WO2023198860A1

WO2023198860A1 - Vehicular air conditioner

Info

Publication number: WO2023198860A1
Application number: PCT/EP2023/059729
Authority: WO
Inventors: Naoto Hayashi
Original assignee: Valeo Systemes Thermiques
Priority date: 2022-04-14
Filing date: 2023-04-13
Publication date: 2023-10-19

Abstract

Vehicular air conditioner comprising a downstream driven door (83) having a plate shape being connected to an extended tip end of a downstream extension door (81) of a butterfly-type mix door (60) via a downstream hinge (82), wherein the downstream extension door (81) and the downstream driven door (83) close a warm air passage (50) when the butterfly-type mix door (60) is at a full-cool position, a downstream door diameter (R2) from a rotation shaft (62) of the butterfly-type mix door (60) to a tip end of the downstream driven door (83) is variable and the downstream door diameter (R2) is larger when the butterfly-type mix door (60) is at the full-cool position than that when the butterfly-type mix door (60) is at a full-hot position.

Description

DESCRIPTION

Title of Invention: VEHICULAR AIR CONDITIONER

Technical Field [0001]

The present invention relates to a vehicular air conditioner including a butterfly-type mix door.

Background Art [0002]

Many vehicles such as passenger vehicles include a vehicular air conditioner for conditioning a temperature by taking in outside air or inside air into a vehicle interior. PTL 1 discloses a vehicular air conditioner in the related art. [0003]

The vehicular air conditioner disclosed in PTL 1 includes a case in which air flows, a cooling heat exchanger capable of cooling the air flowing through the case, and a heater capable of heating the air flowing out from the cooling heat exchanger. [0004]

Further, in the case, a warm air passage through which the air flowing out from the heater flows, a cool air passage through which the air flowing out from the cooling heat exchanger flows without being heated by the heater, a mix door capable of adjusting a ratio of the air flowing through the warm air passage to the air flowing through the cool air passage, and a mix space in which the air flowing through the warm air passage and the air flowing through the cool air passage merge are formed.

[0005]

The mix door includes a rotation shaft, an extension door extending from the rotation shaft to a radially outer side of the rotation shaft, and a driven door connected to a tip end of the extension door via a hinge. When the rotation shaft rotates, positions of the extension door and the driven door change, the ratio of the air in the warm air passage flowing into the mix space to the air in the cool air passage flowing into the mix space changes, and a temperature of conditioned air conditioned in the mix space can be changed. The conditioned air is discharged into the vehicle interior through a duct or the like.

Citation List

Patent Literature

[0006]

PTL 1: JP2009-090730 A Summary of Invention

Technical Problem

[0007]

At a full-cool position at which a ratio of cool air flowing through the cool air passage is the largest, the mix door is located in a manner of closing an inlet of the heater. The heater is located below the rotation shaft of the mix door. Therefore, at the full-cool position, the extension door of the mix door extends obliquely downward from the rotation shaft, and the driven door extends substantially vertically downward from the tip end of the extension door.

[0008]

In addition to a weight of the mix door, a dynamic pressure of cool air flowing in a substantially horizontal direction from the cooling heat exchanger is also applied to the mix door at the full-cool position. In order to move the mix door, a torque for rotating the rotation shaft against the weight of the mix door and the dynamic pressure of the cool air is required. It is desirable that the torque of the rotation shaft when the mix door is moved from the full-cool position can be reduced.

[0009]

An object of the invention is to provide a vehicular air conditioner capable of rotating a rotation shaft of a mix door with a small torque.

Solution to Problem

[0010]

In the following description, reference signs in the accompanying drawings are appended in parentheses to facilitate understanding of the invention, but the invention is not limited to the illustrated embodiment. [0011]

The invention provides a vehicular air conditioner (10) including: a case (20) in which air flows; a cooling heat exchanger (13) capable of cooling the air flowing through the case (20) ; a heater (31) capable of heating the air flowing out from the cooling heat exchanger (13) ; a warm air passage (50) through which the air flowing out from the heater (31) flows; a cool air passage (40) through which the air flowing out from the cooling heat exchanger (13) flows without being heated by the heater (31) ; a mix door (60) capable of adjusting a ratio of the air flowing through the warm air passage (50) to the air flowing through the cool air passage (40) ; and a mix space (27) in which the air flowing through the warm air passage (50) and the air flowing through the cool air passage (40) merge, in which the mix door (60) includes a butterfly door portion (61) including a rotation shaft (62) substantially orthogonal to a flow direction of the air flowing through the cool air passage (40) , an upstream extension door (71) extending from the rotation shaft (62) and being movable upstream of the rotation shaft (62) , and a downstream extension door (81) extending from the rotation shaft (62) in a direction substantially opposite to a direction in which the upstream extension door (71) extends, in the mix door (60) , the upstream extension door (71) and the downstream extension door (81) swing about the rotation shaft (62) , and the mix door (60) is capable of being located at a full-cool position at which a ratio of the air flowing through the warm air passage (50) is minimized, a full-hot position at which the ratio of the air flowing through the warm air passage (50) is maximized, and a temperature conditioning position at which neither the ratio of the air flowing through the warm air passage (50) nor a ratio of the air flowing through the cool air passage (40) is maximized, an upstream driven door (73) having a plate shape is connected to an extended tip end of the upstream extension door (71) via an upstream hinge (72) , a downstream driven door (83) having a plate shape is connected to an extended tip end of the downstream extension door (81) via a downstream hinge (82) the downstream extension door (81) and the downstream driven door (83) close the warm air passage (50) when the mix door (60) is at the full-cool position, a downstream door diameter (R2) from the rotation shaft (62) to a tip end of the downstream driven door (83) is variable, and the downstream door diameter (R2) is larger when the mix door (60) is at the full-cool position than that when the mix door (60) is at the full-hot position.

Advantageous Effects of Invention

[0012]

The mix door (60) includes the downstream extension door (81) extending in a direction opposite to the direction in which the upstream extension door (71) extends, and the downstream driven door (83) connected to the downstream extension door (81) via the downstream hinge (82) . The downstream door diameter (R2) is the largest when the mix door (60) is at the full-cool position. That is, a downstream door (80) has a linear shape when the mix door (60) is at the full-cool position. A torque due to a weight of the downstream door (80) can be increased. This torque can weaken a torque for maintaining the full-cool position by an upstream door 70, and can reduce a torque when the mix door (60) starts to move from the full-cool position toward the full-hot position. The rotation shaft (62) of the mix door (60) can be rotated with a small torque.

Brief Description of Drawings

[0013]

[FIG. 1] FIG. 1 is a perspective view of a vehicular air conditioner according to an embodiment.

[FIG. 2] FIG. 2 is a schematic cross-sectional view of the vehicular air conditioner illustrated in FIG. 1.

[FIG. 3] FIG. 3 is a view (a portion surrounded by a line 3 in FIG. 2) illustrating a configuration of a mix door at a temperature conditioning position (between a full-hot position and a boundary point) and an air flow.

[FIG. 4A] FIG. 4A is a view illustrating the mix door at a full-cool position.

[FIG. 4B] FIG. 4B is a view illustrating the mix door at the temperature conditioning position.

[FIG. 4G] FIG. 4G is a view illustrating the mix door at a full-hot position.

[FIG. 5] FIG. 5 is a graph illustrating a relationship between a position of the mix door and a downstream door diameter .

[FIG. 6] FIG. 6 is a view illustrating the configuration of the mix door at the temperature conditioning position (between the full-cool position and the boundary point) and the air flow.

[FIG. 7] FIG. 7 is a view illustrating the configuration of the mix door at the full-hot position and the air flow.

[FIG. 8] FIG. 8 is a view illustrating the configuration of the mix door at the full-cool position and the air flow.

[FIG. 9] FIG. 9 is a view illustrating a function of the vehicular air conditioner according to the embodiment.

Description of Embodiments

[0014]

An embodiment will be described below with reference to the accompanying drawings. In the drawings, Fr indicates a front side, Rr indicates a rear side, L indicates a left side with an occupant in a vehicle interior as a reference, R indicates a right side with the occupant in the vehicle interior as the reference, Up indicates an upper side, and Dn indicates a lower side. Further, "upstream" and "downstream" in the following description are set with a flow direction of air as a reference.

[0015]

FIG. 1 illustrates a vehicular air conditioner 10 that adjusts a temperature by taking in outside air or inside air into a vehicle interior. The vehicular air conditioner 10 is mounted on, for example, a passenger vehicle, and extends in a left-right direction at the front part of the vehicle interior.

[0016]

The vehicular air conditioner 10 includes an air blower 11 that blows inhaled air, and a temperature regulator 12 that regulates a temperature of air blown from the air blower 11 and blows out conditioned air into the vehicle interior. [0017]

An electric motor and an impeller driven by the electric motor are provided in the air blower 11. When the impeller rotates, air inside and/or outside the vehicle interior is inhaled into the air blower 11. [0018]

The temperature regulator 12 includes a case 20 in which the air blown from the air blower 11 flows. Openings 21 to 23 opened for blowing out the conditioned air are formed in the case 20. [0019]

The openings 21 to 23 include a defroster opening 21 for blowing the conditioned air toward a windshield to remove fog on the windshield, vent openings 22 for blowing the conditioned air toward an upper body of an occupant on a front seat, and foot openings 23 and 23 for blowing the conditioned air toward feet of the occupant on the front seat .

[0020]

FIG. 2 is a cross-sectional view of the temperature regulator 12. FIGS. 1 and 2 are referred to in combination. The defroster opening 21 can be opened and closed by an opening and closing member 17. The vent openings 22 can be opened and closed by an opening and closing member 18. The foot openings 23 and 23 can be opened and closed by opening and closing members 19 and 19. [0021]

The case 20 of the temperature regulator 12 includes an intake portion 24 that is open to take in the air blown from the air blower 11 into the case 20.

[0022]

The case 20 accommodates a cooling heat exchanger 13 capable of cooling the air flowing out from the intake portion 24. Gaps between the cooling heat exchanger 13 and the case 20 are preferably filled with sealing materials 14 and 14. [0023] [Heater]

The case 20 accommodates a heater 31 capable of heating the air flowing out from the cooling heat exchanger 13. The heater 31 is located vertically below a rotation shaft 62 to be described later. The heater 31 includes an inflow surface 32 into which cool air flows, and an outflow surface 33 from which warm air flows out that is the cool air flowing in from the inflow surface 32 and heated inside the heater 31.

[0024]

A support portion 25 that supports an upper end portion of the heater 31 is provided in the case 20. A gap between the support portion 25 and the upper end portion of the heater 31 is preferably filled with a sealing material. A gap between a lower end portion of the heater 31 and the case 20 is preferably filled with a sealing material. The heater 31 may be any of a heater that generates heat by electric power, a heater through which warm water flows, and a heater through which a high- temperature refrigerant flows. [0025] [Warm Air Passage, Cool Air Passage, and Mix Space]

In the case 20, a warm air passage 50 through which the air flowing out from the heater 31 flows, a cool air passage 40 through which the air flowing out from the cooling heat exchanger 13 flows in a cool-air state without being heated by the heater 31, and a mix space 27 in which the air flowing through the warm air passage 50 and the air flowing through the cool air passage 40 merge are formed.

[0026]

[Mix Door]

Reference is made to FIG. 3. A mix door 60 capable of adjusting a ratio of the air flowing through the warm air passage 50 to the air flowing through the cool air passage 40 is provided in the case 20.

[0027]

[Butterfly Door Portion]

The mix door 60 includes a butterfly door portion 61 including two plate-shaped doors 71 and 81 capable of swinging about a rotation shaft 62. [0028] [Rotation Shaft, Upstream Extension Door, and Downstream Extension Door]

Specifically, the butterfly door portion 61 includes the rotation shaft 62 whose axis extends in a direction substantially orthogonal to a flow direction of the air flowing through the cool air passage 40, the upstream extension door 71 extending from the rotation shaft 62 and being movable upstream of the rotation shaft 62, and the downstream extension door 81 extending from the rotation shaft 62 in a direction substantially opposite to a direction in which the upstream extension door 71 extends.

[0029] [Upstream Hinge and Upstream Driven Door]

An upstream driven door 73 having a plate shape is connected to the upstream extension door 71 via an upstream hinge 72. The upstream driven door 73 is preferably provided at an extended tip end of the upstream extension door 71 or in the vicinity of the extended tip end of the upstream extension door 71.

[0030]

[Upstream Sealing Members]

Each door has a rectangular shape. An upstream intermediate sealing member 77 is provided at an edge of the upstream extension door 71. An upstream tip end sealing member 78 is provided at an edge of the upstream driven door 73.

[0031]

[Upstream Door Diameter and Upstream Door Angle]

The upstream driven door 73 can swing about the upstream hinge 72 with respect to the upstream extension door 71. An upstream groove 91 capable of guiding swinging of the upstream driven door 73 is formed on side wall surfaces 90 and 90 (see also FIG. 1) of the case 20. An upstream pin 74 that is slidable with respect to the upstream groove 91 is attached to the vicinity of a tip end of the upstream driven door 73. By appropriately changing a shape and a position of the upstream groove 91, a trajectory of the upstream driven door 73 can be appropriately changed.

[0032]

When the rotation shaft 62 rotates, an upstream door diameter R1 from the rotation shaft 62 to the upstream tip end sealing member 78 of the upstream driven door 73 varies. An upstream door angle 01 formed by the upstream driven door 73 and the upstream extension door 71 is also variable. The upstream door angle 01 is always 180 degrees or less. Hereinafter, the upstream extension door 71, the upstream hinge 72, and the upstream driven door 73 are collectively referred to as an upstream door 70. [0033] [Downstream Hinge and Downstream Driven Door]

A downstream driven door 83 having a plate shape is connected to the downstream extension door 81 via a downstream hinge 82. The downstream driven door 83 is preferably provided at an extended tip end of the downstream extension door 81 or in the vicinity of the extended tip end of the downstream extension door 81. [0034] [Downstream Sealing Members]

A downstream intermediate sealing member 87 is provided at an edge of the downstream extension door 81. A downstream tip end sealing member 88 is provided at an edge of the downstream driven door 83.

[0035]

[Downstream Door Diameter and Downstream Door Angle]

The downstream driven door 83 can swing about the downstream hinge 82 with respect to the downstream extension door 81. A downstream groove 92 capable of guiding swinging of the downstream driven door 83 is formed on the side wall surfaces 90 and 90 of the case 20. A downstream pin 84 that is slidable with respect to the downstream groove 92 is attached to the vicinity of a tip end of the downstream driven door 83. By appropriately changing a shape and a position of the downstream groove 92, a trajectory of the downstream driven door 83 can be appropriately changed. [0036]

When the rotation shaft 62 rotates, a downstream door diameter R2 from the rotation shaft 62 to the downstream tip end sealing member 88 of the downstream driven door 83 varies. A downstream door angle 02 formed by the downstream driven door 83 and the downstream extension door 81 is also variable. The downstream door angle 02 is always 180 degrees or less. Hereinafter, the downstream extension door 81, the downstream hinge 82, and the downstream driven door 83 are collectively referred to as a downstream door 80. [0037]

[Details of Cool Air Passage]

The cool air passage 40 includes an upstream cool air passage 41 between the cooling heat exchanger 13 and a swing range of the upstream door 70, a mix space side cool air passage 42 in which cool air flowing from the upstream cool air passage 41 is branched by the upstream door 70 and flows toward the mix space 27, and a heater-side cool air passage 43 through which the cool air flowing from the upstream cool air passage 41 is branched by the upstream door 70 and flows toward the heater 31.

[0038]

A block portion 25a is provided between the rotation shaft 62 and the support portion 25 to reduce or prevent a part of the cool air flowing into the heater-side cool air passage 43 from bypassing the heater 31 and flowing into the warm air passage 50. The block portion 25a is a plateshaped portion integrated with the support portion 25 and extending from the support portion 25 to the rotation shaft 62. A tip end of the block portion 25a is located in the vicinity of the rotation shaft 62, and substantially prevents the cool air flowing into the heater-side cool air passage 43 from flowing into the warm air passage 50.

[0039]

[Position of Mix Door] When the rotation shaft 62 is rotated, the upstream door 70 and the downstream door 80 swing about the rotation shaft 62, thereby changing a position of the mix door 60. [0040] [Full-cool Position]

FIG. 4A illustrates the mix door 60 located at a fullcool position at which a ratio of the air flowing through the warm air passage 50 is minimized. [0041] [Temperature Conditioning Position]

FIG. 4B illustrates the mix door 60 located at a temperature conditioning position at which neither the ratio of the air flowing through the warm air passage 50 nor a ratio of the air flowing through the cool air passage 40 is maximized. [0042] [Full-hot Position]

FIG. 40 illustrates the mix door 60 located at a full- hot position at which the ratio of the air flowing through the warm air passage 50 is maximized. [0043] [Swinging of Downstream Driven Door]

Reference is made to FIG. 3 and FIGS. 4A to 40. As the mix door 60 moves from the full-cool position (FIG. 4A) to the full-hot position (FIG. 40) , both the downstream door angle 02 and the downstream door diameter R2 decrease. In other words, as the mix door 60 moves from the full-cool position to the full-hot position, the downstream driven door 83 swings toward downstream (a direction close to the mix space 27) of the downstream extension door 81 in the warm air passage 50 (the downstream door angle 02 gradually decreases) .

[0044]

[Change Rate of Downstream Door Diameter]

FIG. 5 is a graph illustrating a relationship between the position of the mix door 60 and the downstream door diameter R2. When the mix door 60 is at the full-cool position, the downstream door diameter R2 is maximized. As the mix door 60 moves from the full-cool position to the full-hot position, the downstream door diameter R2 decreases. When the mix door 60 is at the full-hot position, the downstream door diameter R2 is minimized. [0045]

A change amount of the downstream door diameter R2 with respect to a movement amount (magnitude of an angle by which the rotation shaft 62 rotates) of the mix door 60 is defined as a downstream door diameter change rate C. The downstream door diameter change rate C has different characteristics with a boundary point B between the fullcool position and the full-hot position as a boundary. In the downstream door diameter change rate C, a change rate from the full-cool position to the boundary point B is defined as a full-cool side change rate Cl, and a change rate from the boundary point B to the full-hot position is defined as a full-hot side change rate C2. The full-cool side change rate Cl is set to be smaller than the full-hot side change rate C2.

[0046]

Reference is made to FIGS. 3 and 5. The downstream groove 92 is formed such that the downstream driven door 83 swings based on the downstream door diameter change rate C. Specifically, the downstream groove 92 includes a fullcool side groove 92a corresponding to a portion from the full-cool position to the boundary point B, and a full-hot side groove 92b corresponding to a portion from the boundary point B to the full-hot position.

[0047]

Reference is made to FIG. 6. Similarly to FIG. 3, the mix door 60 is at the temperature conditioning position. The downstream pin 84 is located on the full-cool side groove 92a (between the full-cool position and the boundary point B) . As illustrated in the graph in FIG. 5, the fullcool side change rate Cl is set to be smaller than the full-hot side change rate C2. Therefore, when the downstream pin 84 slides on the full-cool side groove 92a from the full-cool position toward the boundary point B, the downstream door diameter R2 is less likely to be smaller than that when the downstream pin 84 slides on the full- hot side groove 92b.

[0048]

[Swinging of Upstream Driven Door]

Reference is made to FIG. 3 and FIGS. 4A to 4G. As the mix door 60 moves from the full-cool position (FIG. 4A) to the full-hot position (FIG. 4G) , both the upstream door angle 01 and the upstream door diameter R1 decrease. In other words, as the mix door 60 moves from the full-cool position to the full-hot position, the upstream driven door 73 swings toward downstream (a direction close to the heater 31) of the upstream extension door 71 in the heater-side cool air passage 43 (the upstream door angle 01 gradually decreases) .

[0049] [Configuration of Mix Door at Temperature Conditioning Position and Air Flow]

Reference is made to FIG. 3. At the temperature conditioning position, the upstream intermediate sealing member 77 is separated from a wall surface 20a at a downstream end of the mix space side cool air passage 42. That is, the downstream end of the mix space side cool air passage 42 is open. Cool air Cl can flow into the mix space 27 from the mix space side cool air passage 42. [0050]

The upstream tip end sealing member 78 is separated from a wall surface 20b at an upstream end of the heaterside cool air passage 43. That is, the upstream end of the heater-side cool air passage 43 is open. Cool air C2 can flow from the upstream cool air passage 41 into the heaterside cool air passage 43. The cool air C2 flows into the heater 31 from the inflow surface 32 of the heater 31. [0051]

The cool air C2 flows out from the outflow surface 33 of the heater 31 as warm air Hl and flows into the warm air passage 50.

[0052]

The downstream tip end sealing member 88 is separated from a wall surface 20c at a downstream end of the warm air passage 50. That is, the downstream end of the warm air passage 50 is open. The warm air Hl flows into the mix space 27 from the warm air passage 50. [0053]

In this manner, when the mix door 60 is at the temperature conditioning position, a part of the air flowing out from the cooling heat exchanger 13 flows through the cool air passage 40 as the cool air Cl, and at the same time, another part of the air flows through the warm air passage 50 as the warm air Hl. Therefore, when the mix door 60 is at the temperature conditioning position, neither the ratio of the air flowing through the warm air passage 50 nor the ratio of the air flowing through the cool air passage 40 is maximized.

[0054] [Configuration of Mix Door at Full-hot Position and Air Flow]

Reference is made to FIG. 7. At the full-hot position, the upstream door 70 is in a most bent state. The upstream door diameter R1 (FIG. 3) is the smallest, and the upstream door angle 01 (FIG. 3) is the smallest. [0055]

The upstream intermediate sealing member 77 is in close contact with the wall surface 20a at the downstream end of the mix space side cool air passage 42. That is, the downstream end of the mix space side cool air passage 42 is closed. The upstream tip end sealing member 78 is separated from the wall surface 20b at the upstream end of the heater-side cool air passage 43. That is, the upstream end of the heater-side cool air passage 43 is open. Cool air C3 flows into the heater-side cool air passage 43 from the upstream cool air passage 41.

[0056]

At the full-hot position, the downstream door 80 is in a most bent state. The downstream door diameter R2 (FIG. 3) is the smallest, and the downstream door angle 02 (FIG. 3) is the smallest. [0057]

The cool air C3 flows through the heater-side cool air passage 43 and flows into the heater 31 from the inflow surface 32 of the heater 31. The cool air C3 heated by the heater 31 flows out as warm air H2 from the outflow surface 33 of the heater 31 and flows into the warm air passage 50. [0058]

The downstream tip end sealing member 88 is separated from a wall surface 20c at a downstream end of the warm air passage 50. The warm air H2 flows into the mix space 27 from the warm air passage 50. With the above configuration, a ratio of cool air flowing from the upstream cool air passage 41 into the heater-side cool air passage 43 is maximized. That is, the ratio of the air flowing through the warm air passage 50 is maximized. [0059] [Configuration of Mix Door at Full-cool Position and Air Flow]

Reference is made to FIG. 8. Reference is made to FIG. 6. At the full-cool position, the upstream door 70 is in a most unfolded state. The upstream door diameter

R1 (FIG. 3) is the largest, and the upstream door angle 01 (FIG. 3) is the largest.

[0060]

The upstream tip end sealing member 78 is in close contact with the wall surface 20b at the upstream end of the heater-side cool air passage 43. That is, the upstream end of the heater-side cool air passage 43 is closed. The upstream intermediate sealing member 77 is separated from the wall surface 20a at the downstream end of the mix space side cool air passage 42. That is, the downstream end of the mix space side cool air passage 42 is open. [0061]

The upstream intermediate sealing member 77 is in close contact with a proximal end 73a (an end portion on a side close to the rotation shaft 62) of the upstream driven door 73, and reduces or prevents the cool air from flowing into the heater-side cool air passage 43 via a gap between the upstream extension door 71 and the upstream driven door 73.

[0062]

At the full-cool position, the downstream door 80 is in a most unfolded state. The downstream door diameter R2 (FIG. 3) is the largest, and the downstream door angle 02 (FIG. 3) is the largest. [0063]

The downstream intermediate sealing member 87 is in close contact with the proximal end 83a of the downstream driven door 83. The downstream tip end sealing member 88 is in close contact with the wall surface 20c at the downstream end of the warm air passage 50. That is, the downstream end of the warm air passage 50 is closed. With the above configuration, a ratio of cool air flowing into the mix space side cool air passage 42 from the upstream cool air passage 41 is maximized. That is, the ratio of the air flowing through the warm air passage 50 is minimized [0064] [Effects according to Embodiment] [Decrease in Torque for Rotation Shaft of Mix Door]

Reference is made to FIG. 8. The mix door 60 includes the downstream extension door 81 extending in a direction opposite to a direction in which the upstream extension door 71 extends, and the downstream driven door 83 connected to the downstream extension door 81 via the downstream hinge 82. The downstream door diameter R2 is the largest when the mix door 60 is at the full-cool position. That is, the downstream door 80 has a linear shape when the mix door 60 is at the full-cool position. Hereinafter, the description will be made in more detail. [0065]

FIG. 9 schematically illustrates the mix door 60 at the full-cool position and the mix door 60 at the full-hot position. The downstream door diameter R2 is the largest at the full-cool position and smaller toward the full-hot position, and is the smallest at the full-hot position. When viewed from a direction along the rotation shaft 62 (a state in FIG. 9) , a line passing through the rotation shaft 62 of the mix door 60 and extending in a vertical direction is defined as a vertical line V. As the mix door 60 moves from the full-cool position toward the full-hot position, a center of gravity G of the downstream door 80 is brought close to the vertical line V. A horizontal distance LI from the vertical line V to the center of gravity G of the downstream door 80 at the full-cool position is larger than a horizontal distance L2 from the vertical line V to the center of gravity G of the downstream door 80 at the full-hot position (LI > L2) . [0066]

With the above configuration, when the mix door 60 at the full-cool position is moved, a torque for rotating the rotation shaft 62 of the mix door 60 can be generated due to a weight of the downstream door 80. In particular, since the center of gravity G at the full-cool position is the most separate from the vertical line V, a larger torque can be generated. This torque can reduce a torque for maintaining the full-cool position by the upstream door 70. The torque applied to the rotation shaft 62 when the mix door 60 moves from the full-cool position can be reduced. As compared with a case in which the downstream door 80 is not provided, the rotation shaft 62 of the mix door 60 can be rotated with a small torque.

[0067]

A line passing through the rotation shaft 62 of the mix door 60 and extending in a horizontal direction is defined as a horizontal line H. The heater 31 is located below the horizontal line H. [0068]

When the mix door 60 is at the full-cool position, the upstream hinge 72 (a center of a swing shaft) is located below the horizontal line H. The upstream driven door 73 extends forward and downward with the upstream hinge 72 as a base point. That is, the upstream door 70 extends, as a whole, forward and downward from the rotation shaft 62. The downstream hinge 82 (a center of a swing shaft) is located above the horizontal line H. The downstream driven door 83 extends rearward and upward with the downstream hinge 82 as a base point. The downstream door 80 extends, as a whole, rearward and upward from the rotation shaft 62. [0069]

When the mix door 60 is at the full-hot position, the upstream hinge 72 is located above the horizontal line H.

The upstream driven door 73 extends substantially downward with the upstream hinge 72 as the base point. The downstream hinge 82 is located below the horizontal line H. The downstream driven door 83 extends rearward and upward with the downstream hinge 82 as a base point.

[0070]

[Prevention of Decrease in Torque due to Weight of Downstream Door]

Reference is made to FIGS. 5 and 6. The full-cool side change rate Cl is set to be smaller than the full-hot side change rate C2. Therefore, when the downstream pin 84 slides on the full-cool side groove 92a from the fullcool position toward the boundary point B (when the mix door 60 is in the vicinity of the full-cool position) , the downstream door diameter R2 is less likely to be smaller than that when the downstream pin 84 slides on the full- hot side groove 92b. That is, in the vicinity of the fullcool position, the downstream door diameter R2 is maintained (R2 is less likely to be smaller) even when the mix door 60 moves.

[0071]

Reference is made to FIG. 9. In other words, from the full-cool position to the boundary point B, the center of gravity G of the downstream door 80 is set to maintain a state of being separated from the vertical line V. The downstream door 80 receives an action of gravity in a manner of falling from the center of gravity G toward a direction W, and applies a rotational torque to the rotation shaft 62 in a direction toward the full-hot position via the downstream extension door 81. As the mix door 60 moves from the full-cool position toward the full-hot position, the downstream door 80 is bent and the center of gravity G of the downstream door 80 is brought close to the vertical line V, and the torque due to the weight of the downstream door 80 with respect to the rotation shaft 62 gradually decreases. However, the torque is prevented from decreasing by preventing a reduction in a distance from the vertical line V to the center of gravity G of the downstream door 80. When the position of the mix door 60 is in the vicinity of the full-cool position, a rotational force of returning to the full-cool position is attenuated, and a movement from the position in the vicinity of the full-cool position to the full-hot position can be made smooth.

[0072]

[Balance between Torque of Upstream Door and Torque of Downstream Door]

The upstream door diameter R1 is smaller when the mix door 60 is at the full-hot position than that when the mix door 60 is at the full-cool position. That is, when the mix door 60 is at the full-hot position, the upstream door

70 is in a folded state, and a torque for moving the mix door 60 to the full-cool position due to a weight of the upstream door 70 can decrease. At the full-hot position, the downstream door 80 is also in a folded state, and a torque for maintaining the full-hot position due to the weight of the downstream door 80 is attenuated. By balancing the torques due to the weights of the doors, the mix door 60 can easily start moving from the full-hot position toward the full-cool position.

[0073]

[Other Effects]

In addition, when the mix door 60 is at the full-cool position, the downstream door 80 closes the downstream end of the warm air passage 50. It is possible to prevent the warm air from flowing into the mix space 27 from the warm air passage 50. [0074]

In addition, as the mix door 60 moves from the fullcool position to the full-hot position, the downstream driven door 83 swings toward downstream of the downstream extension door 81 in the warm air passage 50. The downstream driven door 83 is less likely to hinder the warm air flowing through the warm air passage 50, and can reduce airflow resistance of the warm air passage 50.

[0075]

[Reduction in Number of Components of Intermediate Sealing Members ]

Reference is made to FIG. 3. The upstream intermediate sealing member 77 integrally includes a full- hot side sealing portion 77a that can come into contact with the case 20 at the full-hot position, and a full-cool side sealing portion 77b that can come into contact with the proximal end 73a of the upstream driven door 73 at the full-cool position. Although the full-hot side sealing portion 77a and the full-cool side sealing portion 77b may be provided separately, the number of components can be reduced by integrating the full-hot side sealing portion 77a and the full-cool side sealing portion 77b. [0076]

The invention is not limited to the embodiment as long as functions and effects according to the invention are exhibited. For example, although the full-cool side change rate Cl and the full-hot side change rate C2 of the downstream groove 92 have been described as having constant values, the change rates may vary as long as the full-cool side change rate Cl is smaller than the full-hot side change rate C2 (the downstream door diameter R2 varies in a gentler manner) . Alternatively, a boundary point CO between the full-cool side change rate Cl and the full-hot side change rate C2 may not be clearly set, and the change rates may be set such that the change rates gradually increase with a change from the full-cool position to the full-hot position .

[0077]

A weight of the downstream driven door 83 may be appropriately changed in order to adjust magnitude of the rotational torque applied to the rotation shaft 62 by changing the distance LI (the horizontal distance LI from the vertical line V to the center of gravity of the downstream door when the mix door 60 is at the full-cool position) from the rotation shaft 62 to the center of gravity G of the downstream door 80. [0078]

An example has been described in which the block portion 25a is provided on the support portion 25 that supports the upper end portion of the heater 31. Alternatively, the invention may be applied to a vehicular air conditioner in which the block portion 25a is not provided .

Industrial Applicability [0079]

The vehicular air conditioner according to the invention is suitable for being mounted on a passenger vehicle . Reference Signs List

[0080]

10: vehicular air conditioner

13: cooling heat exchanger

20: case

27 : mix space

31 : heater

40: cool air passage

50: warm air passage

60 : mix door

61: butterfly door portion

71: upstream extension door

72: upstream hinge

73: upstream driven door

80: downstream door

81: downstream extension door

82: downstream hinge

83: downstream driven door

B: boundary point

C: downstream door diameter change rate

CO: boundary point between full-cool side change rate and full-hot side change rate

Cl: full-cool side change rate,

C2 : full-hot side change rate

LI: distance from vertical line to center of gravity of downstream door at full-cool position, L2 : distance from vertical line to center of gravity of downstream door at full-hot position

G: center of gravity of downstream door R1 : upstream door diameter

R2 : downstream door diameter

V: vertical line

Claims

[Claim 1]

A vehicular air conditioner (10) comprising: a case (20) in which air flows; a cooling heat exchanger (13) capable of cooling the air flowing through the case (20) ; a heater (31) capable of heating the air flowing out from the cooling heat exchanger (13) ; a warm air passage (50) through which the air flowing out from the heater (31) flows; a cool air passage (40) through which the air flowing out from the cooling heat exchanger (13) flows without being heated by the heater (31) ; a mix door (60) capable of adjusting a ratio of the air flowing through the warm air passage (50) to the air flowing through the cool air passage (40) ; and a mix space (27) in which the air flowing through the warm air passage (50) and the air flowing through the cool air passage (40) merge, wherein the mix door (60) includes a butterfly door portion (61) including a rotation shaft (62) substantially orthogonal to a flow direction of the air flowing through the cool air passage (40) , an upstream extension door (71) extending from the rotation shaft (62) and being movable upstream of the rotation shaft (62) , and a downstream extension door (81) extending from the rotation shaft (62) in a direction substantially opposite to a direction in which the upstream extension door (71) extends, in the mix door (60) , the upstream extension door (71) and the downstream extension door (81) swing about the rotation shaft (62) , and the mix door (60) is capable of being located at a full-cool position at which a ratio of the air flowing through the warm air passage (50) is minimized, a full-hot position at which the ratio of the air flowing through the warm air passage (50) is maximized, and a temperature conditioning position at which neither the ratio of the air flowing through the warm air passage (50) nor a ratio of the air flowing through the cool air passage (40) is maximized, an upstream driven door (73) having a plate shape is connected to an extended tip end of the upstream extension door (71) via an upstream hinge (72) , a downstream driven door (83) having a plate shape is connected to an extended tip end of the downstream extension door (81) via a downstream hinge (82) , the downstream extension door (81) and the downstream driven door (83) close the warm air passage (50) when the mix door (60) is at the full-cool position, a downstream door diameter (R2) from the rotation shaft (62) to a tip end of the downstream driven door (83) is variable, and the downstream door diameter (R2) is larger when the mix door (60) is at the full-cool position than that when the mix door (60) is at the full-hot position.

[Claim 2]

The vehicular air conditioner (10) according to claim

1, wherein when a line passing through the rotation shaft (62) of the mix door (60) and extending in a vertical direction is defined as a vertical line (V) , a distance (LI, L2) between the vertical line (V) and a center of gravity (G) of a downstream door (80) including the downstream extension door (81) , the downstream hinge (82) , and the downstream driven door (83) is larger at the full-cool position than that at the full-hot position.

[Claim 3]

The vehicular air conditioner (10) according to claim

2, wherein when a change amount of the downstream door diameter (R2) with respect to a movement amount of the mix door (60) when the mix door (60) moves from the full-cool position to the full-hot position is defined as a downstream door diameter change rate (C) , the downstream door diameter change rate (C) includes, with a boundary point (B) between the full-cool position and the full-hot position as a boundary, a full-cool side change rate (Cl) from the fullcool position to the boundary point and a full-hot side change rate (C2) from the boundary point to the full-hot position, and the full-cool side change rate (Cl) is smaller than the full-hot side change rate (C2) .

[Claim 4]

The vehicular air conditioner (10) according to claim 1 or 2, wherein the upstream extension door (71) and the upstream driven door (73) close the cool air passage (40) when the mix door (60) is at the full-cool position, an upstream door diameter (Rl) from the rotation shaft (62) to a tip end of the upstream driven door (73) is variable, and the upstream door diameter (Rl) is smaller when the mix door (60) is at the full-hot position than that when the mix door (60) is at the full-cool position.