first heater core 10 using the low-temperature side cooling water as the heat source, the heated air is heated with the second heater core 20 using 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.

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

  4 and 5 show the cooling water flow in the second heater core 20 in the present embodiment and Comparative Example 1, respectively. In Comparative Example 1, the heat exchanger 2 for heating according to the present embodiment is installed vertically on the air conditioning case 51 so that the air inflow surface thereof is parallel to the vertical direction. Further, in Comparative Example 1, when the cooling water inlet 20a is projected in the longitudinal direction of the inlet side tank portion 22, the entire cooling water inlet 20a of the inlet side tank portion 22 is directly below the inlet side end portion 21a of the tube 21. The high-temperature cooling water is not stored in the liquid storage part.

  When the cooling water flowing into the second heater core 20 has a smaller flow rate and a lower flow rate than the cooling water flowing into the first heater core 10, in the comparative example 1 shown in FIG. In many cases, a phenomenon occurs in which the cooling water hardly flows from the cooling water inlet to the tube far from the cooling water inlet.

  On the other hand, in the present embodiment, as shown in FIG. 2, the second heater core 20 is inclined, and therefore, in the region above the inlet side end 21 a of the tube 21 in the inlet side tank portion 22, A liquid storage portion 71 that stores high-temperature cooling water is formed over the entire region of the plurality of tubes 21 in the stacking direction. The liquid storage portion 71 is formed at a corner portion at the highest position among corner portions of the inlet side tank portion 22.

  For this reason, as shown in FIG. 4, the cooling water that has flowed into the inlet side tank unit 22 and is hotter than the cooling water in the outlet side tank unit is stored in the liquid storage unit 71 due to the influence of buoyancy. Then, it flows into each of a plurality of tubes from this liquid storage part 71.

  In particular, in the present embodiment, as shown in FIG. 2, when the cooling water inlet 20 a is projected in the longitudinal direction of the inlet side tank unit 22 (perpendicular to the paper surface in FIG. 2), a part of the cooling water inlet 20 a The tube 21 is positioned outside the tube inner extension line (imaginary line) 81 drawn parallel to the direction of gravity from the tube inner wall 21b at the inlet side end 21a.

  Here, when the cooling water inlet 20a is projected in the longitudinal direction of the inlet side tank unit 22, if all of the cooling water inlets 20a of the inlet side tank unit 22 are located directly below the inlet of the tube 21 in the gravity direction, Since the high-temperature cooling water that has flowed into the side tank section 22 rises due to buoyancy, when high-temperature cooling water flows into the inlet-side tank section 22 from the cooling water inlet 20a, the high-temperature cooling water flows into the tube 21 positioned above the flowing cooling water. Hot cooling water will flow in.

  On the other hand, in this embodiment, since a part of the cooling water inlet 20a is located at a position other than directly below the inlet of the tube 21, a part of the high-temperature cooling water flowing from the cooling water inlet 20a is reliably stored. It can be led to the part 71.

  Therefore, according to this embodiment, the temperature difference in the vehicle left-right direction of the cooling water flowing through the heat exchange core portion 25 can be reduced as compared with the first comparative example. Therefore, according to this embodiment, the temperature difference in the left-right direction of the vehicle generated in the conditioned air after passing through the heating heat exchanger 2 can be reduced.

  As a result, the conditioned air after passing through the heat exchanger 2 for heating branches into one side and the other side in the left-right direction of the vehicle, 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. In this case, the difference in the temperature of the blown air between the driver seat side and the passenger seat side in the passenger compartment is reduced.

  Moreover, according to this embodiment, since the substantial heat exchange area in the heat exchange core part 25 increases compared with the comparative example 1, the amount of heat that can be taken from the cooling water in the heat exchange core part 25 is improved. Heat exchange performance is improved.

(Second Embodiment)
FIG. 6 shows a cross-sectional view of the heat exchanger 2 for heating in the present embodiment. 6 is a view seen in the same direction as FIG.

  Also in the present embodiment, as shown in FIG. 6, the second heater core 20 is inclined, so that the liquid storage part is located in the area above the inlet side end 21 a of the tube 21 in the inlet side tank part 22. 71 is formed.

  Furthermore, in this embodiment, the positional relationship between the cooling water inlet 20a and the tube 21 in the inlet side tank portion 22 of the second heater core 20 is as follows. That is, as shown in FIG. 6, when the cooling water inlet 20 a is projected in the longitudinal direction of the inlet side tank portion 22, a part of the cooling water inlet 20 a (the region not hatched in FIG. 6) is the tube 21. Is located below the inlet side end (lower end surface) 21a.

  And most of the cooling water inlet 20a (shaded area in FIG. 6) is between two imaginary lines 81, 82 drawn in parallel to the gravity direction from the tube inner wall 21b at the inlet side end 21a of the tube 21. Located outside. Here, the majority of the cooling water inlet 20a means a portion occupying 50% or more of the area of the cooling water inlet 20a. Further, the position between the two imaginary lines 81 and 82 and below the inlet of the tube 21 is a position directly below the inlet of the tube 21.

  Thus, in this embodiment, since most of 50% or more of the total area of the cooling water inlet 20a protrudes outside from the region between the two imaginary lines 81 and 82, from the cooling water inlet 20a. More than half of the inflowing cooling water can be guided to the liquid storage unit 71.

(Third embodiment)
FIG. 7 shows a sectional view of the heating heat exchanger 2 in the present embodiment. FIG. 7 is a view seen in the same direction as FIG.

  Also in the present embodiment, as shown in FIG. 7, the second heater core 20 is inclined so that the inlet side end portion of the tube 21 in the inlet side tank portion 22 is the same as in the first and second embodiments. A liquid storage part (not shown) is formed in a region above 21a.

  The positional relationship between the cooling water inlet 20a and the tube 21 in the inlet side tank portion 22 of the second heater core 20 is as follows.

  That is, as shown in FIG. 7, when the cooling water inlet 20 a is projected in the longitudinal direction of the inlet side tank portion 22, a part of the cooling water inlet 20 a (the region not hatched in FIG. 7) is the tube 21. The inlet side end (lower end surface) 21a is located directly below. The other part of the cooling water inlet 20a (the hatched area in FIG. 7) is at a position excluding just below the tube 21. Specifically, a part of the cooling water inlet 20a (the hatched area in which the direction of the oblique line in FIG. 7 is from the upper left to the lower right) is parallel to the gravity direction from the tube inner wall 21b at the inlet side end 21a of the tube 21. It is located outside the space between the two imaginary lines 81 and 82 drawn. Further, a part of the cooling water inlet 20a (a hatched area in which the direction of the oblique line in FIG. 7 is from the upper right to the lower left) is located above the virtual line 83 passing through the inlet side end 21a of the tube 21, and the cooling water A part of the inlet 20 a overlaps with the tube 21. The inlet side end portion 21 a through which the virtual line 83 passes is the inlet side end side of the tube 21 when the cooling water inlet 20 a is projected in the longitudinal direction of the inlet side tank portion 22. Moreover, being located above the virtual line 83 means being located on the other end side in the longitudinal direction of the tube 21 from the virtual line 83.

  Incidentally, as in the case of the first heater core 10, when the flowing cooling water has a large flow rate, a part of the cooling water inlet is positioned above the inlet side end of the tube, and a part of the cooling water inlet is connected to the tube. If the positional relationship overlaps, there is a problem that the pressure loss increases when the cooling water flows through the inlet side tank unit 22, and thus such positional relationship cannot be adopted. On the other hand, since the problem of such an increase in pressure loss does not occur if the cooling water flowing in has a small flow rate as in the second heater core 20, a part of the cooling water inlet 20a is connected to the tube 21. Can be used.

  Thus, in addition to positioning a part of the cooling water inlet 20a outside the space between the two virtual lines 81 and 82 parallel to the direction of gravity, the cooling water inlet 20a is located above the inlet side edge of the tube 21. Also by positioning, a part of the high-temperature cooling water flowing from the cooling water inlet 20a can be reliably guided to the liquid storage part 71. As a result, according to the present embodiment, it is possible to reduce the temperature difference in the left-right direction of the vehicle that occurs in the conditioned air after passing through the heat exchanger 2 for heating.

  Here, the ratio of the area of the portion at the position excluding the area directly below the inlet of the tube 21 to the total area of the cooling water inlet 20a (hereinafter simply referred to as the area ratio) and the conditioned air after passing through the heat exchanger 2 for heating. The relationship with the effect of reducing the temperature difference in the left-right direction of the vehicle will be described.

  FIG. 8 is a side view of the heating heat exchanger 2 for explaining the inclination angle θ <b> 1 of the second heater core 20. FIG. 9 is an evaluation result showing the relationship between the temperature difference between the left and right blown air from the heating heat exchanger 2 and the inclination angle θ1 shown in FIG. FIG. 10 shows an evaluation result in which the horizontal axis in FIG. 9 is changed from the tilt angle θ1 to the area ratio. As shown in FIG. 8, the inclination angle θ1 is an angle formed between the longitudinal direction of the tube 21 and the vertical direction when the heating heat exchanger 2 is viewed from the side. The temperature difference between the left and right blown air from the heating heat exchanger 2 is the average temperature of the blown air from one half and the average of the blown air from the other half of the heating heat exchanger in the left-right direction. It is the difference (absolute value) from the temperature.

  Incidentally, in the heating heat exchanger 2 shown in FIG. 8, the cooling water inlet 20a is provided at the end on one side in the left-right direction, similarly to the heating heat exchanger shown in FIG. In the heating heat exchanger 2 shown in FIG. 8, the diameter of the cooling water inlet 20a is substantially equal to the inner diameter of the tube 21 in the air flow direction, and the center of the cooling water inlet 20a and the center of the tube 21 are the same. The cooling water inlet 20 a is partly located above the inlet side end of the tube 21.

  In such a heat exchanger 2 for heating, when the inclination angle θ1 changes, the area ratio also changes. Specifically, each of inclination angles θ1 in FIG. 9 of 0, 10, 20, 50, and 90 degrees corresponds to the area ratio in FIG. 10 of 8, 25, 35, 65, and 100%. When the inclination angle θ1 is 0 degree, the portion located outside the space between the two virtual lines 81 and 82 parallel to the direction of gravity at the cooling water inlet 20a (the direction of the oblique lines in FIG. 7 is from the upper left to the lower right) The area of the hatched area) is minimized. When the inclination angle θ1 is increased, as shown in FIG. 7, the area of the portion of the cooling water inlet 20a located outside the space between the two virtual lines 81 and 82 parallel to the direction of gravity increases. To do. When the inclination angle θ1 is 90 degrees, the inlet-side end of the tube 21 is parallel to the vertical direction, so the virtual lines 81 and 82 overlap one another, and there is no region directly below the inlet of the tube 21. The ratio is 100%. The area of the portion where the cooling water inlet 20a overlaps the tube 21 is constant regardless of the inclination angle θ.

  9 and 10, the temperature difference between the left and right blown air from the heating heat exchanger 2 tends to decrease as the inclination angle θ1 increases, that is, the area ratio increases. In particular, when the inclination angle θ1 is 20 degrees or more, that is, when the area ratio is 35% or more, the temperature difference between the left and right blown air is when the inclination angle θ1 is 90 degrees, that is, when the area ratio is 100%. The temperature difference is close. From this, it can be said that the area ratio is preferably 35% or more in order to particularly reduce the temperature difference between the left and right blown air from the heating heat exchanger 2.

  Further, in this embodiment, since a part of the cooling water inlet 20a is in a positional relationship overlapping with the tube 21, as can be seen in comparison with the inlet side tank portion 22 in FIG. 6 described in the second embodiment, The dimension in the tube longitudinal direction of the inlet side tank part 22 can be made small.

  In the present embodiment, a part of the cooling water inlet 20a is parallel to the direction of gravity so that a part of the cooling water inlet 20a (shaded area in FIG. 7) is located at a position other than directly below the tube 21. Both the positioning between the imaginary lines 81 and 82 and the imaginary line 83 passing through the inlet side end of the tube 21 are both employed, but only one of them is employed. You may do it. Also in these cases, it is preferable that the area ratio is 35% or more as in the present embodiment.

(Fourth embodiment)
FIG. 11 shows a sectional view of the heating heat exchanger 2 in the present embodiment. FIG. 11 is a view seen in the same direction as FIG.

  In the present embodiment, unlike the first to third embodiments described above, the vehicle mounting posture of the heating heat exchanger 2 is a posture in which the air inflow / outflow surface is parallel to the vertical direction. That is, the heating heat exchanger 2 is held in the air conditioning case with the longitudinal direction of the tubes 11 and 21 being parallel to the vertical direction.

  In the second heater core 20, a portion 91 of the wall constituting the inlet side tank portion 22 swells outward from the other portions, and the swelled portion 91 causes the liquid storage portion 72 to store high-temperature cooling water. Is formed. In addition, the liquid storage part 72 of this embodiment is also an area | region above the inlet side edge part 21a of the tube 21 among the inlet side tank parts 22. FIG.

  Specifically, although not shown, the inlet side tank portion 22 is an upper wall constituting the inlet side tank portion 22 in which a core plate into which the tube 21 is inserted and the tank main body portion are combined. A part 91 of the core plate bulges outward.

  Also in the present embodiment, the positional relationship between the cooling water inlet 20a and the tube 21 in the inlet side tank unit 22 is as follows.

  That is, as shown in FIG. 11, a part of the cooling water inlet 20 a (region not hatched in FIG. 11) is located below the inlet side end (lower end surface) 21 a of the tube 21. . A part of the cooling water inlet 20a (the hatched area in FIG. 11) is between the two imaginary lines 81 and 82 drawn in parallel to the direction of gravity from the tube inner wall 21b at the inlet side end 21a of the tube 21. It is located outside.

  Therefore, also in this embodiment, since a part of the cooling water inlet 20a is located at a position other than directly below the inlet of the tube 21, the high-temperature cooling water flowing from the cooling water inlet 20a is reliably guided to the liquid storage part 72. Can do. And since a high temperature cooling water can be made to flow in into each of the some tube 21 from this liquid storage part 72, the temperature difference in the vehicle left-right direction of the cooling water which flows through a heat exchange core part can be reduced, and it is for heating The temperature difference in the left-right direction of the vehicle generated in the conditioned air after passing through the heat exchanger 2 can be reduced. In the present embodiment, it is preferable that the area ratio is 35% or more, as in the third embodiment.

(Fifth embodiment)
FIG. 12 shows a sectional view of the heating heat exchanger 2 in the present embodiment. FIG. 12 is a view seen in the same direction as FIG.

  In this embodiment, the direction of the heat exchanger 2 for heating described in the third embodiment is changed to a direction in which the longitudinal directions of the tubes 11 and 21 are parallel to the vertical direction, as in the fourth embodiment. . However, in this embodiment, the bulging portion 91 in FIG. 11 described in the fourth embodiment is not provided in the inlet side tank portion 22 of the second heater core 20.

  Specifically, as shown in FIG. 12, also in this embodiment, a liquid storage portion 73 is formed in a region of the inlet side tank portion 22 above the inlet side end portion 21 a of the tube 21.

  In addition, when the cooling water inlet 20a is projected in the longitudinal direction of the inlet side tank portion 22, a part of the cooling water inlet 20a (the region not shaded in FIG. 12) is the inlet side end (lower side) of the tube 21. End face) 21a is located below.

  A part of the cooling water inlet 20a (the hatched area in which the direction of the oblique line in FIG. 12 is from the upper left to the lower right) is drawn in parallel to the gravity direction from the tube inner wall 21b at the inlet side end 21a of the tube 21. It is located outside the space between the two virtual lines 81 and 82. Furthermore, a part of the cooling water inlet 20a (a hatched area in which the direction of the oblique line in FIG. 12 is from the upper right to the lower left) is located above the virtual line 83 passing through the inlet side end of the tube 21.

  Therefore, also in this embodiment, there exists an effect similar to 3rd Embodiment. In the present embodiment, it is preferable that the area ratio is 35% or more, as in the third embodiment.

  Further, from the viewpoint of securing the volume of the liquid storage part 73, it is inserted into the inlet side tank part 22 of the second heater core 20 as compared with a general heat exchanger as in a sixth embodiment described later. It is preferable to increase the insertion length of the tube 21.

(Sixth embodiment)
FIG. 13 shows a sectional view of the heating heat exchanger 2 in the present embodiment. FIG. 13 is a view seen in the same direction as FIG.

  As shown in FIG. 13, the heating heat exchanger 2 of this embodiment is also held in the air conditioning case with the longitudinal direction of the tubes 11 and 21 being parallel to the vertical direction, as in the fourth and fifth embodiments. Has been.

  The insertion length 84 of the tube 21 inserted into the inlet side tank portion 22 of the second heater core 20 is the insertion length 85 of the tube 11 inserted into the inlet side tank portion 12 of the first heater core 10. Longer than. The insertion lengths 84 and 85 are the lengths from the inner walls of the inlet side tank portions 22 and 12 to the inlet side end portions 21a and 11a of the tubes 21 and 11, respectively. Thereby, the volume of the liquid storage part 74 formed in the area | region above the inlet side edge part 21a of the tube 21 among the inlet side tank parts 22 is enlarged.

  Further, in the present embodiment, in the positional relationship between the cooling water inlet 20a and the tube 21 in the inlet side tank portion 22 of the second heater core 20, most of the cooling water inlet 20a (shaded area in FIG. 13) is horizontal. It is in the relationship located above the imaginary line 83 passing through the inlet side end (inlet side edge) 21a of the tube drawn in parallel to. Here, most of the cooling water inlet 20a preferably has an area ratio of 35% or more, as described in the third embodiment.

  In addition, when the insertion length 84 of the tube 21 inserted in the inlet side tank part 22 of the 2nd heater core 20 is long like this embodiment, the position 20a1 of the lower end of the cooling water inlet 20a is the inlet side of the tube 21. Most preferably, it is located at the same position as or higher than the end 21a. In other words, it is most preferable that 100% of the area of the cooling water inlet 20 a overlap with the tube 21. Thus, all of the high-temperature cooling water that has flowed from the cooling water inlet 20 a can be guided to the liquid storage unit 74.

(Seventh embodiment)
In FIG. 14, the front view of the heat exchanger for a heating in this embodiment is shown. In the present embodiment, the vehicle mounting posture of the heating heat exchanger 2 shown in FIG. 12 described in the fifth embodiment is the same as that of the inlet side tank unit 22 in addition to the air inflow / outflow surface being parallel to the vertical direction. It is changed so as to incline upward in the gravity direction from the cooling water inlet 10a to the back. About another structure, it is the same as that of 5th Embodiment.

  Specifically, as shown in FIG. 14, the inlet side tank portion 22 of the second heater core 20 has a cooling water inlet 20 a at one end portion in the longitudinal direction (left-right direction) of the inlet side tank portion 22, Cooling water flows from one end of the inlet side tank portion 22 in the longitudinal direction. When the second heater core 20 is viewed from the front, the second heater core 20 has the upper wall of the inlet-side tank portion 22 with the other end in the longitudinal direction higher than the one end in the longitudinal direction of the inlet-side tank 22. It is in an inclined state so as to be positioned. At this time, the second heater core 20 has a predetermined inclination angle θ2 with an angle formed between the upper wall of the inlet side tank portion 22 of the second heater core 20 and the horizontal direction as an inclination angle θ2.

  Here, the upper wall of the inlet side tank portion 22 is a core plate in the case where the inlet side tank portion 22 has a core plate into which the tube 21 is inserted and a tank main body portion constituting the tank portion. It is. In addition, the predetermined inclination angle θ2 is the same as 1 to 1.5 degrees that is a standard die-cutting angle for die-cutting provided in the holding unit of the heat exchanger for heating the air-conditioning case at the time of resin molding of the air-conditioning case. However, it is preferable that the size be larger than that, for example, 3 degrees or more. The second heater core 20 is held in the air-conditioning case 51 and mounted on the vehicle in such a tilted state.

  In this way, by inclining the upper wall of the inlet side tank unit 22 so that the depth is higher than the cooling water inlet 20a, compared to the case where the upper wall of the inlet side tank unit 22 is horizontal, The high-temperature cooling water flowing through the liquid storage part can be transmitted to the upper wall and can be guided more easily on the far side away from the cooling water inlet 20a of the inlet side tank part 22. As a result, according to the present embodiment, the temperature difference in the left-right direction of the vehicle that occurs in the conditioned air after passing through the heating heat exchanger 2 is greater than in the fifth embodiment in which the upper wall of the inlet side tank unit 22 is horizontal. Can be reduced.

  Here, in FIG. 15, the evaluation result about the relationship between inclination-angle (theta) 2 and right and left blowing air temperature difference is shown. As can be seen from FIG. 15, when the inclination angle θ2 is in the range of 0 to 12 degrees, the left and right blown air temperature difference tends to decrease as the inclination angle θ2 increases, but in the range where the inclination angle θ2 exceeds 12 degrees, As the inclination angle θ2 increases, the left and right blown air temperature difference tends to increase. Therefore, the upper limit of the tilt angle θ2 is preferably 19.5 degrees, which is the same as the left and right blown air temperature difference (absolute value) when the tilt angle θ2 is 3 degrees.

  In the present embodiment, by tilting the entire heat exchanger 2 for heating, the angle formed between the upper wall of the inlet side tank portion 22 of the second heater core 20 and the horizontal direction is set to a predetermined inclination angle θ2. Instead of inclining the entire heat exchanger 2 for heating, the shape of the inlet side tank portion 22 of the second heater core 20 may be a shape in which the upper wall of the inlet side tank portion 22 is inclined.

  Further, the present embodiment is not limited to the fifth embodiment, and can be applied to the fourth and sixth embodiments in which the air inflow / outflow surface is parallel to the vertical direction. The present invention can also be applied to the third embodiment.

(Eighth embodiment)
In each of the above-described embodiments, a liquid storage part in which high-temperature cooling water is stored is formed inside the inlet-side tank unit 22, but in the present embodiment, cooling on the cooling-water inlet side of the inlet-side tank unit 22 is performed. It increases the flow rate of water.

  FIG. 16 shows a front view of the second heater core 20 in the present embodiment. As shown in FIG. 16, in the present embodiment, the inlet side tank unit is used as a flow rate increasing means for increasing the flow rate of the cooling water flowing into the inlet side tank unit 22 on the cooling water inlet side inside the inlet side tank unit 22. A plate-like member 92 having a flow hole 91 having a channel cross-sectional area smaller than 22 is provided.

  About the dimension of the circulation hole 91, when the diameter of the inside of the inlet side tank part 22 is 16 mm, the diameter of the circulation hole 91 shall be 5 mm or less. Thus, the diameter of the flow hole 91 is set to about 約 or less of the diameter of the inlet side tank portion 22.

  Thereby, according to this embodiment, the flow rate of the cooling water after passing through the circulation hole 91 can be made higher than the flow rate of the cooling water before passing through the circulation hole 91.

  Here, as described in the first embodiment, when the cooling water flowing into the second heater core 20 has a small flow rate, if the flow rate of the cooling water flowing through the inlet side tank portion 22 is low, the cooling is performed from the cooling water inlet to the far tube. The phenomenon that water is difficult to flow will occur.

  On the other hand, according to the present embodiment, since the flow rate of the cooling water flowing into the inlet side tank unit 22 can be increased, compared to the case where no means for increasing the flow rate of the cooling water is provided, Cooling water can flow to the depth of the inlet side tank unit 22.

  Therefore, also in this embodiment, the temperature difference in the vehicle left-right direction of the cooling water flowing through the heat exchange core portion 25 can be reduced, and the temperature difference in the vehicle left-right direction generated in the conditioned air after passing through the heat exchanger 2 for heating. Can be reduced.

  In addition, in this embodiment, although the liquid storage part demonstrated in 1st-7th embodiment is not formed, you may form a liquid storage part similarly to 1st-7th embodiment. That is, this embodiment may be combined with the first to seventh embodiments, and a higher effect can be obtained by combining.

(Ninth embodiment)
FIG. 17 shows a cross-sectional view of the heat exchanger 2 for heating in the present embodiment. FIG. 17 is a view seen in the same direction as FIG. In the present embodiment, with respect to the heat exchanger 2 for heating shown in FIG. 12 described in the fifth embodiment, the opening area of the cooling water inlet 20a of the second heater core 20 and the channel cross-sectional area of the cooling water introduction path (not shown). Is made smaller than that of the first heater core 10 to increase the flow rate of the cooling water flowing through the inlet side tank portion 22 of the second heater core 20. Here, the cooling water introduction path is a pipe connected to the cooling water inlet 20a in order to guide the cooling water to the inlet side tank section 22.

  For this reason, according to this embodiment, compared with the case where the opening area of the cooling water inlet 20a of the second heater core 20 and the cross-sectional area of the cooling water introduction path (not shown) are equal to those of the first heater core 10. The cooling water can flow to the back of the inlet side tank unit 22.

  In the present embodiment, the flow path cross-sectional area of the inlet side tank portion 22 of the second heater core 20 is smaller than the flow path cross-sectional area of the inlet side tank portion 12 of the first heater core 10. Also by this, compared with the case where the flow path cross-sectional area of the inlet side tank part 22 of the 2nd heater core 20 is equivalent to the flow path cross-sectional area of the inlet side tank part 12 of the 1st heater core 10, the 2nd heater core 20 is. The flow rate of the cooling water flowing through the inlet side tank unit 22 can be increased, and the cooling water can flow to the back of the inlet side tank unit 22.

  In the present embodiment, the flow rate of the cooling water flowing through the inlet side tank unit 22 of the second heater core 20 is increased so as to be equal to or higher than the flow rate of the cooling water flowing through the inlet side tank unit 12 of the first heater core 10. preferable.

  In the present embodiment, both the opening area of the cooling water inlet 20a of the second heater core 20 and the flow passage cross-sectional area of the cooling water introduction passage (not shown) and the flow passage cross-sectional area of the inlet side tank portion 22 of the second heater core 20 are both included. However, the flow rate of the cooling water flowing through the inlet side tank portion 22 of the second heater core 20 may be increased by only one of them. Moreover, about the structure which raises the flow rate of the cooling water which flows through the inlet side tank part 22 of the 2nd heater core 20 in this way, it is not restricted to 5th Embodiment, The heat exchanger for heating demonstrated in each other embodiment other than that. It is applicable to.

  Also in this embodiment, a part of the cooling water inlet 20a (the hatched area in FIG. 17) is drawn from two inner walls 21b at the inlet side end 21a of the tube 21 in parallel with the direction of gravity. It is located on the outer side than between the lines 81 and 82. For this reason, part of the high-temperature cooling water that has flowed from the cooling water inlet 20 a can be guided to the liquid storage unit 73.

  In the present embodiment, the cooling water can flow to the depth of the inlet side tank unit 22 by increasing the flow rate of the cooling water flowing through the inlet side tank unit 22 of the second heater core 20, and therefore the cooling water inlet 20a. May be located directly under the inlet of the tube 21.

  In the present embodiment, in addition to integrating the tank portions of the first heater core 10 and the second heater core 20, the tubes 11 and 21 of the first heater core 10 and the second heater core 20 are integrated, thereby The 1 heater core 10 and the 2nd heater core 20 are integrated. Incidentally, although the tubes 11 and 21 of the first heater core 10 and the second heater core 20 are connected to each other, the flow paths inside the tubes 11 and 21 are separately formed by the first heater core 10 and the second heater core 20. At this time, the fins of the first heater core 10 and the second heater core 20 may be separated or integrated.

(10th Embodiment)
FIG. 18A shows a side view of the heating heat exchanger 2 in the present embodiment, and FIG. 18B shows a front view of the second heater core 20 in FIG. 18A.

  In this embodiment, the structure of the heat exchanger 2 for heating is the same as that of the first embodiment, but the upper and lower sides of the heat exchanger 2 for heating are different from those of the first embodiment. That is, the inlet side tank portions 12 and 22 of the first and second heater cores 10 and 20 are positioned on the upper side, and the outlet side tank portions 13 and 23 of the first and second heater cores 10 and 20 are on the lower side. positioned. And the heat exchanger 2 for a heating is hold | maintained in the air-conditioning case in the direction where the longitudinal direction of the tubes 11 and 21 is parallel to a perpendicular direction.

  For this reason, in this embodiment, when cooling water flows into the inlet side tank part 22 of the 2nd heater core 20, as shown in FIG.18 (b), it is cooling higher than the cooling water in the outlet side tank part 23. FIG. Water is stored over the entire region in the stacking direction of the plurality of tubes 21 in the upper region 75 in the inlet side tank portion 22 due to the influence of buoyancy, and then flows into each of the plurality of tubes from the upper region 75. Then, the high-temperature cooling water flows through the plurality of tubes 21 from the top to the bottom. Thus, in the present embodiment, the upper region 75 in the inlet side tank unit 22 is a liquid storage unit.

  Therefore, according to this embodiment, the temperature difference in the vehicle left-right direction of the cooling water flowing through the heat exchange core portion 25 can be reduced, and the temperature in the vehicle left-right direction generated in the conditioned air after passing through the heat exchanger 2 for heating. The difference can be reduced.

(Eleventh embodiment)
FIG. 19 shows a side view of the heat exchanger 2 for heating in the present embodiment. In the present embodiment, the upper and lower sides of the first heater core 10 are replaced with respect to the heating heat exchanger 2 shown in FIG. 18 described in the tenth embodiment.

  Specifically, as shown in FIG. 19, the first heater core 10 and the second heater core 20 have a structure in which both the inlet side and the outlet side tank portions are integrated, so that both are integrated. Yes.

  The inside of the upper tank portion 61 located above the heating heat exchanger 2 is partitioned by the partition wall 62 into an outlet side tank portion 13 of the first heater core 10 and an inlet side tank portion 22 of the second heater core 20. Has been.

  Similarly, the inside of the lower tank portion 63 located on the lower side of the heating heat exchanger 2 is divided by a partition wall 64 into the inlet side tank portion 12 of the first heater core 10 and the outlet side tank portion 23 of the second heater core 20. It is divided into and.

  In the first heater core 10, the cooling water flowing in from the cooling water inlet 10 a provided in the lower inlet side tank portion 12 flows from the bottom to the upper side of the tube 11, and the upper outlet side tank portion. 13 flows out from a cooling water outlet 10b provided in the vehicle.

  On the other hand, in the 2nd heater core 20, the cooling water which flowed in from the cooling water inlet 20a provided in the inlet side tank part 22 located in the upper side flows through the tube 21 from the top to the bottom, and the outlet side located in the lower side It flows out from the cooling water outlet 20b provided in the tank part 23. FIG.

  Also in this embodiment, since the inlet side tank portion 22 of the second heater core 20 is located on the upper side, the same effect as in the eighth embodiment can be obtained.

  Furthermore, according to the present embodiment, the flow direction of the cooling water in the first heater core 10 is opposite to the flow direction of the cooling water in the second heater core 20, so the upper and lower sides of the air after passing through the heat exchanger 2 for heating. The temperature distribution, that is, the temperature difference between the upper side and the lower side can be reduced.

(Other embodiments)
(1) In each of the above-described embodiments, the cooling water inlet 20a provided in the inlet side tank portion 22 of the second heater core 20 is an opening formed in a wall constituting the inlet side tank portion 22. A tube may be inserted into the opening, and the tube may protrude from the inner wall of the inlet side tank unit 22 to the inside of the inlet side tank unit 22. In this case, the distal end portion of the pipe protruding inward of the inlet side tank portion 22 faces the inlet side tank portion 22 and is the end opening portion of the cooling water introduction path for introducing the cooling water into the inlet side tank portion 22. is there.

  (2) In the above-described first to seventh and ninth to eleventh embodiments, the cooling water inlet 20a of the second heater core 20 is disposed on one end side in the vehicle left-right direction of the inlet side tank portion 22, but one end side. It may be arranged not only at both ends, but also at the center. Even with such an arrangement, according to the present invention, high-temperature cooling water can be allowed to flow through the tube 21 located away from the cooling water inlet 20a.

  (3) In each of 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.

  (4) In each of the above-described embodiments, the cooling water flowing out from the first cooling water outlet 31b of the engine 30 is only the cooling water that has 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.

  (5) 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.

  (6) 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, the coolant of an electric device such as an inverter can be used as the first liquid, and the engine coolant 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. Thus, the vehicle air conditioner of the present invention can be applied to vehicles other than hybrid vehicles.

  (7) 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)
21 Tube 22 Inlet side tank part 23 Outlet side tank part 51 Air-conditioning case 71 Liquid storage part 72 Liquid storage part 73 Liquid storage part 74 Liquid storage part

Claims (13)

A heat exchanger (2) for heating that heats the air blown into the vehicle interior 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,
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). A second heat exchange section (20) for exchanging heat with the blown air,
The second heat exchange 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 side in the longitudinal direction of the plurality of tubes (21) and serves as a liquid outlet side,
The second heat exchange part (20) includes an air conditioning case (51) such that the inlet side tank part (22) is located on the lower side in the gravitational direction and the outlet side tank part (23) is located on the upper side in the gravitational direction. )
The second heat exchange part (20) is a second liquid that has flowed into the inlet side tank part (22), and a liquid having a higher temperature than the liquid in the outlet side tank part (23) After being stored in the liquid storage part (71, 72, 73, 74) in the inlet side tank part over the entire stacking direction of the tube (21), it is configured to flow into the plurality of tubes (21). A vehicle air conditioner. The second heat exchange part (20) is inclined so that an angle formed between the longitudinal direction of the tube (21) and the vertical direction becomes an acute angle when the second heat exchange part (20) is viewed from the side. In this state, it is held in the air conditioning case (51) and mounted on the vehicle,
The liquid storage part (71) is inclined from the inlet side end part (21a) of the tube (21) in the inlet side tank part (22) by the inclination of the second heat exchange part (20). The vehicle air conditioner according to claim 1, wherein the vehicle air conditioner is also formed in an upper region.   The said liquid storage part (72) is formed when a part (91) of the wall which comprises the said inlet side tank part (22) swells outside rather than another part. Or the vehicle air conditioner of 2. The first heat exchange section (10) communicates with a plurality of stacked tubes (11) and one end side in the longitudinal direction of the plurality of tubes (11), and forms an inlet side tank section (12) serving as a liquid inlet side. And an outlet side tank portion (13) that communicates with the other end side in the longitudinal direction of the plurality of tubes (11) and is a liquid outlet side,
The insertion length (84) of the tube (21) inserted into the inlet side tank part (22) of the second heat exchange part (20) is the inlet of the first heat exchange part (10). It is longer than the insertion length (85) of the tube (11) inserted in the side tank part (12),
The liquid storage part (74) is located above the inlet side end part (21a) of the tube (21) in the gravity direction in the inlet side tank part (22) of the second heat exchange part (10). The vehicle air conditioner according to any one of claims 1 to 3, wherein the vehicle air conditioner is formed in a region. A terminal opening (20a) of the liquid introduction path for introducing the second liquid into the inlet side tank part (22) of the second heat exchange part (20) is projected in the longitudinal direction of the inlet side tank part (22). When
The at least one part of the terminal opening part (20a) of the said liquid introduction path exists in the position except the right under the gravity direction of the inlet_port | entrance of the said tube (21), The one of Claim 1 thru | or 4 characterized by the above-mentioned. The vehicle air conditioner described in 1.   At least a part of the end opening (20a) of the liquid introduction path was pulled in parallel to the gravity direction from the inner wall (21b) of the tube (21) at the inlet end (21a) of the tube (21). The vehicle air conditioner according to claim 5, wherein the vehicle air conditioner is located outside the space between the two virtual lines (81, 82).   The at least part of the terminal opening (20a) of the liquid introduction path is located above an imaginary line (83) passing through the inlet side end (21a) of the tube (21). The vehicle air conditioner according to 5 or 6.   A portion of 35% or more of the total area of the terminal opening (20a) of the liquid introduction path is located at a position excluding the portion directly below the inlet of the tube (21) in the direction of gravity. The vehicle air conditioner according to any one of the above.   In the second heat exchange section (20), the second liquid flows from one end side in the longitudinal direction of the inlet side tank section (22), and the upper wall of the inlet side tank section (22) is connected to the inlet side. The tank unit (22) is held in the air conditioning case (51) and mounted on the vehicle in an inclined state so that the other end side in the longitudinal direction is located above the one end side in the longitudinal direction in the gravity direction. The vehicle air conditioner according to any one of claims 1 to 7.   A flow rate increasing means (92) for increasing the flow rate of the second liquid flowing into the inlet side tank part (22) is provided inside the inlet side tank part (22) of the second heat exchange part (20). The vehicle air conditioner according to any one of claims 1 to 9, wherein the vehicle air conditioner is provided. The first heat exchange section (10) communicates with a plurality of stacked tubes (11) and one end side in the longitudinal direction of the plurality of tubes (11), and forms an inlet side tank section (12) serving as a liquid inlet side. And an outlet side tank part (13) that communicates with the other end side in the longitudinal direction of the plurality of tubes (11) and that becomes the liquid outlet side,
The flow path cross-sectional area of the inlet side tank part (22) of the second heat exchange part (20) is smaller than the flow path cross sectional area of the inlet side tank part (12) of the first heat exchange part (10). The vehicle air conditioner according to any one of claims 1 to 10. The first heat exchange section (10) communicates with a plurality of stacked tubes (11) and one end side in the longitudinal direction of the plurality of tubes (11), and forms an inlet side tank section (12) serving as a liquid inlet side. And an outlet side tank part (13) that communicates with the other end side in the longitudinal direction of the plurality of tubes (11) and that becomes the liquid outlet side,
The cross-sectional area of the liquid introduction path for introducing the second liquid into the inlet side tank part (22) of the second heat exchange part (20) is the inlet side tank part of the first heat exchange part (10). The vehicle air conditioner according to any one of claims 1 to 11, wherein the vehicle air conditioner is smaller than a flow path cross-sectional area of a liquid introduction path for introducing the first liquid into (12). A heat exchanger (2) for heating that heats the air blown into the vehicle interior 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,
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). A second heat exchange section (20) for exchanging heat with the blown air,
The second heat exchange 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 side in the longitudinal direction of the plurality of tubes (21) and serves as a liquid outlet side,
The second heat exchange part (20) includes an air conditioning case (51) such that the inlet side tank part (22) is located on the lower side in the gravitational direction and the outlet side tank part (23) is located on the upper side in the gravitational direction. )
A vehicle air conditioner characterized in that a flow velocity increasing means (92) for increasing the flow velocity of the second liquid flowing into the inlet side tank portion (22) is provided inside the inlet side tank portion (22).

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