Patent Description:
An air conditioner mounted on a vehicle is configured to include an air conditioning unit which is called a heating, ventilating, and air conditioning (HVAC) provided in a vehicle interior.

For example, as described in PTL <NUM>, the HVAC includes a blower that sucks outside air or inside air and blows the air from an air blowing port through a duct, a first heat exchanger (evaporator) to which a refrigerant is supplied from a refrigerant system, and a second heat exchanger (heater core) to which engine cooling water, which is warm water, is supplied from a coolant system as a heat source. The evaporator cools and dehumidifies the air by causing the refrigerant and the air to exchange heat with each other. The heater core heats the air by causing the warm water and the air to exchange heat with each other. The HVAC performs temperature regulation by mixing air which has passed through the heat exchangers, and blows the air from each of air blowing ports for defrost, face, and foot.

A flow channel for flowing air which has passed through the evaporator into the heater core is set in the duct of the HVAC, and the flow rate of the air flowing in the flow channel is regulated by regulating an opening degree of an air mix damper disposed between the evaporator and the heater core. Air which has passed through only the evaporator and has a relatively low temperature and air which has passed through the evaporator and the heater core and has a relatively high temperature are mixed in a predetermined region in the duct, and is distributed to each blowing port. PTL <NUM> describes a heat exchanger in an automotive vehicle. PTL <NUM> describes a power cooling device for hybrid vehicle.

In a case where two heat exchangers are included as in the HVAC unit described in PTL <NUM>, as shown in <FIG>, a space for providing an air mix damper <NUM> and a region <NUM> which is downstream of an evaporator <NUM> and a heater core <NUM> and in which air is mixed are necessary inside the unit.

Herein, since it is necessary to introduce air from the mixing region <NUM> positioned in the vicinity of a trailing end of the duct toward each of the blowing ports for a face (FACE), defrost (DEF), and a foot (FOOT), it is difficult to supply air having an appropriate temperature to each blowing port in some cases. When the mixing region <NUM> cannot be widely secured, it is difficult to appropriately set a flow channel in which air in a different temperature range flows from the mixing region <NUM> toward each blowing port.

An object of the present invention is to provide a heat exchanger that can realize supply of air having an appropriate temperature to a plurality of blowing ports in an air conditioning unit such as an HVAC unit, and an air conditioning unit including the heat exchanger, and an air conditioner.

According to an aspect of the present invention, there is provided an air conditioning unit according to claim <NUM>.

In the air conditioning unit of the present invention, it is preferable that the low-temperature-side coolant inflow portion positioned closer to the air supply surface than the high-temperature-side coolant inflow portion in the direction D1.

In the air conditioning unit of the present invention, it is preferable that the air outflow portion includes a low-temperature-side air outflow portion through which the air having a relatively low temperature flows out and a high-temperature-side air outflow portion through which the air having a relatively high temperature flows out.

In the air conditioning unit of the present invention, it is preferable that the air conditioning unit is used in air conditioning of an interior of a vehicle, the air outflow portion includes the low-temperature-side air outflow portion, the high-temperature-side air outflow portion, and a medium temperature air outflow portion through which the air having a relatively medium temperature flows out, the low-temperature-side air outflow portion, the medium temperature air outflow portion, and the high-temperature-side air outflow portion are spaced from each other in the intersecting direction D2, the low-temperature-side air outflow portion corresponds to an air blowing port for a face, the medium temperature air outflow portion corresponds to an air blowing port for a window, and the high-temperature-side air outflow portion corresponds to an air blowing port for feet.

In the air conditioning unit of the present invention, it is preferable that the heat exchanger has a curved shape in which a part is positioned relatively on an upstream side in the direction D1 and the other part is positioned relatively on a downstream side.

In the air conditioning unit of the present invention, it is preferable that the inlet header and the outlet header communicate with a plurality of rows of the tubes arranged in the direction D1, an inside of the inlet header is divided into a low-temperature-side section into which the coolant is able to flow from the low-temperature-side coolant inflow portion and a high-temperature-side section into which the coolant is able to flow from the high-temperature-side coolant inflow portion, the low-temperature-side section communicates with the tubes in a row on an upstream side or a downstream side in the direction D1, the high-temperature-side section communicates with the tubes in the other row, and a movement of the coolant between the low-temperature-side section and the high-temperature-side section is allowed.

In addition, according to another aspect that is not part of the present invention, there is provided a heat exchanger that causes air and a coolant to exchange heat with each other, the heat exchanger including a plurality of stacked tubes each of which allows the coolant to flow therein, an inlet header that communicates with end portions of the plurality of tubes on an upstream side in a direction in which the coolant flows, an outlet header that communicates with end portions of the plurality of tubes on a downstream side in the direction in which the coolant flows, and a fin that is thermally coupled to the plurality of tubes. The inlet header includes a low-temperature-side coolant inflow portion into which the coolant having a relatively low temperature flows and a high-temperature-side coolant inflow portion into which the coolant having a relatively high temperature flows. The low-temperature-side coolant inflow portion and the high-temperature-side coolant inflow portion are shifted from each other in a direction of flow of the air passing through the heat exchanger and are shifted from each other in an intersecting direction intersecting the direction of flow of the air.

According to still another aspect of the present invention, there is provided an air conditioner including a refrigerant circuit that includes a compressor, a condenser, a decompression unit, and an evaporator, a high-temperature-side coolant circuit that includes a high-temperature-side heat exchanger which causes a coolant and a refrigerant flowing in the condenser to exchange heat with each other, a low-temperature-side coolant circuit that includes a low-temperature-side heat exchanger which causes the coolant and a refrigerant flowing in the evaporator to exchange heat with each other, a first heat exchanger to which the coolant is supplied from at least one of the high-temperature-side coolant circuit and the low-temperature-side coolant circuit, and a second heat exchanger to which the coolant is supplied from at least one of the high-temperature-side coolant circuit and the low-temperature-side coolant circuit. The first heat exchanger is the heat exchanger of the air conditioning unit described above. The coolant is able to flow from the low-temperature-side coolant circuit into the low-temperature-side coolant inflow portion. The coolant is able to flow from the high-temperature-side coolant circuit into the high-temperature-side coolant inflow portion.

It is preferable that the air conditioner of the present invention is used in air conditioning of an interior of a vehicle, and the air outflow portion of the air conditioning unit corresponds to a blowing port through which the air is blown to the interior.

In the present invention, as the low-temperature-side coolant inflow portion and the high-temperature-side coolant inflow portion, into which the coolants having relatively different temperatures flow respectively, are included in the inlet header of the heat exchanger and the coolant inflow portions are spaced from each other in the direction of flow of the air, the coolant which has flowed into the inlet header from each of the low-temperature-side coolant inflow portion and the high-temperature-side coolant inflow portion flows unevenly into a close tube from the inflow portion that the coolant has flowed in.

For this reason, since a temperature gradient in a tube stage direction is given to the coolant flowing in each tube, the same temperature gradient is given also to the air that gives and receives heat to and from the coolant which is supplied to the heat exchanger and flows in each of the tubes.

Then, air in a temperature range suitable for each supply destination can be easily and reliably distributed to a plurality of supply destinations, to which temperature-controlled air is to be supplied, from a region adjacent to a downstream side of the heat exchanger by causing air having an appropriate temperature to flow out through the air outflow portion which can be selected for an appropriate position.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.

An air conditioning unit <NUM> and a heat exchanger <NUM> configuring the air conditioning unit <NUM> will be described with reference to <FIG>. The air conditioning unit <NUM> and the heat exchanger <NUM> can be used, for example, in air conditioning of the interior of a vehicle as will be described below. An air conditioner <NUM> (<FIG>) including the air conditioning unit <NUM> is mounted on, for example, the vehicle. The air conditioning unit <NUM> is provided in a vehicle interior In (<FIG>).

The air conditioning unit <NUM> shown in <FIG> can configure the air conditioner <NUM> shown in <FIG>. First, after describing the air conditioning unit <NUM>, the air conditioner <NUM> will be described.

The air conditioning unit <NUM> (<FIG>) includes the heat exchanger <NUM> (first heat exchanger) that causes air and a coolant to exchange heat with each other, a blower <NUM> that supplies air to the heat exchanger <NUM>, an air outflow portion <NUM> (<NUM> to <NUM>) through which air, which has passed through the heat exchanger <NUM>, flows out from the air conditioning unit <NUM>, and a duct <NUM> in which the heat exchanger <NUM> is disposed. The duct <NUM> also serves as a casing of the air conditioning unit <NUM>.

One heat exchanger <NUM> included in the air conditioning unit <NUM> is sufficient. Unlike an HVAC unit in an example of the related art shown in <FIG> including two heat exchangers (<NUM> and <NUM>), the air conditioning unit <NUM> includes only one heat exchanger <NUM>. The air conditioning unit <NUM> does not include elements corresponding to an air mix damper <NUM> and a mixing region <NUM> included in the HVAC unit shown in <FIG>.

The air conditioning unit <NUM> is a so-called heating, ventilation, and air conditioning (HVAC), and has functions of cooling, heating, dehumidifying, and ventilating of the vehicle interior. The air conditioning unit <NUM> can be provided inside an interior panel such as a vehicle instrument panel. As for a posture in which the air conditioning unit <NUM> is provided, for example, an upper side and a lower side of <FIG> correspond to an upper side and a lower side of the air conditioning unit <NUM> in a vertical direction, a left side of <FIG> corresponds to a front side in a vehicle traveling direction, and a right side of <FIG> corresponds to a rear side in the vehicle traveling direction. However, without being limited thereto, the air conditioning unit <NUM> can be provided in an appropriate posture.

The air conditioning unit <NUM> supplies air sucked by the blower <NUM> to the heat exchanger <NUM>, and causes the air, of which a temperature is regulated by passing through the heat exchanger <NUM>, to flow out from the air outflow portion <NUM>. In <FIG>, the flow of air from the blower <NUM> to the air outflow portion <NUM> is schematically shown with solid arrows. The air flowed out from the air outflow portion <NUM> passes through a flow channel (not shown) to a plurality of blowing ports <NUM> to <NUM> (<FIG>) provided in the interior panel, and is blown out to the vehicle interior.

The blowing ports <NUM> to <NUM> (<FIG>) are, for example, the blowing port <NUM> for a face, through which air blows out toward the face of an occupant, the blowing port <NUM> for a window, through which air blows out toward a window of the vehicle, and the blowing port <NUM> for feet, through which air blows out toward the feet of the occupant. It is preferable that positions where the blowing ports <NUM> to <NUM> are provided in the panel of the vehicle interior are determined such that temperature-controlled air is efficiently supplied toward a supply destination such as the face, the window, and the feet.

With the air conditioning unit <NUM>, air having an appropriate temperature can be supplied to each supply destination through each of the blowing ports <NUM> to <NUM>. When an appropriate temperature of air blown out from the blowing port <NUM> for a face is set as T1, an appropriate temperature of air blown out from the blowing port <NUM> for a window is set as T2, and an appropriate temperature of air blown out from the blowing port <NUM> for feet is set as T3, a relative relationship therebetween is typically T1 < T2 < T3. In light of keeping the head cool and the feet warm, which is regarded preferable for performing air conditioning, T1 < T3 is satisfied.

By being rotationally driven by a drive force of a motor (not shown), the blower <NUM> sucks air outside the vehicle (outside air) or air in the vehicle (inside air) from a suction portion 11A (<FIG>) according to the selection of an outside air/inside air mode of the air conditioning unit <NUM>. The air sucked by the blower <NUM> is discharged from a discharge portion 11B (<FIG>) into the duct <NUM>, and is supplied to the heat exchanger <NUM>.

By causing air supplied from the blower <NUM> and a coolant supplied from a coolant circuit CL shown in <FIG> to exchange heat with each other, the heat exchanger <NUM> (<FIG>) obtains temperature-controlled air.

As will be described later, a high-temperature-side coolant and a low-temperature-side coolant are obtained through heat exchange with a refrigerant circulating in a refrigerant circuit <NUM> (<FIG>) that is a heat pump cycle, which compresses the refrigerant and transports the refrigerant to a heat load with outside air as a heat source, and the refrigerant is supplied to the heat exchanger <NUM>.

The coolant is, for example, a liquid for a heat medium such as pure water and brine, and water that cools an engine mounted on the vehicle can be used as the coolant.

As shown in <FIG> and <FIG>, the heat exchanger <NUM> includes a plurality of stacked flat tubes <NUM>, a plurality of fins <NUM>, an inlet header <NUM>, and an outlet header <NUM>.

Inside each of the tubes <NUM>, a coolant flows. Each of the tubes <NUM> extends parallel to each other from an upstream end portion 21A on an upstream side, in which the coolant flows, to a downstream end portion 21B on a downstream side. Each of the tubes <NUM> extends in a direction orthogonal to the page of <FIG>.

The tubes <NUM> can be formed by extrusion molding and roll molding using, for example, metallic materials excellent in thermal conductivity, such as copper, a copper alloy, aluminum, and an aluminum alloy. The fins <NUM> and the headers <NUM> and <NUM> can also be molded through an appropriate method using the same metallic materials as the tubes <NUM>.

The fins <NUM> are thermally coupled to the tubes <NUM>, are formed in a shape appropriate for increasing a heat transfer area between air and a coolant, and are assembled with the tubes <NUM>. The fins <NUM> may be, for example, a corrugated type which is formed in a wavy shape and in which the fins are stacked alternately with the tubes <NUM>, or may be a plate type in which the fins are disposed orthogonally to each of the stacked tubes <NUM>.

A heat exchange core 20C having first to nth stages is configured by n tubes <NUM> and the plurality of fins <NUM> assembled with the tubes <NUM>. Air is supplied in a direction D1 intersecting a direction D3 (<FIG>), in which a coolant flows in the tubes <NUM>, to an air supply surface 20A of the heat exchange core 20C by the blower <NUM>. The air supplied to the air supply surface 20A exchanges heat with the coolant flowing in the tubes <NUM> while passing through a gap between the fins <NUM>.

The direction D1 in which the air supplied to the heat exchanger <NUM> passes through the heat exchanger <NUM> will be called the air flow direction D1, and the direction D3 in which the coolant flows in the tubes <NUM> will be called the coolant flow direction D3.

The inlet header <NUM> and the outlet header <NUM> extend in a direction (D2) in which the tubes <NUM> are stacked.

A coolant flows into each of the stacked tubes <NUM> through the inlet header <NUM>, and the coolant flowing in each of the tubes <NUM> flows out to the coolant circuit CL (<FIG>) through the outlet header <NUM>.

The inlet header <NUM> includes a space communicating with the upstream end portion 21A of each of the first stage tube <NUM> to the nth stage tube <NUM>. An opening into which the upstream end portion 21A of each of the tubes <NUM> is inserted is formed in the inlet header <NUM>.

The outlet header <NUM> includes a space communicating with the downstream end portion 21B of each of the first stage tube <NUM> to the nth stage tube <NUM>. An opening into which the downstream end portion 21B of each of the tubes <NUM> is inserted is formed in the outlet header <NUM>.

The tubes <NUM>, the fins <NUM>, the inlet header <NUM>, and the outlet header <NUM> are bonded to each other, for example, through brazing.

The heat exchanger <NUM> of the present embodiment has a shape curved with respect to the air flow direction D1, in which air passes through the heat exchanger <NUM>, as a whole. Specifically, the heat exchange core 20C has a shape of which a central portion in a direction of each of the first to nth stages (stacking direction) is curved in a direction of being convex downstream in the direction of flow of air with respect to both end portions. The inlet header <NUM> and the outlet header <NUM> also have a shape curved in the same direction.

As the heat exchanger <NUM> is curved, the heat exchanger <NUM> can be comfortably disposed inside the duct <NUM> under the restriction of a space allowed in the vehicle for providing the air conditioning unit <NUM>. The heat exchanger <NUM> may be curved in an opposite direction to the direction shown in <FIG> in order to avoid other in-vehicle devices.

However, the heat exchanger <NUM> is not necessarily curved.

The heat exchanger <NUM> has a main feature in coolant inflow portions <NUM> and <NUM> (<FIG>) through which a coolant can flow into the inlet header <NUM>.

The inlet header <NUM> includes the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM>, which correspond to coolants having temperatures different from each other, respectively. A coolant flows into the inlet header <NUM> through at least one of the coolant inflow portions <NUM> and <NUM>.

A coolant LC (low-temperature-side coolant) that has a relatively low temperature can flow into the low-temperature-side coolant inflow portion <NUM> from a low-temperature-side coolant circuit <NUM> to be described later. A coolant HC (high-temperature-side coolant) that has a relatively high temperature can flow into the high-temperature-side coolant inflow portion <NUM> from a high-temperature-side coolant circuit <NUM> to be described later, independently of the low-temperature-side coolant inflow portion <NUM>.

The coolant which has flowed into the inlet header <NUM> from at least one of the coolant inflow portions <NUM> and <NUM> flows in each of the tubes <NUM>, flows into the outlet header <NUM>, and flows out from a coolant outflow portion <NUM> provided in the outlet header <NUM> to the coolant circuit CL.

For example, as schematically shown in <FIG>, the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM> are spaced from each other in the air flow direction D1 and are spaced from each other in the intersecting direction D2 intersecting the air flow direction D1. Based on the shifts in the positions of the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM>, a temperature gradient in the intersecting direction D2 is given to air that is supplied to the heat exchanger <NUM> by the blower <NUM> and has exchanged heat with a coolant flowing in the tubes <NUM>. This will be described later.

The intersecting direction D2 intersects both of the air flow direction D1 and the coolant flow direction D3.

As for the shift in the air flow direction D1, it is preferable that the low-temperature-side coolant inflow portion <NUM> is shifted on to upstream side in the air flow direction D1 from the high-temperature-side coolant inflow portion <NUM> in order to dehumidify air.

The air outflow portion <NUM> (<FIG>) corresponds to an opening provided in a wall of the duct <NUM> in which air flows. A temperature gradient in the intersecting direction D2 intersecting the air flow direction D1 is given to air supplied to the heat exchanger <NUM> as passing through the heat exchanger <NUM>. For this reason, it is possible to cause air having a temperature suitable for each of the blowing ports <NUM> to <NUM> to flow out from a position of a temperature range suitable for each of the blowing ports <NUM> to <NUM> in a region <NUM> (<FIG>), which is adjacent to a downstream side of the heat exchanger <NUM> and extends in the intersecting direction D2, toward each of the blowing ports <NUM> to <NUM>.

Air, which has passed through the heat exchanger <NUM> and is in a relatively different temperature range, flows out through the air outflow portion <NUM> toward each of the blowing port <NUM> for a face, the blowing port <NUM> for a window, and the blowing port <NUM> for feet.

The air outflow portion <NUM> is formed by the plurality of air outflow portions <NUM> to <NUM> individually corresponding to the plurality of blowing ports <NUM> to <NUM>. Specifically, the air outflow portion <NUM> is formed by the low-temperature-side air outflow portion <NUM> through which air having a relatively low temperature flows out, the medium temperature air outflow portion <NUM> through which air having a relatively medium temperature flows out, and the high-temperature-side air outflow portion <NUM> through which air having a relatively high temperature flows out. The air outflow portions <NUM> to <NUM> are openings independent of each other, and are provided in the duct <NUM> by selecting a position where air having a temperature suitable for a corresponding blowing port is to be taken out from the region <NUM>. The air outflow portions <NUM> to <NUM> may not necessarily be independent of each other, or the air outflow portions at positions close to each other are allowed to be integrated as one opening.

A blowing port corresponding to each of the air outflow portions <NUM> to <NUM> can be determined as appropriate in consideration of keeping the head cool and the feet warm.

In the present embodiment, the low-temperature-side air outflow portion <NUM> corresponds to the blowing port <NUM> for a face, the medium temperature air outflow portion <NUM> corresponds to the blowing port <NUM> for a window, and the high-temperature-side air outflow portion <NUM> corresponds to the blowing port <NUM> for feet.

Since the temperature of a side of the heat exchanger <NUM>, which is close to the blowing port <NUM> for a face, can be made relatively low and the temperature of a side of the heat exchanger <NUM>, which is close to the blowing port <NUM> for feet, can be made relatively high according to a posture in which the heat exchanger <NUM> is provided and the positions of the air outflow portions <NUM> to <NUM> in the present embodiment, the occupant's comfort can be improved by keeping the head cool and the feet warm.

The blowing port corresponding to each of the air outflow portions <NUM> to <NUM> is not limited to the present embodiment.

In the example shown in <FIG>, the high-temperature-side air outflow portion <NUM> is positioned on a most upstream side of flow of air toward a trailing end 13A of the duct <NUM> from the heat exchanger <NUM>, and the low-temperature-side air outflow portion <NUM> is positioned on a most downstream side. The medium temperature air outflow portion <NUM> through which air in a medium temperature range, which is between temperature ranges of air flowed out through the low-temperature-side air outflow portion <NUM> and the high-temperature-side air outflow portion <NUM> respectively, flows out is positioned between the high-temperature-side air outflow portion <NUM> and the low-temperature-side air outflow portion <NUM>.

It is preferable to appropriately determine the position of each of the air outflow portions <NUM> to <NUM> according to the shape of the duct <NUM> or the heat exchanger <NUM> and the position of the heat exchanger <NUM> in the duct <NUM>.

The size and direction of the opening of each of the air outflow portions <NUM> to <NUM> can be appropriately determined such that air flows smoothly to a corresponding blowing port while preventing a pressure loss.

The workings of the air conditioning unit <NUM> will be described based on the configuration of the heat exchanger <NUM> (<FIG>).

The coolant LC having a relatively low temperature flows into the inlet header <NUM> of the heat exchanger <NUM> from the low-temperature-side coolant inflow portion <NUM>, and the coolant HC having a relatively high temperature flows into the inlet header from the high-temperature-side coolant inflow portion <NUM>.

As described above, since the positions of the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM> are spaced from each other in the direction of flow of air D1 and are spaced from each other also in the intersecting direction D2, a coolant which has flowed into the inlet header <NUM> from each of the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM> flows unevenly into a close tube <NUM> from the inflow portion <NUM> or <NUM> that the coolant has flowed in.

For example, as shown in <FIG>, since the low-temperature-side coolant inflow portion <NUM> is positioned on the upstream side in the air flow direction D1 and one side (upper side of <FIG>) in the intersecting direction D2, the coolant LC which has flowed in from the low-temperature-side coolant inflow portion <NUM> mainly flows into the tube <NUM> disposed on a first stage side among the stacked tubes <NUM>.

On the other hand, since the high-temperature-side coolant inflow portion <NUM> is positioned on a downstream side in the air flow direction D1 and the other side (lower side of <FIG>) in the intersecting direction D2 contrary to the low-temperature-side coolant inflow portion <NUM>, the coolant HC which has flowed in from the high-temperature-side coolant inflow portion <NUM> mainly flows into the tube <NUM> disposed on an nth stage side among the stacked tubes <NUM>.

A temperature gradient in a stage direction is given to a coolant flowing in each of the tubes <NUM> in the coolant flow direction D3. For this reason, the same temperature gradient is given also to air that is supplied to the heat exchanger <NUM> by the blower <NUM> and gives and receives heat to and from the coolant flowing in each of the tubes <NUM>.

<FIG> shows that a temperature gradient existing in a coolant flowing in the tube <NUM> of each stage in the heat exchanger <NUM> is in a pattern different for each temperature range. A relationship as to which temperature ranges B1, B2, B3, B4, and B5 are higher or lower is B1 < B2 < B3 < B4 < B5. Since such a temperature gradient is given to air that gives and receives heat to and from the coolant while passing through the heat exchanger <NUM>, flow F of air that has immediately passed through the heat exchanger <NUM> from the first to nth stages also has the same temperature gradient as the temperature gradient shown in <FIG>.

As described above, in the present embodiment, a direction in which the coolant inflow portions <NUM> and <NUM> are spaced from each other is set such that the low-temperature-side coolant inflow portion <NUM> is positioned on the upstream side in the air flow direction D1 with respect to the high-temperature-side coolant inflow portion <NUM>. For this reason, as shown in <FIG>, when flowing into the heat exchanger <NUM>, a large amount of air supplied to the heat exchanger <NUM> passes through the temperature ranges B1 and B2 in which the temperature of a coolant is relatively low. After a dew point temperature is lowered as the air is sufficiently cooled by exchanging heat with the coolant in the temperature ranges B1 and B2 and the air is efficiently dehumidified, air, of which a temperature is increased as the air passes through the temperature ranges B3 to B5 in which the temperature of a coolant is higher, is supplied to a supply destination. For this reason, it is possible to contribute to prevention of fogging of a window and improvement of comfort in the vehicle interior.

Although the heat exchanger <NUM> is shown in a shape simplified into a rectangular shape in <FIG>, the same temperature gradient as shown in <FIG> is given to air, which has passed through the heat exchanger <NUM>, even when the heat exchanger <NUM> is curved as shown in <FIG> and <FIG>, based on the fact that the positions of the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM> are spaced from each other.

The heat exchanger <NUM> may actually be formed in a rectangular shape.

As described above, when the low-temperature-side coolant inflow portion <NUM> and the high-temperature-side coolant inflow portion <NUM> are spaced from each other in the air flow direction D1 and the intersecting direction D2, a temperature gradient is given to the region <NUM> adjacent to the downstream side of the heat exchanger <NUM>. The air temperature is distributed in the stage direction from the first to nth stages, that is, in the region <NUM> over a wide range in the intersecting direction D2.

For example, as shown in <FIG>, in the HVAC unit including the two heat exchangers (<NUM> and <NUM>), it is difficult to expand the mixing region <NUM> positioned in the vicinity of a trailing end of a duct due to the restriction of the volume of the unit. When it is required to distribute air in different temperature ranges obtained by mixing of air that has passed through only the heat exchanger <NUM> and air that has passed through both of the heat exchangers <NUM> and <NUM> to each blowing port from such a mixing region <NUM>, it is difficult to distribute air having an appropriate temperature to each blowing port in some cases.

On the contrary, air in a temperature range suitable for each supply destination can be easily and reliably distributed to a plurality of supply destinations, to which temperature-controlled air is to be supplied, from the region <NUM> of the present embodiment by selecting an appropriate position and causing air in an appropriate temperature to flow out through the air outflow portion <NUM> (<NUM> to <NUM>) provided in the duct <NUM>.

In addition, since a blowing port for feet positioned in a lower part of the vehicle interior is far from the mixing region <NUM> positioned at an upper end of the HVAC unit in the configuration shown in <FIG>, it is difficult to secure a flow channel corresponding to an air amount necessary for the blowing port in some cases.

On the contrary, in a case where, in accordance with an up-and-down direction of the page of <FIG>, the heat exchanger <NUM> is disposed to extend in the up-and-down direction in general as in the present embodiment, the high-temperature-side air outflow portion <NUM> is positioned at a lowermost position among the air outflow portions <NUM> to <NUM>, and is close to the position of the blowing port <NUM> for feet, which is usually positioned in the lower part of the vehicle interior. For this reason, a sufficient amount of air can be supplied from the high-temperature-side air outflow portion <NUM> to the blowing port <NUM> for feet while preventing a pressure loss.

Next, an example of a configuration of the air conditioner <NUM> including the air conditioning unit <NUM> will be described with reference to <FIG>. In the air conditioner <NUM>, as will be described below, functions of cooling and heating can be performed with only one heat exchanger <NUM> given to the air conditioning unit <NUM> as a low-temperature-side coolant (for example, chilled water) and a high-temperature-side coolant (for example, warm water) are suppliable to the heat exchanger <NUM> of the air conditioning unit <NUM>.

In the air conditioner <NUM>, each of a condenser <NUM> and an evaporator <NUM> of a steam compression refrigerating cycle exchanges heat with a coolant. As shown in <FIG>, the air conditioner <NUM> includes the refrigerant circuit <NUM>, the coolant circuit CL that includes the high-temperature-side coolant circuit <NUM> and the low-temperature-side coolant circuit <NUM>, the air conditioning unit <NUM> described above, a vehicle exterior heat exchanger CL1 (second heat exchanger), a fan CL2, and a controller <NUM> that controls an operation of the air conditioner <NUM>. In addition, the air conditioner <NUM> is provided with a first regulating valve V1, a second regulating valve V2, a third regulating valve V3, a first electromagnetic valve SV1, and a second electromagnetic valve SV2. The valves are controlled by the controller <NUM>.

The high-temperature-side coolant circuit <NUM> sends a coolant having a high temperature, which has exchanged heat with a high temperature refrigerant through the condenser <NUM>, and regulates the distribution of the flow rate of a coolant to be sent to each of the vehicle exterior heat exchanger CL1 and the heat exchanger <NUM> (vehicle interior heat exchanger) of the air conditioning unit <NUM> through the first regulating valve V1 according to an air conditioning load.

The low-temperature-side coolant circuit <NUM> sends a coolant having a low temperature, which has exchanged heat with a low temperature refrigerant through the evaporator <NUM>, and regulates the distribution of the flow rate of a coolant to be sent to each of the vehicle exterior heat exchanger CL1 and the heat exchanger <NUM> through the second regulating valve V2 according to an air conditioning load.

The air conditioner <NUM> has a configuration described below in order to realize the functions described above.

As shown in <FIG>, the refrigerant circuit <NUM> is provided in a vehicle exterior Out.

The refrigerant circuit <NUM> includes a compressor <NUM> that compresses a refrigerant, the condenser <NUM> that is a heat exchanger which performs heat exchange between a high temperature and high pressure gas refrigerant compressed by the compressor <NUM> and a high-temperature-side coolant flowing in the high-temperature-side coolant circuit <NUM>, a liquid receiver <NUM>, an expansion valve <NUM> that is a decompression unit which decompresses a refrigerant flowing out from the liquid receiver <NUM>, and the evaporator <NUM> that is a heat exchanger which performs heat exchange between the refrigerant decompressed by the expansion valve <NUM> and a low-temperature-side coolant flowing in the low-temperature-side coolant circuit <NUM>.

The high temperature and high pressure gas refrigerant exchanges heat with the high-temperature-side coolant and is condensed by the condenser <NUM>. At this time, since the gas refrigerant releases condensation heat, the temperature of the high-temperature-side coolant used in cooling rises. The state of the refrigerant changes from a gas to a liquid due to condensation, and becomes a high temperature and high pressure liquid. The liquid refrigerant flows into the liquid receiver <NUM>.

Since the expansion valve <NUM> releases a refrigerant after restricting the flow of a high temperature and high pressure liquid refrigerant, the pressure of the refrigerant drops sharply. For this reason, a refrigerant in the evaporator <NUM> easily evaporates. In the evaporator <NUM>, the refrigerant evaporates by taking away evaporation heat from a low-temperature-side coolant. For this reason, the temperature of the low-temperature-side coolant decreases. The low temperature and low pressure gas refrigerant which has passed through the evaporator <NUM> flows into the compressor <NUM>, and is compressed into a high temperature and high pressure gas refrigerant. A refrigerating cycle is repeated from each of processes including condensation by the condenser <NUM>, decompression by the expansion valve <NUM>, and evaporation by the evaporator <NUM>, in addition to the compression of the gas refrigerant.

The high-temperature-side coolant circuit <NUM> includes a high-temperature-side heat exchanger <NUM> that is provided side by side with the condenser <NUM> of the refrigerant circuit <NUM> and performs heat exchange between a refrigerant flowing in the condenser <NUM> and a high-temperature-side coolant and a high-temperature-side circulation pump <NUM> that circulates the high-temperature-side coolant.

The first regulating valve V1 regulates the flow of a high-temperature-side coolant to any one or both of the heat exchanger <NUM> and the vehicle exterior heat exchanger CL1. The first regulating valve V1 can be configured by a so-called three-way valve, and can regulate the distribution of the high-temperature-side coolant flowing in the heat exchanger <NUM> and the vehicle exterior heat exchanger CL1. The regulating valve can regulate the flow rate.

The third regulating valve V3 regulates the flow of a coolant flowed out from the heat exchanger <NUM> to any one or both of the high-temperature-side coolant circuit <NUM> and the low-temperature-side coolant circuit <NUM>.

The first electromagnetic valve SV1 and the second electromagnetic valve SV2 selectively cause any one of a high-temperature-side coolant and a low-temperature-side coolant to flow into the vehicle exterior heat exchanger CL1.

The first electromagnetic valve SV1 allows or prevents the coolant from the vehicle exterior heat exchanger CL1 from flowing into the high-temperature-side heat exchanger <NUM> via an exhaust heat collector <NUM>.

The second electromagnetic valve SV2 allows or prevents the coolant from the vehicle exterior heat exchanger CL1 from flowing into an exhaust heat collector <NUM>.

The high-temperature-side circulation pump <NUM> has one end connected to a downstream side of the high-temperature-side heat exchanger <NUM> and the other end provided on a flow channel of a pipe LH1 connected to the first regulating valve V1. The downstream side is based on a direction in which a high-temperature-side coolant flows in the high-temperature-side heat exchanger <NUM>.

One end of a pipe LH2 and one end of a pipe LH3 are connected to the first regulating valve V1. The other end of the pipe LH2 is connected to the vehicle exterior heat exchanger CL1 via a connection pipe <NUM>. The other end of the pipe LH3 is connected to the inlet header <NUM> (<FIG>) of the heat exchanger <NUM> via a connection pipe <NUM>.

One end of a pipe LH6 is connected to an upstream side of the high-temperature-side heat exchanger <NUM>, and a confluence point C3 is provided at the other end of the pipe LH6. One end of a pipe LH4 and one end of a pipe LH5 are connected to the confluence point C3. The other end of the pipe LH4 is connected to the vehicle exterior heat exchanger CL1 via a connection pipe <NUM>, and is also connected to a pipe LL2 of the low-temperature-side coolant circuit <NUM>. The first electromagnetic valve SV1 described above is provided on a flow channel of the pipe LH4. The other end of the pipe LH5 is connected to the third regulating valve V3. The third regulating valve V3 is connected to the outlet header <NUM> (<FIG>) of the heat exchanger <NUM> via a connection pipe <NUM>.

In <FIG>, arrows shown in the pipes LH1 to LH6 indicate a direction in which a high-temperature-side coolant flows. Although the direction in which the high-temperature-side coolant flows is shown for all of the pipes LH1 to LH6 in <FIG>, there also is a pipe in which the high-temperature-side coolant does not flow, among the pipes LH1 to LH6, depending on an operation mode of the air conditioner <NUM>. The same applies to pipes LL1 to LL6 to be described later.

The low-temperature-side coolant circuit <NUM> includes a low-temperature-side heat exchanger <NUM> that is provided side by side with the evaporator <NUM> of the refrigerant circuit <NUM> and performs heat exchange between a refrigerant flowing in the evaporator <NUM> and a low-temperature-side coolant, a low-temperature-side circulation pump <NUM> that circulates the low-temperature-side coolant, and the exhaust heat collectors <NUM> and <NUM> that collect heat from air discharged from the vehicle interior In to the outside.

Instead of the exhaust heat collectors <NUM> and <NUM>, a heat exchanger or an electric heater that collects vehicle device exhaust heat or ventilation exhaust heat can also be provided.

The second regulating valve V2 regulates the flow of a low-temperature-side coolant to any one or both of the heat exchanger <NUM> and the vehicle exterior heat exchanger CL1. The second regulating valve V2 can be configured by a so-called three-way valve, and can regulate the distribution of the low-temperature-side coolant flowing in the heat exchanger <NUM> and the vehicle exterior heat exchanger CL1.

The low-temperature-side circulation pump <NUM> has one end connected to a downstream side of the low-temperature-side heat exchanger <NUM> and the other end provided on a flow channel of the pipe LL1 connected to the second regulating valve V2.

One end of the pipe LL2 and one end of the pipe LL3 are connected to the second regulating valve V2. The exhaust heat collector <NUM> and the first electromagnetic valve SV1 are provided on a flow channel of the pipe LL2. The other end of the pipe LL2 is connected to the vehicle exterior heat exchanger CL1 via the connection pipe <NUM>. The other end of the pipe LL3 is connected to the heat exchanger <NUM> via a connection pipe <NUM>.

One end of the pipe LL6 is connected to an upstream side of the low-temperature-side heat exchanger <NUM>, and a confluence point C5 is provided at the other end of the pipe LL6. One end of the pipe LL4 and one end of the pipe LL5 are connected to the confluence point C5. The other end of the pipe LL4 is connected to the third regulating valve V3. In addition, the other end of the pipe LL5 is connected to the vehicle exterior heat exchanger CL1 via the connection pipe <NUM>, and is also connected to the pipe LH2 of the high-temperature-side coolant circuit <NUM>. The exhaust heat collector <NUM> and the second electromagnetic valve SV2 are provided on a flow channel of the pipe LL5.

While the air conditioner <NUM> is operating, the high-temperature-side heat exchanger <NUM> continuously performs heat exchange between a high temperature and high pressure gas refrigerant and a high-temperature-side coolant, and the low-temperature-side heat exchanger <NUM> continuously performs heat exchange between a refrigerant decompressed by the expansion valve <NUM> and a low-temperature-side coolant.

The air conditioner <NUM> realizes a plurality of operation modes by distributing the high-temperature-side coolant and the low-temperature-side coolant to the heat exchanger <NUM> and the vehicle exterior heat exchanger CL1.

An operation of the air conditioner <NUM> for each operation mode will be described with reference to <FIG>.

The air conditioner <NUM> of the present embodiment operates in any one of four modes including the pure cooling mode shown in <FIG>, the mild cooling mode shown in <FIG>, a mild heating and dehumidified heating mode shown in <FIG>, and a pure heating mode shown in <FIG>.

As shown in <FIG>, in the pure cooling mode, only a low-temperature-side coolant is sent to the heat exchanger <NUM> by the low-temperature-side coolant circuit <NUM>, and a high-temperature-side coolant flowing in the high-temperature-side coolant circuit <NUM> circulates between the high-temperature-side heat exchanger <NUM> and the vehicle exterior heat exchanger CL1.

In order to realize the pure cooling mode, the first regulating valve V1, the third regulating valve V3, the second regulating valve V2, the first electromagnetic valve SV1, and the second electromagnetic valve SV2 are controlled as follows.

ON means that a flow channel is open, and OFF means that the flow channel is closed.

In <FIG>, a flow channel section where a coolant does not flow as the valve is turned off is shown by a broken line.

In the pure cooling mode, a high-temperature-side coolant circulates in the high-temperature-side heat exchanger <NUM>, the high-temperature-side circulation pump <NUM>, the first regulating valve V1, and the vehicle exterior heat exchanger CL1 in this order. That is, the high-temperature-side coolant is not sent to the heat exchanger <NUM>, and circulates in the closed high-temperature-side coolant circuit <NUM>.

In the pure cooling mode, a low-temperature-side coolant circulates in the low-temperature-side heat exchanger <NUM>, the low-temperature-side circulation pump <NUM>, the second regulating valve V2, the heat exchanger <NUM>, and the third regulating valve V3 in this order. The low-temperature-side coolant is not sent to the vehicle exterior heat exchanger CL1.

As described above, in the pure cooling mode, only the low-temperature-side coolant is sent to the heat exchanger <NUM>, and the cooling of the vehicle interior In is realized.

As shown in <FIG>, in the mild cooling mode in which the degree of cooling is lower than in the pure cooling mode, the low-temperature-side coolant circuit <NUM> sends a low-temperature-side coolant to the heat exchanger <NUM>, and the high-temperature-side coolant circuit <NUM> sends some of a high-temperature-side coolant to the heat exchanger <NUM> and sends the remaining high-temperature-side coolant to the vehicle exterior heat exchanger CL1.

In order to realize the mild cooling mode, the first regulating valve V1, the third regulating valve V3, the second regulating valve V2, the first electromagnetic valve SV1, and the second electromagnetic valve SV2 are controlled as follows.

Since the flow rate of a coolant is appropriately distributed according to an air conditioning load, turning on the first regulating valve V1 and the third regulating valve V3 means a predetermined opening degree is given.

In the mild cooling mode, a high-temperature-side coolant circulates in the high-temperature-side heat exchanger <NUM>, the high-temperature-side circulation pump <NUM>, the first regulating valve V1, the heat exchanger <NUM>, and the third regulating valve V3 in this order, and circulates in the high-temperature-side heat exchanger <NUM>, the high-temperature-side circulation pump <NUM>, the first regulating valve V1, and the vehicle exterior heat exchanger CL1 in this order.

In the mild cooling mode, a low-temperature-side coolant circulates in the same manner as in the pure cooling mode.

As shown in <FIG>, in the mild heating and dehumidified heating mode, the high-temperature-side coolant circuit <NUM> sends a high-temperature-side coolant to the heat exchanger <NUM>, sends some of a low-temperature-side coolant flowing in the low-temperature-side coolant circuit <NUM> to the heat exchanger <NUM>, and sends the remaining low-temperature-side coolant to the vehicle exterior heat exchanger CL1.

Also in the mild heating and dehumidified heating mode, both of a low-temperature-side coolant and a high-temperature-side coolant are supplied to the heat exchanger <NUM> as in the mild cooling mode. However, in the mild heating and dehumidified heating mode, the flow rate of the low-temperature-side coolant supplied to the heat exchanger <NUM> is low compared to the mild cooling mode, and conversely, the flow rate of the high-temperature-side coolant is high. In the mild heating and dehumidified heating mode, the degree of heating is lower than in the pure heating mode (<FIG>) in which the low-temperature-side coolant is not supplied to the heat exchanger <NUM>.

In order to realize the mild heating and dehumidified heating mode, the first regulating valve V1, the third regulating valve V3, the second regulating valve V2, the first electromagnetic valve SV1, and the second electromagnetic valve SV2 are controlled as follows.

Since the flow rate of a coolant is appropriately distributed according to an air conditioning load, turning on the second regulating valve V2 and the third regulating valve V3 means a predetermined opening degree is given.

In the mild heating and dehumidified heating mode, a high-temperature-side coolant circulates in the high-temperature-side heat exchanger <NUM>, the high-temperature-side circulation pump <NUM>, the first regulating valve V1, the heat exchanger <NUM>, and the third regulating valve V3 in this order.

In the mild heating and dehumidified heating mode, a low-temperature-side coolant circulates in the low-temperature-side heat exchanger <NUM>, the low-temperature-side circulation pump <NUM>, the second regulating valve V2, the heat exchanger <NUM>, and the third regulating valve V3 in this order, and circulates in the low-temperature-side heat exchanger <NUM>, the low-temperature-side circulation pump <NUM>, the second regulating valve V2, the exhaust heat collector <NUM>, the vehicle exterior heat exchanger CL1, and the exhaust heat collector <NUM> in this order.

As shown in <FIG>, in the pure heating mode, only a high-temperature-side coolant is sent to the heat exchanger <NUM> by the high-temperature-side coolant circuit <NUM>, and a low-temperature-side coolant flowing in the low-temperature-side coolant circuit <NUM> circulates between the low-temperature-side heat exchanger <NUM> and the vehicle exterior heat exchanger CL1.

In order to realize the pure heating mode, the first regulating valve V1, the third regulating valve V3, the second regulating valve V2, the first electromagnetic valve SV1, and the second electromagnetic valve SV2 are controlled as follows.

In the pure heating mode, a high-temperature-side coolant circulates in the high-temperature-side heat exchanger <NUM>, the high-temperature-side circulation pump <NUM>, the first regulating valve V1, the heat exchanger <NUM>, and the third regulating valve V3 in this order.

In the pure heating mode, a low-temperature-side coolant circulates in the low-temperature-side heat exchanger <NUM>, the low-temperature-side circulation pump <NUM>, the second regulating valve V2, the exhaust heat collector <NUM>, the vehicle exterior heat exchanger CL1, and the exhaust heat collector <NUM> in this order.

As described above, in the pure heating mode, only the high-temperature-side coolant is sent to the heat exchanger <NUM>, and the heating of the vehicle interior In is realized.

In the air conditioner <NUM> of the present embodiment, one or both of a high-temperature-side coolant heated as exchanging heat with a refrigerant in the refrigerant circuit <NUM> by means of the high-temperature-side coolant circuit <NUM> and a low-temperature-side coolant cooled as exchanging heat with the refrigerant in the refrigerant circuit <NUM> by means of the low-temperature-side coolant circuit <NUM> are supplied to the heat exchanger <NUM>. The air conditioner <NUM> can perform cooling and heating as described above even when only one heat exchanger <NUM> is provided in the air conditioning unit <NUM>.

That is, since the air conditioner <NUM> has functions of heating and cooling and can reduce the number of the air conditioning units <NUM> necessary for the heat exchanger <NUM> to one, the air conditioning unit <NUM> can be miniaturized. As is clear from comparing the air conditioning unit <NUM> shown in <FIG> to the HVAC unit shown in <FIG>, the volume of the air conditioning unit <NUM> is smaller than the volume of the HVAC unit including the two heat exchangers (<NUM> and <NUM>) by a region indicated with a shaded pattern in <FIG>.

In addition, since the air conditioner <NUM> has only one heat exchanger <NUM>, it is not necessary to include the air mix damper (<NUM> of <FIG>). Accordingly, the following effects are obtained.

Wind noise generated when the opening degree of the air mix damper is particularly small can be eliminated.

In addition, a driving source such as a motor that drives the air mix damper is not necessary, and a moving portion in the air conditioning unit <NUM> can be eliminated by eliminating the air mix damper. For this reason, the weight and cost of the air conditioning unit <NUM> can be reduced, and reliability can be improved.

When there is only one heat exchanger <NUM> and the air mix damper is eliminated, a large cross sectional area of the flow channel for air in the duct <NUM> can be secured. For this reason, since a flow speed can be decreased under constant air flow rate, noise can be reduced.

Further, since a pressure loss of air flowing in the duct <NUM> is reduced as there is only one heat exchanger <NUM> included in the air conditioning unit <NUM>, power input to the blower <NUM> can be reduced.

In addition, since a direction in which a refrigerant flows in the refrigerant circuit <NUM> is constant, it is not necessary to provide the air conditioner <NUM> with a flow channel switching valve such as a four-way valve. Therefore, a decrease in air conditioning performance, which is attributable to a refrigerant pressure loss caused by the flow channel switching valve, and the generation of refrigerant flowing noise when passing through the valve can be avoided.

In addition, since the refrigerant circuit <NUM> is provided in the vehicle exterior Out, the air conditioner <NUM> has a low risk of a refrigerant leaking to the vehicle interior In. Therefore, a heating capacity can be increased by using a refrigerant (R454C) having considerable combustibility and a high pressure refrigerant such as CO<NUM> without necessarily preventing a refrigerant leak by increasing the size of a device configuring the refrigerant circuit <NUM>.

In addition, since a risk of combustion at the time of a refrigerant leak can be decreased by using water as a coolant, in this respect, it is possible to use a refrigerant having combustibility.

Since the temperature of a refrigerant flowing in the evaporator <NUM> is made lower than an outside air temperature to absorb heat from outside air at the time of heating, an evaporation temperature (low pressure) of the evaporator <NUM> depends on the outside air temperature. The temperature of a low-temperature-side coolant that exchanges heat with a refrigerant by means of the low-temperature-side heat exchanger <NUM> and is supplied to the heat exchanger <NUM> used in dehumidifying also corresponds to the evaporation temperature.

However, in the air conditioner <NUM>, even under a frost generation condition in which a refrigerant temperature falls below <NUM> since the outside air temperature is low, the temperature of the low-temperature-side coolant flowing in the heat exchanger <NUM> can be maintained at <NUM> or higher through mixing between the low-temperature-side coolant and a high-temperature-side coolant in the coolant circuit CL. For this reason, heating performance can be maintained by preventing frost on the heat exchanger <NUM>.

Each operation mode of the air conditioner <NUM>, which is described above, is merely an example, and is not limited to the description above.

For example, it is allowed that a small amount of high-temperature-side coolant is also supplied to the inlet header <NUM> of the heat exchanger <NUM> while a low-temperature-side coolant is supplied in the pure cooling mode, and a small amount of low-temperature-side coolant is also supplied to the inlet header <NUM> of the heat exchanger <NUM> while the high-temperature-side coolant is supplied in the pure heating mode. In this case, also in the pure cooling mode and the pure heating mode, a temperature gradient can be given to air which has passed through the heat exchanger <NUM>, and keeping the head cool and the feet warm can be achieved.

Next, a heat exchanger <NUM> according to a second embodiment of the present invention will be described with reference to <FIG>. Hereinafter, points different from the first embodiment will be mainly described.

As shown in <FIG>, the heat exchanger <NUM> according to the second embodiment includes a plurality of rows (<NUM> and <NUM>) of the tubes <NUM> arranged in the air flow direction D1, the fins <NUM> appropriately provided on the tubes <NUM>, an inlet header <NUM>, and the outlet header <NUM>.

Like the heat exchanger <NUM> of the first embodiment, the heat exchanger <NUM> can configure, for example, the air conditioner <NUM> shown in <FIG>.

A heat exchange core disposed on the upstream side in the air flow direction D1 will be called an upwind row <NUM>, and a heat exchange core disposed on the downstream side in the air flow direction D1 will be called a downwind row <NUM>.

The upwind row <NUM> is formed by the plurality of tubes <NUM> stacked in the intersecting direction D2 intersecting the air flow direction D1 and the plurality of fins <NUM>. The same applies to the downwind row <NUM>.

The heat exchanger <NUM> of the first embodiment described above may be configured to include the upwind row <NUM> and the downwind row <NUM>.

The number of the tubes <NUM> in the upwind row <NUM> and the number of the tubes <NUM> in the downwind row <NUM> are the same n, the tubes <NUM> in the upwind row <NUM> and the tubes <NUM> in the downwind row <NUM> which are at the same stage of the first to nth stages are disposed at the same position in the intersecting direction D2.

However, without being limited to the present embodiment, the number of the tubes <NUM> may be different between the upwind row <NUM> and the downwind row <NUM>, and the positions of the tubes <NUM> in the upwind row <NUM> and the downwind row <NUM> which are at the same stage may be shifted from each other in the intersecting direction D2.

The inside of the inlet header <NUM> communicates with all of the tubes <NUM> in the upwind row <NUM> and all of the tubes <NUM> in the downwind row <NUM>. The same applies also to the inside of the outlet header <NUM>.

The second embodiment has a main feature that the inside of the inlet header <NUM> is divided into a low-temperature-side section A1 into which a low-temperature-side coolant can flow from the low-temperature-side coolant inflow portion <NUM> and a high-temperature-side section A2 into which a high-temperature-side coolant can flow from the high-temperature-side coolant inflow portion <NUM>.

In the example shown in <FIG>, the inside of the inlet header <NUM> is divided into the low-temperature-side section A1 and the high-temperature-side section A2 by a panel-shaped partition member <NUM> disposed along the stage direction.

In the second embodiment, the low-temperature-side coolant inflow portion <NUM> is shifted to the upstream side (upwind side) in the air flow direction D1 with respect to the high-temperature-side coolant inflow portion <NUM> as in the first embodiment. For this reason, the low-temperature-side section A1 into which a low-temperature-side coolant can flow is positioned on the upstream side (upwind side) in the air flow direction D1 inside the inlet header <NUM>, and the high-temperature-side section A2 into which a high-temperature-side coolant can flow is positioned on the downstream side (downwind side) in the air flow direction D1 inside the inlet header <NUM>.

For this reason, the low-temperature-side section A1 communicates with the tubes <NUM> in the upwind row <NUM>, and the high-temperature-side section A2 communicates with the tubes <NUM> in the downwind row <NUM>.

As shown in <FIG>, in a state where a movement of a coolant between the low-temperature-side section A1 and the high-temperature-side section A2 through a gap <NUM> is allowed, the inside of the inlet header <NUM> is divided into the low-temperature-side section A1 and the high-temperature-side section A2. That is, the inside of the inlet header <NUM> is not completely partitioned.

For this reason, the partition member <NUM> is disposed inside the inlet header <NUM> with the gap <NUM> between an end edge thereof and an inner wall of the inlet header <NUM>.

<FIG> schematically shows a temperature gradient of a coolant flowing in each of the tubes <NUM> of the heat exchanger <NUM> of the second embodiment.

The coolant LC which has flowed from the low-temperature-side coolant inflow portion <NUM> into the low-temperature-side section A1 mainly flows into the tubes <NUM> disposed particularly on the first stage side of the upwind row <NUM>.

On the other hand, the coolant HC which has flowed from the high-temperature-side coolant inflow portion <NUM> into the high-temperature-side section A2 mainly flows into the tubes <NUM> disposed particularly on the nth stage side of the downwind row <NUM>.

In the second embodiment, a temperature difference between the upwind side and the downwind side is emphasized in a temperature gradient given to the coolant flowing in each of the tubes <NUM>.

Therefore, in the second embodiment, in addition to the effects described in the first embodiment, a capacity of dehumidifying air in the vehicle interior can be improved and fogging of a window can be sufficiently prevented since a low-temperature-side coolant is easily distributed to the tubes <NUM> on the upwind side.

Even in a case where a coolant is supplied only to the low-temperature-side section A1 as in the pure cooling mode or the coolant is supplied only to the high-temperature-side section A2 as in the pure heating mode by allowing the movement of the coolant between the low-temperature-side section A1 and the high-temperature-side section A2, the coolant flows into both of the low-temperature-side section A1 and high-temperature-side section A2, and the coolant flows also to any one of the tubes <NUM> in the upwind row <NUM> and the downwind row <NUM> through the gap <NUM>. For this reason, all of the tubes <NUM> included in the heat exchanger <NUM> can contribute to heat exchange.

The configuration for dividing into the low-temperature-side section A1 and the high-temperature-side section A2 while allowing the movement of a coolant is not limited to the present embodiment. For example, instead of providing the gap <NUM> between the end edge of the partition member <NUM> and an inner wall of the inlet header <NUM>, the partition member may have a hole through which the coolant can enter and exit.

Alternatively, the inlet header <NUM> is formed by two separate tubular bodies, and the tubular bodies may be configured to communicate with each other via a passage through which the coolant passes.

The heat exchanger <NUM> may include the tubes <NUM> arranged in three or more rows. In this case, for example, the tubes <NUM> in a first row positioned on the upwind side communicate with the low-temperature-side section A1, and the remaining tubes <NUM> in a second row and a third row communicate with the high-temperature-side section A2.

The heat exchanger, the air conditioning unit, and the air conditioner of the present invention are not limited for use in vehicles, and can also be applied to air conditioning of buildings.

Although the air conditioning unit <NUM> includes the three air outflow portions <NUM> to <NUM> in the embodiments, the air conditioning unit of the present invention may include only two air outflow portions.

In this case, for example, the two air outflow portions may correspond to the blowing port for a face and the blowing port for a window, may correspond to the blowing port for a window and the blowing port for feet, or may correspond to the blowing port for a face and the blowing port for feet.

Claim 1:
An air conditioning unit (<NUM>) comprising:
a heat exchanger (<NUM>) that causes air and a coolant to exchange heat with each other;
a blower (<NUM>) that supplies the air to the heat exchanger (<NUM>); and
an air outflow portion (<NUM>) through which the air, which has passed through the heat exchanger (<NUM>), flows out from the air conditioning unit (<NUM>),
wherein the heat exchanger (<NUM>) includes
a plurality of stacked tubes (<NUM>) each of which allows the coolant to flow therein in a direction (D3), the tubes being stacked in a direction (D2) intersecting the direction (D3),
an air supply surface (20A) intended to receive from the blower (<NUM>) a flow of air that will pass through the heat exchanger (<NUM>),
an inlet header (<NUM>) that communicates with end portions of the plurality of tubes (<NUM>) on an upstream side in the direction (D3) in which the coolant flows,
an outlet header (<NUM>) that communicates with end portions of the plurality of tubes (<NUM>) on a downstream side in the direction (D3) in which the coolant flows, and
a fin (<NUM>) that is thermally coupled to the plurality of tubes (<NUM>),
the air conditioning unit (<NUM>) being characterized in that:
the inlet header (<NUM>) includes a low-temperature-side coolant inflow portion (<NUM>) into which the coolant having a relatively low temperature is able to flow and a high-temperature-side coolant inflow portion (<NUM>) into which the coolant having a relatively high temperature is able to flow, and
the low-temperature-side coolant inflow portion (<NUM>) and the high-temperature-side coolant inflow portion (<NUM>) are spaced from each other in a direction (D1) that intersects both directions (D2) and (D3) such that the low-temperature-side coolant inflow portion (<NUM>) and the high-temperature-side coolant inflow portion (<NUM>) are at different positions from the air supply surface (20A) in the direction (D1), the low-temperature-side coolant inflow portion (<NUM>) and the high-temperature-side coolant inflow portion (<NUM>) being also spaced from each other in the intersecting direction (D2).