JP6915022B2 - Vehicle air conditioner - Google Patents

Description

The present invention relates to a vehicle air conditioner.

Vehicle air conditioners used in automobiles and the like include a heater core that is a heat exchanger for heating, an evaporator that is a heat exchanger for cooling, and an air mix space that mixes hot air or cold air that has passed through these heater cores and evaporators. It is equipped with an air mix damper that changes the mixing ratio of hot air and cold air in this air mix space. In such a device, by adjusting the rotation amount of the air mix damper, the mixing ratio of the cold air and the hot air changes, and the air having a desired temperature can be obtained.

By the way, in the above device, in order to supply wind with a uniform temperature distribution to each seat inside the vehicle, it is important to uniformly suppress air leakage between the heater core side and the evaporator side by an air mix damper. It becomes. That is, if there is a difference in sealing performance in each part of the air mix damper, a local change occurs in the mixing ratio of cold air and hot air. As a result, the temperature distribution of the wind blown into the vehicle may be biased.

As an example of a technique aimed at suppressing such air leakage, the one described in Patent Document 1 below is known. In the vehicle air conditioner described in Patent Document 1, the peripheral edge of the plate-shaped air mix door (air mix damper) abuts on the seal wall integrally formed inside the air conditioner case, thereby causing the air mix door. It is said that the sealing property between the heater core side and the evaporator side is enhanced.

Japanese Unexamined Patent Publication No. 2004-42686

Here, in the device described in Patent Document 1, a gap is formed in the vicinity of the rotation axis of the air mix door so as not to obstruct the movable range. Therefore, while the sealing property at the peripheral edge of the air mix door is improved, air leaks between the heater core side and the evaporator side through the above gap. In the leaked region, cold air and hot air are inadvertently mixed with each other, so that when the wind is supplied into the living space of the vehicle, the temperature distribution of the wind in the space may be biased. As a result, there is a concern that the apparent efficiency of the air conditioner may decrease.

The present invention has been made to solve the above problems, and an object of the present invention is to provide an air conditioner for a vehicle capable of exhibiting sufficient efficiency.

According to the first aspect of the present invention, the vehicle air conditioner includes a rotating shaft portion extending in the axial direction and having an insertion shaft formed at an end portion in the axial direction, and the axial line from the rotating shaft portion. A damper having a plate-shaped first damper body extending in the radial direction of the above, and a unit case having a side wall portion formed with a bearing hole in which the damper is housed and the insertion shaft is rotatably inserted. The rotating shaft portion has a flange portion that is provided only in a part of the circumferential direction of the axis and projects radially outward from the base end of the insertion shaft, and the first damper main body is , The first damper plate surface facing one side in the circumferential direction, the second damper plate surface facing the other side in the circumferential direction, and the end portion of the flange portion on one side in the circumferential direction extending outward in the radial direction and described above. The side wall portion has a first damper side end surface that is flush with the flange portion, and the side wall portion is an inner surface surface on which the flange portion and the first damper side end surface can abut from the axial direction, and the axial direction from the inner side surface. The first damper plate surface of the first damper body has a ridge that can be brought into contact with the other side in the circumferential direction, and is inside the radial direction of the ridge. The radial distance between the end portion and the bearing hole is smaller than the radial dimension of the flange portion, and the damper is provided so as to be separated from the first damper main body in the circumferential direction. It has a plate-shaped second damper body extending from the rotating shaft portion in the radial direction of the axis, and the second damper body is radially outward from the other end in the circumferential direction of the flange portion. extending with have a second damper end surface forming the flange portion and said first damper-side end surface flush with, an evaporator for cooling the air, and a heater core for heating air, a further, wherein said unit case includes A cooling space accommodating the evaporator, a heating space connected to the cooling space and accommodating the heater core, the cooling space and an air mix space connected to the heating space are formed inside, and the damper is the damper. The ratio of air introduced into the air mix space from the cooling space and the heating space is adjusted by being provided in the air mix space in the unit case and rotating between the maximum cooling position and the maximum heating position. In the air mix damper, the maximum cooling position extends in a direction in which the first damper main body and the second damper main body intersect in the direction in which the cooling space and the heating space are separated from each other, and the cooling space and the heating are provided. The position that separates the space, and the maximum heating position is the first damper main body and the second This is a position where the damper main body extends in the direction of separation between the cooling space and the heating space to communicate the cooling space and the heating space.

According to this configuration, the radial distance between the radial inner end of the ridge and the bearing hole is smaller than the radial dimension of the collar. This makes it possible to reduce the possibility of fluid leaking from the gap between the radial inner end of the ridge and the rotating shaft.
On the other hand, when the radial distance between the radial inner end of the ridge and the bearing hole is larger than the radial dimension of the flange, the above gap is caused by the axial deviation of the rotating shaft. Will grow. This can cause fluid to leak through the gap. However, according to the above configuration, such a possibility can be reduced.
Further, by providing the second damper main body, it is possible to secure a larger dimension of the damper. Therefore, when changing / guiding the flow of the fluid flowing in the unit case, it is possible to sufficiently cope with the case where the cross-sectional area of the flow path of the fluid is large.

According to the second aspect of the present invention, in the vehicle air conditioner according to the first aspect, the ridges are the first part constituting the radial outer portion of the ridges and the ridges. The radial inner portion may be configured and may have a second portion extending from the first portion toward either one side or the other side in the circumferential direction toward the inner side in the radial direction.

According to this configuration, the second portion of the ridge allows the radial distance between the radial inner end of the ridge and the bearing hole to be smaller than the radial dimension of the collar. This makes it possible to reduce the possibility of fluid leaking from the gap between the radial inner end of the ridge and the rotating shaft.

According to the present invention, it is possible to provide a vehicle air conditioner capable of exhibiting sufficient efficiency.

It is sectional drawing in the 1st axis direction of the air conditioner for vehicles which concerns on embodiment of this invention. It is a figure which looked at the air mix damper which concerns on embodiment of this invention from the direction of the 1st axis. It is a figure which looked at the air mix damper which concerns on embodiment of this invention from the direction which intersects with the 1st axis. It is a figure which shows the structure of the unit case which concerns on embodiment of this invention. It is an enlarged view of the main part of the air conditioner for vehicles which concerns on embodiment of this invention.

[First Embodiment]

Embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, the vehicle air conditioner 100 according to the present embodiment includes an evaporator 1, a heater core 2, a unit case 3 for accommodating them, and an air mix damper 4 for adjusting the air flow inside the unit case 3. , A foot switching damper 5, and a face differential switching damper 6.
Note that FIG. 1 is a cross-sectional view of the vehicle air conditioner 100 as viewed from the width direction, which is the direction intersecting the traveling direction of the vehicle on which the vehicle air conditioner 100 is mounted. In the following description, "cross-sectional view" refers to a cross section from this width direction.

As an evaporator 1, as an example, a cooling heat exchanger that employs a vapor compression refrigeration cycle is used. The low-pressure refrigerant flowing in the evaporator 1 is evaporated by endothermic heat from the air flowing around the evaporator 1 to cool the air. In the present embodiment, the evaporator 1 is formed in the shape of a thick plate.

As the heater core 2, a hot water type heating heat exchanger that heats air with hot water (engine cooling water) from a vehicle engine or the like (not shown) is used. The air flowing around the heater core 2 is heated by applying the amount of heat from the hot water flowing in the heater core 2. In the present embodiment, the heater core 2 is also formed in the shape of a thick plate like the evaporator 1.

The unit case 3 accommodates the evaporator 1 and the heater core 2 and forms an air flow path inside. More specifically, inside the unit case 3, there are a cooling space 7, a heating space 8, an air mix space 91, a foot outlet flow path 92, a relay space 93, a face outlet flow path 94, and the like. A differential outlet flow path 95 (defogger outlet flow path) is formed.

The evaporator 1 is housed in the cooling space 7. The evaporator 1 divides the cooling space 7 into two spaces. More specifically, the cooling space 7 has an introduction space 71 and a cold air supply space 72. The space formed on one side of the evaporator 1 is an introduction space 71 through which air introduced by a fan or the like (not shown) flows. The space on the other side of the evaporator 1 (the space formed on the side opposite to the introduction space 71 across the evaporator 1) is a cold air supply space 72 through which the air cooled by the evaporator 1 flows. That is, the air in the introduction space 71 is cooled by coming into contact with the evaporator 1 by the air blown from the fan, and flows into the cold air supply space 72. The outlet of the cold air supply space 72 is a cold air discharge port 73.

The heater core 2 is housed in the heating space 8. Further, the heating space 8 communicates with the cooling space 7 via a part of the air mix space 91 described later. More specifically, the heating space 8 is provided at a position facing the cooling space 7 from the cold air supply space 72 side. The heater core 2 divides the heating space 8 into three spaces. The heating space 8 has a second introduction space 81, a warm air supply space 82, and a return space 83. The space on one side (that is, the side facing the cooling space 7) across the heater core 2 is a second introduction space 81 to which the air supplied from the cold air supply space 72 is guided. The space on the other side of the heater core 2 (the space formed on the side opposite to the second introduction space 81 across the heater core 2) is a warm air supply space 82 through which the air heated by the heater core 2 flows. That is, the air in the second introduction space 81 is heated by coming into contact with the heater core 2 and flows into the warm air supply space 82.

Further, in the heating space 8, a space is formed between the upper end portion of the heater core 2 and the inner wall of the unit case 3. This space is a return space 83 for returning the air that has sequentially passed through the second introduction space 81 and the warm air supply space 82 to the air mix space 91 described later. The outlet of the return space 83 is a warm air discharge port 84.

The cooling space 7 and the heating space 8 configured as described above are connected to each other by the air mix space 91. In the air mix space 91, the air cooled in the cooling space 7 (cold air) and the air heated in the heating space 8 (warm air) are mixed. More specifically, the air mix space 91 is a flow path that communicates with the cold air supply space 72 of the cooling space 7 and the hot air supply space 82 of the heating space 8 and extends generally upward. On the cooling space 7 side of the air mix space 91, a guide partition wall portion 10 for guiding the air flowing in the air mix space 91 upward is provided.

Further, the air mix space 91 is provided with an air mix damper 4 (damper) for adjusting the mixing ratio of the air introduced from the cooling space 7 and the heating space 8. As shown in FIGS. 2 and 3, the air mix damper 4 is a plate-shaped member rotatably supported on the hot air discharge port 84 in the heating space 8. More specifically, the air mix damper 4 includes a first support portion 41 (rotating shaft portion) that rotates around a first axis A1 (axis) extending in the width direction of the vehicle, and the first support portion 41. It has an air mix damper main body 42 (first damper main body) extending on a plane intersecting the width direction, and a reheat prevention damper 43 (second damper main body).

The first support portion 41 is a substantially rod-shaped member having a circular cross section. At the end of the first support portion 41 in the direction of the first axis A1, an insertion shaft 41S to be inserted into the bearing hole H formed in the inner side surface 30A of the side wall portion 30 of the unit case 3 is formed. Further, a collar portion 41B is provided on the outer peripheral side of the first support portion 41. The flange portion 41B projects from the base end of the insertion shaft 41S toward the outer side in the radial direction with respect to the first axis A1. Further, the flange portion 41B is provided only in a partial region in the circumferential direction with respect to the first axis A1. In other words, of the outer peripheral surface of the first support portion 41, the region where the flange portion 41B is not provided is exposed radially outward with respect to the first axis A1.

In the present embodiment, the first support portion 41 is provided on a straight line connecting the upper end portion (first end portion t1) and the lower end portion (second end portion t2) of the warm air discharge port 84. ing. Further, the first support portion 41 is provided at a position corresponding to the upper end portion of the heater core 2 in the vertical direction in a cross-sectional view. In addition, the dimensions from the first support portion 41 to the lower end portion (third end portion t3) of the guide partition wall portion 10 are substantially the same as the dimensions from the first support portion 41 to the second end portion t2. be.

The air mix damper main body 42 has the dimensions from the first support portion 41 to the second end portion t2 (that is, the dimensions from the first support portion 41 to the third end portion t3 of the guide partition wall portion 10) in a cross-sectional view. It is extended by the minute. Of both sides of the plate-shaped air mix damper main body 42 in the thickness direction, the surface facing one side in the circumferential direction with respect to the first axis A1 is the first damper plate surface 42A, and the surface facing the other side in the circumferential direction is the first. It is said that the two damper plate surface 42B. Further, the surface connecting the first damper plate surface 42A and the second damper plate surface 42B and facing the side wall portion 30 (inner side surface 30A) of the unit case 3 is designated as the first damper side end surface 42C. ing. The first damper side end surface 42C extends outward in the radial direction from one end in the circumferential direction of the flange portion 41B, and is flush with the flange portion 41B.

On the other hand, the reheat prevention damper 43 extends in a direction generally opposite to that of the air mix damper main body 42 with the first support portion 41 interposed therebetween. That is, the reheat prevention damper 43 is provided at a distance from the air mix damper 4 in the circumferential direction of the first axis A1. The reheat prevention damper 43 extends in a direction biased toward the air mix space 91 side with respect to the extending plane of the air mix damper main body 42. Like the air mix damper main body 42, the reheat prevention damper 43 also has a plate shape extending in the radial direction of the first axis A1 from the first support portion 41. Further, the surface connecting both sides of the reheat prevention damper 43 in the circumferential direction and facing the side wall portion 30 (inner side surface 30A) of the unit case 3 is the second damper side end surface 43C. The second damper side end surface 43C extends radially outward with respect to the first axis A1 from the end surface on the other side in the circumferential direction of the flange portion 41B, and is flush with the collar portion 41B and the first damper side end surface 42C. Is doing.

In addition, as shown in FIG. 2 or 3, on the first damper plate surface 42A of the air mix damper main body 42, a plurality extending along a plane intersecting the radial direction and the circumferential direction with respect to the first axis A1. Ribs 44 are provided. In the present embodiment, the three ribs 44 are arranged on the first damper plate surface 42A at intervals in the extending direction of the first axis A1. As shown in FIG. 2, each rib 44 has a substantially rectangular shape when viewed from the extending direction of the first axis A1.

Further, as shown in FIG. 3, sponge seals 45 as elastic members are attached to the peripheral portions of the air mix damper main body 42 and the reheat prevention damper 43, which face both sides in the circumferential direction. The sponge seal 45 exerts a buffering action when the air mix damper main body 42 and the reheat prevention damper 43 come into contact with other members, and seals fluid leakage with the other members. Provided.

The air mix damper 4 configured as described above can rotate between the position shown by the solid line in FIG. 1 (maximum cooling position Pc) and the position shown by the broken line in the figure (maximum heating position Ph). It is said that. At the maximum cooling position Pc, the tip of the air mix damper body 42 (the end opposite to the first support 41) is from the air mix space 91 side with respect to the second end t2 of the warm air discharge port 84. Contact. At the same time, the reheat prevention damper 43 is held at a position substantially facing the first end portion t1 of the warm air discharge port 84 from the first support portion 41 in the vertical direction. As a result, at the maximum cooling position Pc, the cooling space 7 and the heating space 8 are partitioned by the air mix damper main body 42, and the cooling space 7 and the air mix space 91 are communicated with each other. Further, at this time, a gap is formed in the vertical direction between the tips of the air mix damper 4 and the foot switching damper 5.

On the other hand, at the maximum heating position Ph, the tip end portion of the air mix damper main body 42 comes into contact with the third end portion t3 of the guide partition wall portion 10 from the air mix space 91 side. At the same time, the reheat prevention damper 43 comes into contact with the upper end of the heater core 2 from the return space 83 side. As a result, the cooling space 7 and the heating space 8 are communicated with each other, and the heating space 8 and the air mix space 91 are communicated with each other via the return space 83.

Here, as shown in FIG. 4, the unit case 3 has a ridge 31 capable of contacting the first damper plate surface 42A of the air mix damper main body 42 at the maximum cooling position Pc, and a maximum heating position Ph. A contact portion 32 capable of contacting the second damper plate surface 42B of the air mix damper main body 42 is provided. The ridge 31 projects from the inner surface 30A of the unit case 3 in the direction of the first axis A1. Further, the ridge 31 extends in the radial direction of the first axis A1. More specifically, in the present embodiment, the ridge 31 extends in a direction including a radial component with respect to the first axis A1. In other words, the ridge 31 may be slightly angled with respect to the radial direction of the first axis A1.

Further, the ridge 31 has a first portion 31A forming a radial outer portion with respect to the first axis A1 and a second portion 31B forming a radial inner portion. The second portion 31B is bent at a slight angle with respect to the direction in which the first portion 31A extends. That is, the second portion 31B extends from the first portion 31A toward the other side in the circumferential direction toward the inner side in the radial direction.

Further, as shown in FIG. 5, the radial inner end portion of the second portion 31B has a slight radial interval d1 with respect to the outer peripheral surface (periphery of the bearing hole H) of the first support portion 41. Are facing each other. Seen from the radial direction with respect to the first axis A1, the dimension of this interval d1 is also smaller than the dimension of the flange portion 41B in the radial direction. In other words, the dimension of the interval d1 is smaller than the radial thickness of the flange portion 41B.

The contact portion 32 is provided at a position separated from the above-mentioned ridge 31 in the circumferential direction of the first axis A1. Specifically, the abutting portion 32 projects from the inner side surface 30A of the unit case 3 in the direction of the first axis A1 and extends in the radial direction of the first axis A1, similarly to the ridge 31.

When the air mix damper 4 is in the maximum cooling position Pc, the first damper plate surface 42A of the air mix damper main body 42 is peripheral to the first axis A1 via the sponge seal 45 with respect to the protrusion 31. Contact from the other side of the direction. On the other hand, when the air mix damper main body 42 is at the maximum heating position Ph, the second damper plate surface 42B of the air mix damper main body 42 is the first axis line via the sponge seal 45 with respect to the contact portion 32. The contact is made from one side in the circumferential direction of A1. In other words, the ridge 31 and the contact portion 32 define the rotation angle range θ1 of the first support portion 41.

Further, the angle range of the region where the flange portion 41B is not formed in the first support portion 41 (the angle range centered on the first axis A1) coincides with the rotation angle range θ1 of the first support portion 41. ing. That is, when the first support portion 41 rotates, the flange portion 41B, the ridge 31, and the contact portion 32 do not interfere with each other.

In the air mix space 91, a foot outlet flow path 92 is formed by the inner wall of the unit case 3 in a region substantially facing the guide partition wall portion 10 from the traveling direction (that is, above the heating space 8). There is. The foot outlet flow path 92 communicates with a foot outlet (not shown) for sending air to the feet of the passenger inside the vehicle.

The end of the foot outlet flow path 92 (the end on the air mix space 91 side) is a foot introduction port E1 for introducing air from the air mix space 91. The foot introduction port E1 is an opening that generally extends in the vertical direction in a cross-sectional view. The upper end of the foot introduction port E1 is the fifth end t5, and the lower end is the sixth end t6.

A foot switching damper 5 is provided at the foot introduction port E1. The foot switching damper 5 is a plate-shaped member that is rotatably supported on the foot introduction port E1. More specifically, the foot switching damper 5 has a second support portion 51 that rotates around the second axis A2 extending in the width direction of the vehicle and a plane that intersects the width direction with the second support portion 51 in between. It has a foot switching damper main body 52 extending to. The foot switching damper main body 52 extends by the dimension from the fifth end portion t5 to the sixth end portion t6 of the foot introduction port E1. Further, the foot switching damper main body 52 extends by the dimension from the second support portion 51 to the upper end portion (fourth end portion t4) of the guide partition wall portion 10. In other words, the dimensions from the second support portion 51 (second axis A2) to the fourth end portion t4 and the dimensions from the second support portion 51 to the sixth end portion t6 are substantially the same.

The foot switching damper 5 configured as described above is rotatable between the position shown by the solid line in FIG. 1 (blocking position Ps) and the position shown by the broken line in FIG. 1 (communication position Pt). ing. At the closed position Ps, both ends of the foot switching damper main body 52 come into contact with the fifth end t5 and the sixth end t6 of the foot blowing flow path 92. As a result, at the closed position Ps, the air mix space 91 and the foot blowout flow path 92 are partitioned by the foot switching damper main body 52, and the air mix space 91 and the foot blowout flow path 92 are communicated with each other.

On the other hand, at the communication position Pt, the end portion of the foot switching damper main body 52 comes into contact with the fourth end portion t4 of the guide partition wall portion 10 from the air mix space 91 side. As a result, the air mix space 91 and the relay space 93 described later are partitioned, and the air mix space 91 and the foot outlet flow path 92 are communicated with each other.

Yet another space is formed above the air mix space 91. This space is referred to as a relay space 93. The relay space 93 is a space for distributing the air supplied from the air mix space 91 toward the differential blowout flow path 95 and the face blowout flow path 94, which will be described later.

In the region generally facing the foot introduction port E1 from the traveling direction (that is, the region above the cooling space 7 and communicating with the relay space 93), the differential outlet flow path 95 is provided by the inner wall of the unit case 3. It is formed. The differential outlet flow path 95 communicates with a defroster outlet (not shown) for sending air for defrosting (defrosting) from the inside of the vehicle toward the windshield (front window).

The end of the differential outlet flow path 95 (the end on the relay space 93 side) is a differential introduction port E2 for introducing air from the relay space 93. The differential introduction port E2 is an opening that generally expands in the vertical direction in a cross-sectional view. The upper end of the differential introduction port E2 is the seventh end t7, and the lower end is the eighth end t8.

A face differential switching damper 6 is provided at the differential introduction port E2. The face differential switching damper 6 is a plate-shaped member that is rotatably supported on the differential introduction port E2. More specifically, the face differential switching damper 6 is placed on a third support portion 61 that rotates around the third axis A3 extending in the width direction of the vehicle and a plane that intersects the width direction from the third support portion 61. It has an extended face differential switching damper main body 62. The face differential switching damper main body 62 extends by the dimension from the seventh end portion t7 to the eighth end portion t8 of the differential introduction port E2.

Further, the face differential switching damper main body 62 extends by the dimension from the third support portion 61 to the fifth end portion t5 of the foot introduction port E1. In other words, the dimensions from the third support portion 61 (third axis A3) to the fifth end portion t5 and the dimensions from the third support portion 61 to the eighth end portion t8 are substantially the same.

Yet another space is formed above the relay space 93. This space is referred to as a face outlet flow path 94. The face outlet flow path 94 is a flow path for taking in the air supplied from the relay space 93 and sending it to the face outlet (not shown) provided in the living space of the vehicle. The face outlet is provided mainly for sending cold air or hot air toward the upper body of the occupant.

The face differential switching damper 6 is rotatable between the face position Pf shown by the solid line in FIG. 1 and the differential position Pd shown by the broken line in the figure. At the face position Pf, the tip end portion of the face differential switching damper main body 62 comes into contact with the eighth end portion t8 of the differential introduction port E2 from the relay space 93 side. As a result, the differential outlet flow path 95 and the relay space 93 are partitioned, and the relay space 93 and the face outlet flow path 94 are communicated with each other.

On the other hand, at the differential position Pd, the tip end portion of the face differential switching damper main body 62 comes into contact with the fifth end portion t5 of the foot introduction port E1 from the relay space 93 side. As a result, the differential outlet flow path 95 and the relay space 93 are communicated with each other, and the relay space 93 and the face outlet flow path 94 are partitioned.

Under the above configuration, by rotating the air mix damper 4, the foot switching damper 5, and the face differential switching damper 6, the cold air from the cooling space 7 and the hot air from the heating space 8 are combined. The mixing ratio is adjusted, and the distribution state of air to each flow path (foot blowout flow path 92, differential blowout flow path 95, and face blowout flow path 94) is switched.

First, a case where the vehicle air conditioner 100 is cooled (during maximum cooling operation) will be described. At the time of maximum cooling, as shown by the solid line in FIG. 1, the air mix damper 4 is held at the above-mentioned maximum cooling position Pc. More specifically, the tip of the air mix damper main body 42 is held in contact with the second end t2 of the warm air discharge port 84, and the tip of the reheat prevention damper 43 is warm air. It is held in a state of being vertically opposed to the first end portion t1 of the discharge port 84.

As described above, the cooling space 7 and the heating space 8 are partitioned by the air mix damper 4, and the cooling space 7 and the air mix space 91 are communicated with each other. In such a state, air is sent from a fan (not shown) into the cooling space 7. The air introduced into the cooling space 7 is endothermic when it comes into contact with the evaporator 1 from the introduction space 71 side and becomes cold air. This cold air flows into the air mix space 91 that communicates with the cooling space 7 (cold air supply space 72) by the air blown from the fan. Further, after circulating upward from the air mix space 91, any of the face blowing flow path 94, the differential blowing flow path 95, and the foot blowing flow path 92 depends on the positions of the foot switching damper 5 and the face differential switching damper 6. Guided towards one or the other.

Specifically, when the foot switching damper 5 is at the closed position Ps shown by the solid line in FIG. 1, the foot switching damper main body 52 partitions the air mix space 91 and the foot outlet flow path 92, and the air mix space. The 91 and the foot outlet flow path 92 are communicated with each other. As a result, the cold air supplied from the cooling space 7 does not flow into the foot blowing flow path 92, but flows toward the relay space 93. The air flowing in the relay space 93 flows toward one of the face blowout flow path 94 and the differential blowout flow path 95 according to the position of the face differential switching damper 6 (face position Pf or differential position Pd).

When the foot switching damper 5 is at the closed position Ps and the face differential switching damper 6 is at the face position Pf, the air flowing in the relay space 93 flows toward the face blowing flow path 94. On the other hand, when the face differential switching damper 6 is at the differential position Pd, the air flowing in the relay space 93 flows toward the differential outlet flow path 95.

Subsequently, a case where the vehicle air conditioner 100 is heated (during maximum heating operation) will be described. At the time of maximum heating, as shown by the broken line in FIG. 1, the air mix damper 4 is held at the above-mentioned maximum heating position Ph. More specifically, the tip end portion of the air mix damper main body 42 comes into contact with the third end portion t3 of the guide partition wall portion 10 from the air mix space 91 side. At the same time, the reheat prevention damper 43 comes into contact with the upper end of the heater core 2 from the return space 83 side.

As described above, the cooling space 7 and the heating space 8 are communicated with each other, and the heating space 8 and the air mix space 91 are communicated with each other via the return space 83. In such a state, air is sent from a fan (not shown) into the cooling space 7. The air introduced into the cooling space 7 flows into the heating space 8 communicated with the cooling space 7 from the second introduction space 81 side by the air blown from the fan. This air becomes warm air by contacting the heater core 2 in the heating space 8 and receiving heat. Further, the warm air flows upward along the heating space 8 (warm air supply space 82), passes through the return space 83, and then flows into the air mix space 91 communicated with the return space 83.

The warm air that has flowed into the air mix space 91 circulates further upward, and then, as described above, the face outlet flow path 94 and the differential outlet are blown out according to the positions of the foot switching damper 5 and the face differential switching damper 6. It flows toward any one of the flow path 95 and the foot blowout flow path 92.

The air mix damper 4 can freely rotate between the maximum cooling position Pc and the maximum heating position Ph described above. That is, by holding the air mix damper at an intermediate position between the maximum cooling position Pc and the maximum heating position Ph, the mixing ratio of the cold air and the hot air is appropriately adjusted. More specifically, when the air mix damper 4 is held at a position biased to the maximum cooling position Pc, relatively low temperature air can be supplied to the inside of the vehicle. On the other hand, when the air mix damper 4 is held at a position biased to the maximum heating position Ph, relatively high temperature air can be supplied to the inside of the vehicle.

By the way, during the above-mentioned maximum heating operation, careless flow of fluid between the heater core 2 and the evaporator 1 is performed in order to improve the thermal efficiency (improve the heating efficiency) and to make the temperature distribution inside the vehicle uniform. It needs to be suppressed. That is, it is necessary to reduce the possibility that the amount of heat from the heater core 2 is taken away by the air (cold air) cooled by the evaporator 1. In particular, around the first support portion 41 of the air mix damper 4 described above, it is required to secure a movable range of the first support portion 41 and suppress fluid leakage.

Therefore, in the vehicle air conditioner 100 according to the present embodiment, the flow (leakage) of the fluid around the first support portion 41 is blocked by the second portion 31B of the ridge 31 described above. Specifically, the radial inner end of the ridge 31 (second portion 31B) has a slight radial distance d1 with respect to the outer peripheral surface (periphery of the bearing hole H) of the first support portion 41. Open and face each other. Seen from the radial direction with respect to the first axis A1, the dimension of this interval d1 is also smaller than the dimension of the flange portion 41B in the radial direction (see FIG. 5).

According to such a configuration, the radial distance between the radial inner end of the ridge 31 and the bearing hole H is smaller than the radial dimension of the flange portion 41B. This makes it possible to reduce the possibility of fluid leaking from the gap between the radial inner end of the ridge 31 and the rotating shaft portion.
On the other hand, when the radial distance between the radial inner end of the ridge 31 and the bearing hole H is larger than the radial dimension of the flange portion 41B, the rotation shaft portion is displaced in the axial direction. The above gap becomes large. This can cause fluid to leak through the gap. However, according to the above configuration, such a possibility can be reduced.

Further, since the leakage of the fluid (air) around the first support portion 41 can be reduced, the temperature distribution of the air in the direction of the first axis A1 can be made uniform. Here, when air leaks on both sides of the air mix damper 4 in the direction of the first axis A1, the air supplied from the air outlets located on both sides in the width direction of the vehicle is mixed with the cold air from the cooling space 7. Therefore, there is a possibility that the temperature will be lower than that of the wind supplied from another air outlet (air outlet located in the center in the width direction). That is, there is a possibility that the temperature distribution of the wind will be biased in the width direction of the vehicle (A1 direction of the first axis line).

However, in the present embodiment, air leaks from both sides of the first support portion 41 in the width direction due to the ridges 31 (second portion 31B) provided on the inner side surfaces 30A of the unit case 3 located on both sides in the width direction. Is suppressed. As a result, the temperature distribution of air can be made uniform. That is, the efficiency of the vehicle air conditioner 100 can be sufficiently improved.

In particular, in the present embodiment, the second portion 31B of the ridge 31 is angled (bent) with respect to the first portion 31A in the circumferential direction of the first axis A1. According to such a configuration, the second portion 31B can be extended in the radial direction of the bearing hole H (first axis A1) regardless of the extending direction of the first portion 31A. That is, the dimension of the second portion 31B in the radial direction can be made as small as possible, and air leakage can be suppressed as described above. On the other hand, when the radial dimension of the second portion 31B is larger than the above, the second portion 31B may interfere with other members as the first support portion 41 rotates. That is, the rotation angle range of the first support portion 41 may be limited. However, in the present embodiment, since the second portion 31B is minimized by bending with respect to the first portion 31A, the possibility of such interference can be reduced.

Further, according to the above configuration, by providing the reheat prevention damper 43 as the second damper main body, it is possible to secure a larger dimension of the entire damper. Therefore, in changing and guiding the flow of the fluid flowing in the unit case 3, even when the cross-sectional area of the flow path of the fluid is large, it is possible to sufficiently cope with it.

In addition, according to the above configuration, the angle range of the region where the flange portion 41B is not formed coincides with the rotation angle range of the rotation shaft portion. As a result, when the first support portion 41 as the rotation shaft portion rotates, it is possible to prevent the flange portion 41B from interfering with the ridge 31 and the contact portion 32. That is, according to the above configuration, it is possible to suppress the leakage of fluid from the periphery of the first support portion 41, and it is possible to secure a sufficiently large rotation angle range of the first support portion 41.

The embodiments of the present invention have been described above with reference to the drawings. Various changes and modifications can be made to the above configuration without departing from the gist of the present invention.

For example, in the above embodiment, the second portion 31B of the ridge 31 has been described based on an example in which the second portion 31B of the ridge 31 extends from the outer side in the radial direction of the first axis A1 toward the other side in the circumferential direction. However, the aspect of the second part 31B is not limited to this. That is, contrary to the above, the second portion 31B of the ridge 31 may extend toward one side in the circumferential direction from the radial outside to the inside of the first axis A1.

Further, in the above embodiment, the vehicle air conditioner 100 is arranged in the width direction of the vehicle. However, the direction and posture in which the vehicle air conditioner 100 is arranged are not limited by the above-described embodiment, and can be appropriately changed according to the design and specifications.

In addition, in the above embodiment, the description is based on the configuration including the face blowing flow path 94, the differential blowing flow path 95, and the foot blowing flow path 92 as the flow paths communicating with the air mix space 91. However, the mode of these flow paths is not limited to the above embodiments. For example, in addition to the above-mentioned flow paths, other flow paths for sending air toward the rear seats of the vehicle or the like may be provided.

Furthermore, these flow paths, the extending direction and dimensions of each damper, and the relative positional relationship of each part are not limited by the above-described embodiment, and may be appropriately changed according to the design and specifications.

1 ... Evaporator 2 ... Heater core 3 ... Unit case 4 ... Air mix damper 5 ... Foot switching damper 6 ... Face differential switching damper 7 ... Cooling space 8 ... Heating space 10 ... Guide partition wall 30 ... Side wall 30A ... Inner surface 31 ... Crash Article 32 ... Contact part 31A ... First part 31B ... Second part 41 ... First support part 41B ... Flange part 41S ... Insertion shaft 42 ... Air mix damper body 42A ... First damper plate surface 42B ... Second damper plate surface 42C … First damper side end face 43… Reheat prevention damper 43C… Second damper side end face 44… Rib 45… Sponge seal 51… Second support 52… Foot switching damper body 61… Third support 62… Face differential switching damper Main body 71 ... Introduction space 72 ... Cold air supply space 73 ... Cold air discharge port 81 ... Second introduction space 82 ... Warm air supply space 83 ... Return space 84 ... Warm air discharge port 91 ... Air mix space 92 ... Foot outlet flow path 93 ... Relay space 94 ... Face outlet flow path 95 ... Diff outlet flow path 100 ... Vehicle air conditioner A1 ... First axis A2 ... Second axis A3 ... Third axis E1 ... Foot introduction port E2 ... Diff introduction port H ... Bearing hole Pc ... Maximum cooling position Pd ... Diff position Pf ... Face position Ph ... Maximum heating position Ps ... Blocking position Pt ... Communication position t1 ... First end t2 ... Second end t3 ... Third end t4 ... Fourth end t5 ... Fifth end t6 ... Sixth end t7 ... Seventh end t8 ... Eighth end

Claims (2)

A damper having a rotating shaft portion extending in the axial direction and an insertion shaft formed at an end portion in the axial direction, and a plate-shaped first damper body extending from the rotating shaft portion in the radial direction of the axis. ,
A unit case having a side wall portion in which the damper is housed and a bearing hole is formed into which the insertion shaft is rotatably inserted is provided.
The rotating shaft portion has a flange portion that is provided only in a part of the circumferential direction of the axis and projects radially outward from the base end of the insertion shaft.
The first damper main body is radially outward from the first damper plate surface facing one side in the circumferential direction, the second damper plate surface facing the other side in the circumferential direction, and the end portion on one side in the circumferential direction of the collar portion. It has a first damper side end face that extends toward and is flush with the collar.
The side wall portion is an inner side surface where the flange portion and the end surface on the first damper side can be brought into contact with each other from the axial direction, and the side wall portion projects from the inner side surface in the axial direction and extends in the radial direction of the axis, and the first damper. The first damper plate surface of the main body has a ridge that can be contacted from the other side in the circumferential direction.
The radial distance between the radial inner end of the ridge and the bearing hole is smaller than the radial dimension of the collar.
The damper is
It has a plate-shaped second damper body that is provided at a distance from the first damper body in the circumferential direction and extends from the rotating shaft portion in the radial direction of the axis.
The second damper body is
Have a second damper end surface forming the flange portion and said first damper-side end surface flush with and extending radially outward from an end portion of the other circumferential side of the flange portion,
With an evaporator that cools the air,
A heater core that heats the air and
Further prepare,
The unit case is internally formed with a cooling space for accommodating the evaporator, a heating space connected to the cooling space and accommodating the heater core, the cooling space, and an air mix space connected to the heating space.
The damper is provided in the air mix space in the unit case, and is introduced into the air mix space from the cooling space and the heating space by rotating between the maximum cooling position and the maximum heating position. An air mix damper that adjusts the proportion of air
The maximum cooling position is a position where the first damper main body and the second damper main body extend in a direction in which the cooling space and the heating space intersect in a separating direction to separate the cooling space from the heating space. ,
The maximum heating position is a vehicle air conditioner in which the first damper main body and the second damper main body extend in the direction of separation between the cooling space and the heating space to communicate the cooling space and the heating space. .. The ridge is
A first portion constituting the radial outer portion of the ridge and a radial inner portion of the ridge are formed, and one side in the circumferential direction and one side in the circumferential direction from the first portion further inward in the radial direction. The vehicle air conditioner according to claim 1, further comprising a second portion extending toward either side of the other side.

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