Air conditioner for vehicle

Abstract

To provide an air conditioner for a vehicle capable of rotating a rotation shaft of a mix door by a small torque.SOLUTION: A planar downstream side driven door (83) is connected at an extending tip via a downstream side hinge (82) on a downstream side extending door (81) of a butterfly type mix door (60). A downstream side door (80) closes a warm wind passage (50) when the mix door (60) is on a full cool position. A downstream side door radius (R2) from a rotation shaft (62) to a tip of the downstream side driven door (83) can be changed. The downstream side door radius (R2) when the mix door (60) is on a full cool position is longer than that when the mix door is on a full hot position.SELECTED DRAWING: Figure 9

Description

[Technical field]

[0001] The present invention relates to a vehicle air conditioner equipped with a butterfly type mix door. [Background technology]

[0002] 2. Description of the Related Art Many vehicles, such as passenger cars, are equipped with vehicle air conditioners for taking in outside air or inside air into the vehicle compartment and regulating the temperature. Patent Document 1 discloses a conventional technology relating to a vehicle air conditioner.

[0003] The vehicle air conditioning system disclosed in Patent Document 1 includes a case through 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, inside the case, there are provided a hot air passage through which air flowing out from the heater flows, a cold air passage through which air flowing out from the cooling heat exchanger flows without being heated by the heater, a mix door capable of adjusting the ratio of air flowing through the hot air passage and air flowing through the cold air passage, and a mix space where the air flowing through the hot air passage and the air flowing through the cold air passage join together.

[0005] The mix door includes a rotating shaft, an extension door extending radially outward from the rotating shaft, and a driven door connected to the tip of the extension door via a hinge. When the rotating shaft rotates, the positions of the extension door and the driven door change, changing the ratio of the air in the hot air passage and the air in the cold air passage flowing into the mix space, thereby changing the temperature of the conditioned air conditioned in the mix space. The conditioned air is discharged into the vehicle compartment through a duct or the like. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] JP 2009-090730 A Summary of the Invention [Problem to be solved by the invention]

[0007] In the full-cool position, where the ratio of cold air flowing through the cold air passage is the highest, the mix door is positioned so as to block the inlet of the heater. The heater is positioned below the rotation axis of the mix door. Therefore, in the full-cool position, the extension door of the mix door extends diagonally downward from the rotation axis, and the driven door extends approximately vertically downward from the tip of the extension door.

[0008] When the mix door is in the full cool position, in addition to its own weight, it is also subjected to the dynamic pressure of the cold air flowing from the cooling heat exchanger in a substantially horizontal direction. To move the mix door, a torque is required to rotate the rotating shaft against the mix door's own weight and the dynamic pressure of the cold air. It is desirable to be able to reduce the torque of the rotating shaft when moving the mix door from the full cool position.

[0009] An object of the present invention is to provide an air conditioner for a vehicle that can rotate a rotation shaft of a mix door with a small torque. [Means for solving the problem]

[0010] In the following description, reference numerals in the accompanying drawings are placed in parentheses to facilitate understanding of the present invention, but the present invention is not limited to the illustrated form.

[0011] According to the present invention, there is provided an air conditioner (10) for a vehicle, comprising: a case (20) through 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 of the cooling heat exchanger (13); a hot air passage (50) through which the air flowing out of the heater (31) flows; a cold air passage (40) through which the air flowing out of the cooling heat exchanger (13) flows without being heated by the heater (31); a mix door (60) capable of adjusting a ratio of air flowing through the hot air passage (50) and air flowing through the cold air passage (40); and a mix space (27) in which the air flowing through the hot air passage (50) and the air flowing through the cold air passage (40) are joined, The mix door (60) includes a butterfly door portion (61) having a rotation shaft (62) provided so as to be substantially perpendicular to the air flowing through the cold air passage (40), an upstream-side extension door (71) extending from the rotation shaft (62) and movable upstream of the rotation shaft (62), and a downstream-side extension door (81) extending from the rotation shaft (62) in a direction substantially opposite to the direction in which the upstream-side extension door (71) extends, The mix door (60) is The upstream extension door (71) and the downstream extension door (81) swing about the rotation shaft (62), a full-cool position in which the ratio of air flowing through the hot air passage (50) is minimized; a full hot position in which the ratio of air flowing through the hot air passage (50) is maximized; and a temperature harmonization position in which neither the ratio of air flowing through the hot air passage (50) nor the ratio of air flowing through the cold air passage (40) is maximized, The upstream extension door (71) has an extending tip connected to a plate-shaped upstream driven door (73) via an upstream hinge (72), A plate-shaped downstream driven door (83) is connected to the downstream extension door (81) at its extending tip via a downstream hinge (82), the downstream extension door (81) and the downstream driven door (83) close the hot air passage (50) when the mix door (60) is in the full-cool position; a downstream door diameter (R2) from the rotation shaft (62) to the tip of the downstream driven door (83) is variable; The vehicle air conditioner (10) is characterized in that the downstream door diameter (R2) is longer when the mix door (60) is in the full cool position than when the mix door (60) is in the full hot position. Effect of the Invention

[0012] The mix door (60) includes a downstream extension door (81) extending in the opposite direction to the extension direction of the upstream extension door (71), and a downstream driven door (83) connected to the downstream extension door (81) via a downstream hinge (82). The downstream door diameter (R2) is the longest when the mix door (60) is in the full cool position. That is, the downstream door (80) is linear when the mix door (60) is in the full cool position. The torque due to the weight of the downstream door (80) can be increased. This torque weakens the torque of the upstream door (70) that tries to maintain the full cool position, and the torque when the mix door (60) starts to move from the full cool position to the full hot position can be reduced. The rotation shaft (62) of the mix door (60) can be rotated with a small torque. [Brief description of the drawings]

[0013] [Figure 1] 1 is a perspective view of a vehicle air conditioner according to an embodiment of the present invention; [Diagram 2] 2 is a schematic cross-sectional view of the vehicle air conditioning device shown in FIG. [Diagram 3] This is a diagram explaining the configuration of the mix door and the air flow at the temperature harmonization position (between the full hot position and the boundary point) (the area surrounded by line 3 in Figure 2). [Figure 4] Figure 4A illustrates the mix door in a full cool position, Figure 4B illustrates the mix door in a temperature adjustment position, and Figure 4C illustrates the mix door in a full hot position. [Diagram 5] 11 is a graph showing the relationship between the position of the mix door and the downstream door diameter. [Figure 6] This is a diagram explaining the configuration of the mix door and the air flow in the temperature harmonized position (between the full cool position and the boundary point). [Figure 7] FIG. 13 is a diagram illustrating the configuration of the mix door and the air flow in the full hot position. [Figure 8] FIG. 13 is a diagram illustrating the configuration of the mix door and the air flow in the full cool position. [Figure 9]5A to 5C are diagrams illustrating the operation of the vehicle air conditioner according to the embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0014] The embodiment will be described below with reference to the attached drawings. In the drawings, Fr indicates front, Rr indicates rear, L indicates left based on the passenger in the vehicle cabin, R indicates right based on the passenger in the vehicle cabin, Up indicates up, and Dn indicates down. Furthermore, in the following description, "upstream" and "downstream" refer to the air flow direction.

[0015] <Example> 1 shows a vehicle air conditioner 10 that adjusts the temperature by taking in outside air and inside air into a vehicle compartment. The vehicle air conditioner 10 is mounted, for example, on a passenger car and disposed in the front of the vehicle compartment so as to extend in the left-right direction.

[0016] The vehicle air conditioner 10 is configured to include an air blower 11 that blows out the sucked air, and a temperature regulator 12 that adjusts the temperature of the air blown from the air blower 11 and blows out conditioned air into the vehicle cabin.

[0017] The blower 11 includes an electric motor and an impeller driven by the electric motor. When the impeller rotates, air inside and / or outside the vehicle cabin is sucked into the blower 11.

[0018] The temperature adjustment device 12 includes a case 20 through which the air sent from the blower 11 flows. The case 20 is formed with openings 21 to 23 that are open for blowing out the conditioned air.

[0019] The openings 21-23 include a defroster opening 21 that blows conditioned air toward the windshield to remove fogging from the windshield, a vent opening 22 that blows conditioned air toward the upper bodies of front seat occupants, and foot openings 23, 23 that blow conditioned air toward the legs of front seat occupants.

[0020] Fig. 2 shows a cross-sectional view of the temperature adjustment device 12. Please refer to Fig. 1 and Fig. 2 together. The defroster opening 21 can be opened and closed by an opening and closing member 17. The vent opening 22 can be opened and closed by an opening and closing member 18. The foot openings 23, 23 can be opened and closed by opening and closing members 19, 19.

[0021] The case 20 of the temperature adjustment device 12 has an intake section 24 that is open to take in the air sent from the air blower 11 into the case 20 .

[0022] The case 20 houses a cooling heat exchanger 13 capable of cooling the air flowing out from the intake portion 24. The gap between the cooling heat exchanger 13 and the case 20 is preferably filled with sealing materials 14, 14.

[0023] [heater] The case 20 houses 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 described later. The heater 31 has an inlet surface 32 through which cold air flows in, and an outlet surface 33 through which the cold air flowing in from the inlet surface 32 is heated inside the heater 31 and flows out as hot air.

[0024] A support part 25 is provided inside the case 20, supporting the upper end part of the heater 31. A gap between the support part 25 and the upper end part of the heater 31 is preferably filled with a sealant. A gap between the lower end part of the heater 31 and the case 20 is preferably filled with a sealant. The heater 31 may be any of a type that generates heat by electricity, a type through which hot water flows, and a type through which a high-temperature refrigerant flows.

[0025] [Hot air aisle, cold air aisle, mixed space] Inside the case 20, there are provided a hot air passage 50 through which air flowing out from the heater 31 flows, a cold air passage 40 through which air flowing out from the cooling heat exchanger 13 flows in a cold air state without being heated by the heater 31, and a mix space 27 in which the air flowing through the hot air passage 50 and the air flowing through the cold air passage 40 join together.

[0026] [Mixed Door] Please refer to Fig. 3. Inside the case 20, a mix door 60 capable of adjusting the ratio of air flowing through the hot air passage 50 and air flowing through the cold air passage 40 is provided.

[0027] [Butterfly door section] The mix door 60 includes a butterfly door portion 61 having two plate-like doors 71 and 81 that can swing about a rotation axis 62 .

[0028] [Rotating shaft, upstream extension door, downstream extension door] In detail, the butterfly door section 61 has a rotating shaft 62 whose axis extends in a direction approximately perpendicular to the air flowing through the cold air passage 40, an upstream extension door 71 that extends from the rotating shaft 62 and is movable upstream of the rotating shaft 62, and a downstream extension door 81 that extends from the rotating shaft 62 in a direction approximately opposite to the direction in which the upstream extension door 71 extends.

[0029] [Upstream hinge, upstream driven door] A plate-shaped upstream driven door 73 is connected to the upstream extension door 71 via an upstream hinge 72. The upstream driven door 73 is preferably provided at the extended tip of the upstream extension door 71 or in the vicinity thereof.

[0030] [Upstream sealing material] Each door has a rectangular shape. An upstream middle seal member 77 is provided on the edge of the upstream extension door 71. An upstream tip seal member 78 is provided on the edge of the upstream driven door 73.

[0031] [Upstream door diameter, upstream door angle] The upstream driven door 73 can swing around the upstream hinge 72 relative to the upstream extension door 71. An upstream groove 91 capable of guiding the swing of the upstream driven door 73 is formed on side wall surfaces 90, 90 (see also FIG. 1) of the case 20. An upstream pin 74 capable of sliding relative to the upstream groove 91 is attached near the tip of the upstream driven door 73. By appropriately changing the shape and position of the upstream groove 91, the trajectory of the upstream driven door 73 can be appropriately changed.

[0032] When the rotating shaft 62 rotates, an upstream door diameter R1 from the rotating shaft 62 to the upstream tip seal member 78 of the upstream driven door 73 changes. The upstream door angle θ1 between the upstream driven door 73 and the upstream extending door 71 can also change. The upstream door angle θ1 is always 180 degrees or less. Hereinafter, the upstream extending door 71, the upstream hinge 72, and the upstream driven door 73 are collectively referred to as the upstream door 70.

[0033] [Downstream hinge, downstream driven door] A plate-shaped downstream side driven door 83 is connected to the downstream side extending door 81 via a downstream side hinge 82. The downstream side driven door 83 is preferably provided at the extending tip of the downstream side extending door 81 or in the vicinity thereof.

[0034] [Downstream seal material] A downstream intermediate seal member 87 is provided on the edge of the downstream extension door 81. A downstream tip seal member 88 is provided on the edge of the downstream driven door 83.

[0035] [Downstream door diameter, downstream door angle] The downstream driven door 83 can swing around the downstream hinge 82 relative to the downstream extension door 81. A downstream groove 92 capable of guiding the swing of the downstream driven door 83 is formed on side wall surfaces 90, 90 of the case 20. A downstream pin 84 capable of sliding relative to the downstream groove 92 is attached near the tip of the downstream driven door 83. By appropriately changing the shape and position of the downstream groove 92, the trajectory of the downstream driven door 83 can be appropriately changed.

[0036] When the rotating shaft 62 rotates, a downstream door diameter R2 from the rotating shaft 62 to the downstream tip seal member 88 of the downstream driven door 83 changes. The downstream door angle θ2 formed by the downstream driven door 83 and the downstream extending door 81 can also change. The downstream door angle θ2 is always 180 degrees or less. Hereinafter, the downstream extending door 81, the downstream hinge 82, and the downstream driven door 83 are collectively referred to as the downstream door 80.

[0037] [Details of the cold air passage] The cold air passage 40 includes an upstream cold air passage 41 between the cooling heat exchanger 13 and the swing range of the upstream door 70, a mix space side cold air passage 42 in which the cold air flowing from the upstream cold air passage 41 branches off by the upstream door 70 and heads toward the mix space 27, and a heater side cold air passage 43 in which the cold air flowing from the upstream cold air passage 41 branches off by the upstream door 70 and heads toward the heater 31.

[0038] Between the rotating shaft 62 and the support part 25, there is provided a block part 25a that suppresses or prevents a part of the cold air that has flowed into the heater-side cold air passage 43 from flowing into the hot air passage 50, bypassing the heater 31. The block part 25a is integrated with the support part 25 and is a plate-like part that extends from the support part 25 to the rotating shaft 62. The tip of the block part 25a is located near the rotating shaft 62, and substantially suppresses the cold air that has flowed into the heater-side cold air passage 43 from flowing into the hot air passage 50.

[0039] [Mix door position] When the rotary shaft 62 is rotated, the upstream door 70 and the downstream door 80 swing about the rotary shaft 62, thereby changing the position of the mix door 60.

[0040] [Full cool position] FIG. 4A shows the mix door 60 in the full cool position where the proportion of air flowing through the hot air passage 50 is minimized.

[0041] [Temperature harmonization position] FIG. 4B shows the mix door 60 in a temperature matching position that maximizes neither the proportion of air flowing through the hot air passage 50 nor the proportion of air flowing through the cold air passage 40.

[0042] [Full hot position] FIG. 4C shows the mix door 60 in the full hot position which maximizes the proportion of air flowing through the hot air passage 50 .

[0043] [Downstream driven door swing] 3 and 4A to 4C. As the mix door 60 moves from the full cool position (FIG. 4A) to the full hot position (FIG. 4C), both the downstream door angle θ2 and the downstream door diameter R2 become smaller. 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 the downstream side of the hot air passage 50 (in the direction approaching the mix space 27) relative to the downstream extension door 81 (the downstream door angle θ2 gradually becomes smaller).

[0044] [Rate of change in downstream door diameter] 5 is a graph showing the relationship between the position of the mix door 60 and the downstream door diameter R2. When the mix door 60 is in the full cool position, the downstream door diameter R2 is maximum. 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 in the full hot position, the downstream door diameter R2 is minimum.

[0045] The amount of change in downstream door diameter R2 relative to the amount of movement of mix door 60 (the magnitude of the angle through which rotation shaft 62 rotates) is defined as downstream door diameter change rate C. The downstream door diameter change rate C has different characteristics with boundary point B between the full cool position and the full hot position as the boundary. Of the downstream door diameter change rate C, the change rate from the full cool position to boundary point B is defined as full cool side change rate C1, and the change rate from boundary point B to the full hot position is defined as full hot side change rate C2. The full cool side change rate C1 is set smaller than the full hot side change rate C2.

[0046] Please refer to Figures 3 and 5. The downstream groove 92 is formed so that the downstream driven door 83 swings based on the downstream door diameter change rate C. In detail, the downstream groove 92 has a full-cool side groove 92a corresponding to the range from the full-cool position to the boundary point B, and a full-hot side groove 92b corresponding to the range from the boundary point B to the full-hot position.

[0047] Please refer to Fig. 6. As in Fig. 3, the mix door 60 is in the temperature adjustment position. The downstream pin 84 is located in the full-cool groove 92a (between the full-cool position and the boundary point B). As shown in the graph in Fig. 5, the full-cool side change rate C1 is set smaller than the full-hot side change rate C2. Therefore, when the downstream pin 84 slides in the full-cool groove 92a from the full-hot position toward the boundary point B, the downstream door diameter R2 is less likely to become small than when the downstream pin 84 slides in the full-hot groove 92b.

[0048] [Upstream driven door swing] 3 and 4A to 4C. As the mix door 60 moves from the full cool position (FIG. 4A) to the full hot position (FIG. 4C), both the upstream door angle θ1 and the upstream door diameter R1 become smaller. 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 the downstream side (closer to the heater 31) of the heater side cool air passage 43 relative to the upstream extension door 71 (the upstream door angle θ1 gradually becomes smaller).

[0049] [Mix door configuration and air flow in temperature-balanced position] Refer to Fig. 3. In the temperature adjustment position, the upstream intermediate seal member 77 is separated from the wall surface 20a at the downstream end of the cold air passage 42 on the mix space side. That is, the downstream end of the cold air passage 42 on the mix space side is open. Cold air C1 can flow from the cold air passage 42 on the mix space side into the mix space 27.

[0050] The upstream end seal member 78 is separated from the wall surface 20b at the upstream end of the heater side cold air passage 43. That is, the upstream end of the heater side cold air passage 43 is open. Cold air C2 can flow from the upstream side cold air passage 41 to the heater side cold air passage 43. The cold air C2 flows from the inlet surface 32 of the heater 31 into the inside of the heater 31.

[0051] The cold air C2 flows out from the outlet surface 33 of the heater 31 as the hot air H1 and flows into the hot air passage 50.

[0052] The downstream end seal member 88 is separated from the wall surface 20c at the downstream end of the hot air passage 50. That is, the downstream end of the hot air passage 50 is open. The hot air H1 flows from the hot air passage 50 into the mix space 27.

[0053] In this way, when the mix door 60 is in the temperature adjustment position, part of the air flowing out from the cooling heat exchanger 13 flows through the cold air passage 40 as cold air C1, and at the same time, another part flows through the hot air passage 50 as hot air H1. For this reason, when the mix door 60 is in the temperature adjustment position, neither the ratio of air flowing through the hot air passage 50 nor the ratio of air flowing through the cold air passage 40 is maximum.

[0054] [Mix door configuration and airflow in full hot position] Refer to Figure 7. In the full hot position, the upstream door 70 is in the most bent state. The upstream door diameter R1 (Figure 3) is the shortest, and the upstream door angle θ1 (Figure 3) is the smallest.

[0055] The upstream middle seal member 77 is in close contact with the wall surface 20a of the downstream end of the mix space side cold air passage 42. That is, the downstream end of the mix space side cold air passage 42 is closed. The upstream end seal member 78 is separated from the wall surface 20b of the heater side cold air passage 43. That is, the upstream end of the heater side cold air passage 43 is open. Cold air C3 flows from the upstream side cold air passage 41 to the heater side cold air passage 43.

[0056] In the full hot position, the downstream door 80 is in the most bent state. The downstream door diameter R2 (FIG. 3) is the shortest, and the downstream door angle θ2 (FIG. 3) is the smallest.

[0057] The cold air C3 flows through the heater-side cold air passage 43 and enters the inside of the heater 31 from the inlet surface 32 of the heater 31. The cold air C3 heated by the heater 31 flows out from the outlet surface 33 of the heater 31 as hot air H2 and flows into the hot air passage 50.

[0058] The downstream end seal member 88 is separated from the wall surface 20c at the downstream end of the hot air passage 50. The hot air H2 flows from the hot air passage 50 into the mix space 27. With the above configuration, the ratio of cold air flowing from the upstream cold air passage 41 to the heater side cold air passage 43 is maximized. In other words, the ratio of air flowing through the hot air passage 50 is maximized.

[0059] [Mix door configuration and airflow in full cool position] Refer to Fig. 8. In the full cool position, the upstream door 70 is in the most expanded state. The upstream door diameter R1 (Fig. 3) is the longest, and the upstream door angle θ1 (Fig. 3) is the largest.

[0060] The upstream end seal member 78 is in close contact with the wall surface 20b at the upstream end of the heater side cold air passage 43. That is, the upstream end of the heater side cold air passage 43 is closed. The upstream middle seal member 77 is separated from the wall surface 20a at the downstream end of the mix space side cold air passage 42. That is, the downstream end of the mix space side cold air passage 42 is open.

[0061] In addition, the upstream intermediate sealing member 77 is in close contact with the base end 73a (the end closer to the rotating shaft 62) of the upstream driven door 73, and suppresses or prevents cold air from flowing into the heater side cold air passage 43 through the 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 the most expanded state, the downstream door diameter R2 (FIG. 3) is the longest, and the downstream door angle θ2 (FIG. 3) is the largest.

[0063] The downstream intermediate seal member 87 is in close contact with the base end 83a of the downstream driven door 83. The downstream tip seal member 88 is in close contact with the wall surface 20c at the downstream end of the hot air passage 50. That is, the downstream end of the hot air passage 50 is closed. With the above configuration, the proportion of cold air flowing from the upstream cold air passage 41 into the mix space cold air passage 42 is maximized. That is, the proportion of air flowing through the hot air passage 50 is minimized.

[0064] [Effects of the embodiment] [Reducing torque on the rotating shaft of the mixed door] Please refer to Fig. 8. The mix door 60 includes a downstream side extending door 81 extending in the opposite direction to the upstream side extending door 71, and a downstream side driven door 83 connected to the downstream side extending door 81 via a downstream side hinge 82. The downstream side door diameter R2 is the longest when the mix door 60 is in the full cool position. That is, the downstream side door 80 is linear when the mix door 60 is in the full cool position. This will be described in more detail below.

[0065] FIG. 9 shows the mix door 60 in the full cool position and the mix door 60 in the full hot position. The downstream door diameter R2 is the longest at the full cool position, shortens toward the full hot position, and is the shortest at the full hot position. When viewed from the direction along the rotation shaft 62 (as shown in FIG. 9), a line passing through the rotation shaft 62 of the mix door 60 and extending vertically is defined as a vertical line V. The center of gravity G of the downstream door 80 approaches the vertical line V as the mix door 60 moves from the full cool position to the full hot position. The horizontal distance L1 from the vertical line V to the center of gravity G of the downstream door 80 at the full cool position is longer than the horizontal distance L2 from the vertical line V to the center of gravity G of the downstream door 80 at the full hot position (L1>L2).

[0066] With the above configuration, when the mix door 60 is moved from the full cool position, a torque for rotating the rotation shaft 62 of the mix door 60 can be generated by the weight of the downstream door 80. In particular, since the center of gravity G at the full cool position is the furthest from the vertical line V, a larger torque can be generated. This torque can reduce the torque applied to the upstream door 70 to maintain the full cool position. The torque applied to the rotation shaft 62 when the mix door 60 is moved from the full cool position can be reduced. Compared to the case where the downstream door 80 is not provided, the rotation shaft 62 of the mix door 60 can be rotated with a smaller torque.

[0067] A line passing through the rotation shaft 62 of the mix door 60 and extending horizontally is defined as a horizontal line H. The heater 31 is located below the horizontal line H.

[0068] When the mix door 60 is in the full cool position, the upstream hinge 72 (center of the swing axis) is located below the horizontal line H. The upstream driven door 73 extends downward toward the front with the upstream hinge 72 as a base point. That is, the upstream door 70 as a whole extends downward toward the front from the rotation axis 62. The downstream hinge 82 (center of the swing axis) is located above the horizontal line H. The downstream driven door 83 extends upward toward the rear with the downstream hinge 82 as a base point. The downstream door 80 as a whole extends upward toward the rear from the rotation axis 62.

[0069] When the mix door 60 is in the full hot position, the upstream hinge 72 is located above the horizontal line H. The upstream driven door 73 extends substantially downward from the upstream hinge 72. The downstream hinge 82 is located below the horizontal line H. The downstream driven door 83 extends upward and rearward from the downstream hinge 82.

[0070] [Suppression of torque reduction due to the weight of the downstream door] 5 and 6. The full-cool side change rate C1 is set to be smaller than the full-hot side change rate C2. Therefore, when the downstream pin 84 slides in the full-cool side groove 92a from the full-hot 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 become smaller than when the downstream pin 84 slides in the full-hot side groove 92b. In other words, in the vicinity of the full-cool position, the downstream door diameter R2 is set to be maintained (R2 is less likely to become shorter) even if the mix door 60 moves.

[0071] Refer 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 be kept away from the vertical line V. The downstream door 80 is subjected to the action of gravity so as to fall from the center of gravity G in the direction W, and a rotational torque in the direction toward the full cool position is applied to the rotation shaft 62 via the downstream extension door 81. As the downstream door 80 moves from the full cool position to the full hot position, the downstream door 80 bends, and the center of gravity G approaches the vertical line V, and the torque due to the weight of the downstream door 80 against the rotation shaft 62 gradually decreases, but the decrease in the torque is suppressed by suppressing the reduction in the 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 near the full cool position, the rotational force that tries to return to the full cool position is attenuated, and the movement from the position near the full cool position to the full hot side can be made smooth.

[0072] [Balancing the torque of the upstream door and the downstream door] The upstream door diameter R1 is shorter when the mix door 60 is in the full hot position than when it is in the full cool position. That is, when it is in the full hot position, the upstream door 70 is folded, and the torque that tries to move the mix door 60 to the full cool position due to the weight of the upstream door 70 can be reduced. When it is in the full hot position, the downstream door 80 is also folded, and the torque that tries to maintain the full hot position due to the weight of the downstream door 80 is attenuated. By balancing the torque due to the weight of each door, it is possible to make it easier for the mix door 60 to start moving from the full hot position to the full cool position.

[0073] [Other Effects] In addition, when the mix door 60 is in the full-cool position, the downstream door 80 closes the downstream end of the hot air passage 50. The flow of hot air from the hot air passage 50 into the mix space 27 can be suppressed.

[0074] In addition, as the mix door 60 moves from the full cool position to the full hot position, the downstream driven door 83 swings toward the downstream side of the hot air passage 50 relative to the downstream extension door 81. The downstream driven door 83 is less likely to obstruct the hot air flowing through the hot air passage 50, and the ventilation resistance of the hot air passage 50 can be reduced.

[0075] [Reduction in number of intermediate seal parts] Please refer to Fig. 3. The upstream intermediate seal member 77 is integrally formed with a full hot side seal portion 77a capable of contacting the case 20 at the full hot position, and a full cool side seal portion 77b capable of contacting the base end 73a of the upstream driven door 73 at the full cool position. The full hot side seal portion 77a and the full cool side seal portion 77b may be provided separately, but integrating them can reduce the number of parts.

[0076] As long as the present invention has the functions and effects, it is not limited to the embodiments. For example, the full cool side change rate C1 and the full hot side change rate C2 of the downstream groove 92 have been described as having fixed values, but as long as the full cool side change rate C1 is smaller than the full hot side change rate C2 (the downstream door diameter R2 changes more slowly), the respective change rates may be variable. Alternatively, the boundary point C0 between the full cool side change rate C1 and the full hot side change rate C2 may not be clearly set, and the change rates may be set so that they gradually increase as the position moves from the full cool position to the full hot position.

[0077] In addition, the weight of the downstream driven door 83 may be appropriately changed in order to adjust the magnitude of the rotational torque applied to the rotating shaft 62 by changing the distance L1 from the rotating shaft 62 of the downstream door 80 to the center of gravity G (the horizontal distance L1 from the vertical line V to the center of gravity of the downstream door when the mix door 60 is in the full cool position).

[0078] In addition, an example has been described in which the support portion 25 that supports the upper end portion of the heater 31 is provided with the block portion 25a, but the present invention may also be applied to a vehicle air conditioner that is not provided with the block portion 25a. [Industrial Applicability]

[0079] The vehicle air conditioner of the present invention is suitable for installation in a passenger car. [Explanation of symbols]

[0080] 10...Vehicle air conditioning system 13…Cooling heat exchanger 20…Case 27…Mixed Space 31…Heater 40...Cold air passage 50…Hot air passage 60…Mixed Door 61…Butterfly door section 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 C0: Boundary point between full cool side change rate and full hot side change rate C1…Full cool side change rate C2…Full hot side change rate L1: Distance from the vertical line to the center of gravity of the downstream door at full cool position L2: Distance from the vertical line to the center of gravity of the downstream door in the full hot position G: Center of gravity of downstream door R1…Upstream door diameter R2: Downstream door diameter V…Plumb line

Claims

1. An air conditioner (10) for a vehicle, comprising: a case (20) through 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 of the cooling heat exchanger (13); a hot air passage (50) through which the air flowing out of the heater (31) flows; a cold air passage (40) through which the air flowing out of the cooling heat exchanger (13) flows without being heated by the heater (31); a mix door (60) capable of adjusting a ratio of air flowing through the hot air passage (50) and air flowing through the cold air passage (40); and a mix space (27) in which the air flowing through the hot air passage (50) and the air flowing through the cold air passage (40) join together, The mix door (60) includes a butterfly door portion (61) having a rotation shaft (62) provided so as to be substantially perpendicular to the air flowing through the cold air passage (40), an upstream-side extension door (71) extending from the rotation shaft (62) and movable upstream of the rotation shaft (62), and a downstream-side extension door (81) extending from the rotation shaft (62) in a direction substantially opposite to the direction in which the upstream-side extension door (71) extends, The mix door (60) is The upstream extension door (71) and the downstream extension door (81) swing around the rotation shaft (62), A full-cool position in which the ratio of air flowing through the hot air passage (50) is minimized; a full hot position in which the ratio of air flowing through the hot air passage (50) is maximized; and a temperature harmonization position in which neither the ratio of air flowing through the hot air passage (50) nor the ratio of air flowing through the cold air passage (40) is maximized; The upstream side extension door (71) has an extension tip connected to a plate-shaped upstream side driven door (73) via an upstream side hinge (72), A plate-shaped downstream side driven door (83) is connected to the downstream side extension door (81) at its extended tip via a downstream side hinge (82), the downstream extension door (81) and the downstream driven door (83) close the hot air passage (50) when the mix door (60) is in the full-cool position; A downstream door diameter (R2) from the rotation shaft (62) to the tip of the downstream driven door (83) is variable, The vehicle air conditioner (10) is characterized in that the downstream door diameter (R2) is longer when the mix door (60) is in the full cool position than when the mix door (60) is in the full hot position.

2. If a line passing through the rotation shaft (62) of the mix door (60) and extending vertically is defined as a vertical line (V), 2. The vehicle air conditioning system (10) of claim 1, wherein a distance (L1, 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 longer when in the full cool position than when in the full hot position.

3. When the mix door (60) moves from the full cool position to the full hot position, the downstream door diameter (R2) changes by a downstream door diameter change rate (C), the downstream side door diameter change rate (C) includes a full cool side change rate (C1) from the full cool position to a boundary point (B) between the full cool position and the full hot position, and a full hot side change rate (C2) from the boundary point to the full hot position, 3. The vehicle air conditioner (10) according to claim 2, wherein the full-cool side change rate (C1) is smaller than the full-hot side change rate (C2).

4. the upstream extension door (71) and the upstream driven door (73) close the cold air passage (40) when the mix door (60) is in the full cool position; An upstream door diameter (R1) from the rotation shaft (62) to the tip of the upstream driven door (73) is variable, 3. The vehicle air conditioner (10) according to claim 1 or 2, wherein the upstream door diameter (R1) is smaller when the mix door (60) is in the full hot position than when the mix door (60) is in the full cool position.

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