JP6696498B2 - Air conditioner - Google Patents

Description

  The present invention relates to a vehicle air conditioner.

  BACKGROUND ART Conventionally, there is known an air conditioner with a humidifier in which a waterless humidifier that can operate without water supply is installed in contrast to an air conditioner that performs air conditioning in a vehicle interior.

  In the air conditioner with a humidifier described in Patent Document 1, a waterless humidifier is arranged below the air conditioning case forming the outer shell of the air conditioner. A hygroscopic material and a blower are provided inside the humidifier. The air conditioner with a humidifier introduces air, which has been cooled by an evaporator of the air conditioner and has a high relative humidity (hereinafter referred to as “recovered air”), by driving a blower provided in the humidifier. The moisture contained in the air is adsorbed on the hygroscopic material. Next, by driving a blower provided in the humidifier, air heated by the heater core of the air conditioner and having a lower relative humidity is introduced into the inside of the humidifier, and the moisture of the hygroscopic material is desorbed from the air. The air conditioner with a humidifier can blow the air thus humidified toward the occupant's face through a duct connected to the humidifier.

JP, 2005-217917, A

  The air conditioner with a humidifier described in Patent Document 1 described above introduces the collected air into the humidifier from a collected air outlet provided between the evaporator and the heater core on the bottom wall of the ventilation passage. However, in the space near the bottom wall of the ventilation passage in which the collected air outlet is provided, the internal pressure changes greatly depending on the opening of the air mix door. Therefore, this air conditioner with a humidifier has a problem that it becomes difficult to introduce a stable amount of collected air into the humidifier when the opening degree of the air mix door changes.

  Further, in this air conditioner with a humidifier, the amount of collected air introduced into the humidifier from the ventilation passage can be adjusted by controlling the drive of the blower provided inside the humidifier. However, this air conditioner with a humidifier has a problem in that a blower is provided inside the humidifier, so that the manufacturing cost increases and the size of the humidifier increases.

  In view of the above points, an object of the present invention is to provide an air conditioner with a humidifier, which is capable of supplying recovered air with a stable air volume to a hygroscopic material.

In order to achieve the above object, the invention according to claim 1 is an air conditioner for air conditioning in a vehicle interior,
An air-conditioning case (2) forming an air passage (10) through which air flows,
A cooling device (4) for cooling the air flowing through the ventilation passage,
A heating device (5) arranged downstream of the cooling device for heating the air flowing through the ventilation passage;
An air mix door (17) which is provided between the cooling device and the heating device and which adjusts the ratio of the amount of air that bypasses the heating device after passing through the cooling device and the amount of air that passes through the heating device;
A housing section (25) for housing a hygroscopic material (6) capable of adsorbing and desorbing water contained in air;
A collection wind passage (41) that connects the collection wind outlet (40) provided between the cooling device and the heating device on the side wall (200) of the ventilation passage and the housing portion;
The collected air intake port is provided on a side wall of the ventilation passage at a position including a height range in which the heating device is projected perpendicularly to the cooling device (hereinafter, referred to as “heating device projection range”).

  The inventor has found by simulation that the space in the heating device projection range of the ventilation passage has a smaller change in internal pressure depending on the opening degree of the air mix door than the space above and below the space. It was Therefore, by providing the recovery wind outlet at a position that includes the heating device projection range on the side wall of the ventilation passage, the influence of the opening degree of the air mix door is reduced, and the recovery wind outlet stabilizes the storage unit through the recovery wind passage. It is possible to supply the collected air of the specified air volume. Therefore, in this air conditioner, moisture can be stably held in the hygroscopic material, and the humidified air can be stably blown from the humidifier to the occupant.

  In addition, according to the simulation, when the air passing through the cooling device bypasses the heating device due to the operation of the air mix door, the space in the heating device projection range is larger than when the air passing through the cooling device passes through the heating device. The internal pressure of is low. However, even when the air passing through the cooling device bypasses the heating device due to the operation of the air mix door, the internal pressure of the space in the heating device projection range is higher than the internal pressure of the space above and below the space. Therefore, it is possible to secure a minimum collected air volume with a relatively large air volume by providing the recovered air outlet at a position including the heater core projection range on the side wall of the ventilation passage. Therefore, it is possible to reduce the flow passage cross-sectional areas of the collected air intake port and the collected air passage, and to reduce the size of the air conditioner.

  In addition, the reference numerals in parentheses attached to the above-described respective components show an example of a correspondence relationship with a specific configuration described in an embodiment described later.

It is a front view of the air conditioner of a 1st embodiment. FIG. 2 is a side view of the temperature adjustment unit and the humidifier of the air conditioner taken along the line II-II of FIG. 1. FIG. 3 is a cross-sectional view of the temperature adjustment unit and the humidifier of the air conditioner taken along the line III-III of FIG. 1. FIG. 4 is a cross-sectional view of the temperature adjustment unit and the humidifier of the air conditioner taken along the line IV-IV of FIG. 3. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is a graph which shows the relationship between the opening of an air mixing door, and the internal pressure of a ventilation path. It is a graph which shows the relationship between the opening of an air mix door, and the air volume of collection wind. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 2nd Embodiment is equipped. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 3rd Embodiment is equipped. It is an enlarged view of the XII part of FIG. It is a perspective view of the conical door provided in the accommodation part of an air conditioner. It is a front view of the conical door provided in the accommodation part of an air conditioner. FIG. 15 is a sectional view taken along line XV-XV in FIG. 14. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 4th Embodiment is equipped. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is a graph which shows the relationship between the opening of an air mixing door, and the internal pressure of a ventilation path. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 5th Embodiment is equipped. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is explanatory drawing explaining operation | movement of an air mixing door. It is a graph which shows the relationship between the opening of an air mixing door, and the internal pressure of a ventilation path. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 6th Embodiment is equipped. It is sectional drawing of the temperature adjustment unit and humidifier with which the air conditioning apparatus of 7th Embodiment is equipped.

  Embodiments of the present invention will be described below with reference to the drawings. In each of the following embodiments, the same or equivalent portions will be denoted by the same reference numerals for description.

(First embodiment)
The first embodiment will be described with reference to the drawings. The air conditioner of this embodiment is mounted inside an instrument panel of a vehicle. This air conditioner adjusts the temperature and humidity of the air taken in from inside or outside the vehicle, and blows out the air into the vehicle from a plurality of outlets provided in the vehicle to adjust the air inside the vehicle. Is. In addition, this air conditioner can also blow humidified air toward a passenger's face or the like from a predetermined outlet provided in the vehicle compartment without requiring water supply.

  As shown in FIGS. 1 to 4, the air conditioner 1 includes an air conditioning case 2, a blower 3, an evaporator 4 as a cooling device, a heater core 5 as a heating device, a hygroscopic material 6, and the like.

  The air conditioning case 2 constitutes an outer shell of the air conditioning device 1. The air-conditioning case 2 is formed of a resin (for example, polypropylene) that has elasticity to some extent and is also excellent in strength. An air passage 10 through which air flows is formed inside the air conditioning case 2.

  A partition plate 13 is provided inside the air conditioning case 2 to partition the ventilation passage 10 into an upper ventilation passage 11 on the upper side in the gravity direction and a lower ventilation passage 12 on the lower side in the gravity direction.

  The air-conditioning case 2 has an inside air introduction port 14 for introducing air into the vehicle interior air (that is, the inside air) into the ventilation passage 10 and an outside air passage (that is, outside air) into the ventilation passage 10 on the most upstream side in the air flow direction of the ventilation passage 10. It has an outside air introduction port 15 for introducing it into the air conditioner 10. The inside air introduction port 14 and the outside air introduction port 15 are connected to a duct (not shown) configured as a separate member from the air conditioning case 2. Air is introduced into the upper ventilation passage 11 and the lower ventilation passage 12 from the inside air introduction port 14 or the outside air introduction port 15 via these ducts.

  An inside / outside air switching door 16 as an inside / outside air switching unit is provided near the inside air introducing port 14 and the outside air introducing port 15. The inside / outside air switching door 16 opens / closes the inside air introduction port 14 and the outside air introduction port 15. The inside / outside air switching door 16 may be provided with a door for opening / closing the inside air introducing port 14 and a door for opening / closing the outside air introducing port 15 separately.

  The air conditioner 1 of the present embodiment can switch the air conditioning mode for introducing outside air or inside air into the upper ventilation passage 11 and the lower ventilation passage 12 by rotating the inside / outside air switching door 16 to a desired position. It is possible. As this air conditioning mode, an outside air mode, an inside air mode, and an inside / outside air two-layer mode can be set.

  In the outside air mode, the inside / outside air switching door 16 opens the outside air introduction port 15 and closes the inside air introduction port 14. At this time, the outside air introduction port 15, the upper ventilation passage 11, and the lower ventilation passage 12 communicate with each other. As a result, outside air is introduced into the upper ventilation passage 11 and the lower ventilation passage 12.

  In the inside air mode, the inside air / outside air switching door 16 closes the outside air introduction port 15 and opens the inside air introduction port 14. At this time, the inside air introduction port 14, the upper ventilation passage 11, and the lower ventilation passage 12 communicate with each other. Thereby, the inside air is introduced into the upper ventilation passage 11 and the lower ventilation passage 12.

  In the inside / outside air two-layer mode, both the outside air introduction port 15 and the inside air introduction port 14 are opened by the inside / outside air switching door 16. At this time, the outside air introduction port 15 and the upper ventilation passage 11 communicate with each other, and the inside air introduction port 14 and the lower ventilation passage 12 communicate with each other. As a result, the outside air is introduced into the upper ventilation passage 11 and the inside air is introduced into the lower ventilation passage 12. Note that FIG. 1 shows the position of the inside / outside air switching door 16 when the inside / outside air two-layer mode is selected.

  A blower 3 is provided in the ventilation path 10 inside the air conditioning case 2. The blower 3 has a first centrifugal fan 31, a second centrifugal fan 32, an electric motor (not shown), and the like. By driving the electric motor, the first centrifugal fan 31 and the second centrifugal fan 32 rotate, and air is introduced into the upper air passage 11 and the lower air passage 12 from the inside air introduction port 14 or the outside air introduction port 15. The air blown by the first centrifugal fan 31 flows through the upper ventilation passage 11, and the air blown by the second centrifugal fan 32 flows through the lower ventilation passage 12.

  The air flowing through the ventilation passage 10 has a defroster outlet opening 19, a face outlet opening 20, a foot outlet opening 21, an exhaust passage 43, or a humidifying air passage provided on the most downstream side in the air flow direction, depending on the air conditioning mode. Blow out from any of 44. The fan included in the blower 3 is not limited to the centrifugal fan, and may be, for example, an axial flow fan or a cross flow fan.

  The evaporator 4 is a heat exchanger that cools the air flowing through the ventilation passage 10. The evaporator 4 constitutes a vapor compression refrigeration cycle together with a compressor, a condenser, an expansion valve and the like which are not shown. The evaporator 4 is arranged downstream of the expansion valve and upstream of the compressor in the refrigeration cycle. In the tube (not shown) of the evaporator 4, the refrigerant decompressed by the expansion valve and in the gas-liquid two-layer state flows. The air flowing through the ventilation passage 10 is cooled by heat exchange between the refrigerant flowing inside the tube of the evaporator 4 and the air flowing through the ventilation passage 10.

  The heater core 5 is provided downstream of the evaporator 4 in the air flow direction. The heater core 5 is a heat exchanger that heats the air flowing through the ventilation passage 10. Hot water (for example, engine cooling water) flows inside a tube (not shown) of the heater core 5. The heat exchange between the hot water flowing inside the tube of the heater core 5 and the air flowing through the ventilation passage 10 heats the air flowing through the ventilation passage 10. A PCT heater or the like may be installed together with the heater core 5.

  In the ventilation path 10 between the evaporator 4 and the heater core 5, two air mix doors 17 are provided. The air mix door 17 is a slide type film door and is driven by rotation of a gear 18. The air mix door 17 adjusts the ratio of the air volume that bypasses the heater core 5 after passing through the evaporator 4 and the air volume that passes through the heater core 5 after passing through the evaporator 4.

  The air conditioning case 2 has a plurality of blowout openings for blowing conditioned air from the ventilation passage 10 into the vehicle interior on the most downstream side of the ventilation passage 10 in the air flow direction. The plurality of blowout openings are composed of a defroster blowout opening 19, a face blowout opening 20, a foot blowout opening 21, and the like.

  When the air conditioner 1 is mounted on a vehicle, the defroster blowout opening 19 and the face blowout opening 20 are provided in an upper portion of the air conditioning case 2 in the gravity direction. The face blowout opening 20 blows out the conditioned air toward the upper half of the occupant seated in the front seat. A face door 22 is provided near the face outlet 20. The face door 22 opens and closes the face outlet 20. A face duct (not shown) is connected to the face outlet 20. The face duct is a duct that connects the face outlet 20 and a face outlet (not shown) provided in the vehicle compartment. When the face door 22 opens the face outlet 20, the air-conditioning air flowing through the ventilation passage 10 passes from the face outlet 20 through the face duct and is blown from the face outlet toward the upper body of the occupant seated in the front seat. It

  The defroster blowout opening 19 blows out the conditioned air toward the windshield of the vehicle. A defroster door 23 is provided near the defroster outlet opening 19. The defroster door 23 opens and closes the defroster outlet opening 19. When the defroster door 23 opens the defroster outlet opening 19, the conditioned air flowing through the ventilation passage 10 is blown from the defroster outlet opening 19 through a defroster duct (not shown) toward the windshield of the vehicle.

  The foot blowout openings 21 are respectively provided at left and right portions in the vehicle width direction when the air conditioner 1 is mounted on the vehicle. The foot blowout opening 21 blows out conditioned air toward the lower body side of an occupant seated in the right front seat and the left front seat of the vehicle. A foot door 24 is provided at a place where the ventilation passage 10 and the foot outlet opening 21 communicate with each other. The foot door 24 connects or disconnects the ventilation passage 10 and the foot outlet 21. When the foot door 24 communicates the ventilation passage 10 and the foot outlet 21 with each other, the conditioned air flowing through the ventilation passage 10 is ejected from the foot outlet 21 toward the lower body side of the occupant.

  Furthermore, the air conditioner 1 of the present embodiment is provided with a storage portion 25 that can store the moisture absorbent material 6. Have In the present embodiment, the air conditioning case 2 and the housing portion 25 are configured as separate members. The air conditioning case 2 and the accommodating portion 25 may be integrally formed as in the third embodiment described later.

  The hygroscopic material 6 is housed in the housing space 26 formed inside the housing portion 25. The hygroscopic material 6 is a roll-shaped or rectangular parallelepiped in which a hygroscopic substance having a property of collecting moisture in the air according to the humidity of the air or desorbing moisture from the air is carried on a corrugated plate-shaped member. It is shaped. Further, the hygroscopic material 6 may be a honeycomb-shaped structure formed in a columnar shape or a rectangular parallelepiped shape and carrying the above-mentioned hygroscopic substance. As the above-mentioned hygroscopic substance, for example, a polymeric adsorbent of an organic material, or a zeolite or silica gel of an inorganic material can be adopted.

  As shown in FIGS. 3 and 4, the hygroscopic material 6 has an air inflow surface 61 and an air outflow surface 62. The air that has flowed in from the air inflow surface 61 of the moisture absorbent 6 flows through the gap of the structure formed inside the moisture absorbent 6 and flows out from the air outflow surface 62. In the following description, of the accommodation space 26 inside the accommodation unit 25, the space on the side where the air inflow surface 61 of the hygroscopic material 6 is arranged is called the inflow space 261, and the air outflow surface 62 of the hygroscopic material 6 is referred to as the inflow space 261. The space on the arranged side will be referred to as an outflow space 262. When the humidity of the air flowing through the accommodation space 26 from the inflow space 261 to the outflow space 262 is high, the hygroscopic material 6 recovers the moisture contained in the air. When the humidity of the air flowing through the accommodation space 26 from the inflow space 261 to the outflow space 262 is low, the moisture absorbent 6 desorbs water from the air.

  The collection air passage 41, the warm air passage 42, the exhaust passage 43, and the humidified air passage 44 are connected to the housing portion 25.

  The collected air passage 41 communicates the collected air outlet 40 provided in the side wall 200 of the ventilation passage 10 with the inflow space 261 of the housing portion 25. The collected air outlet 40 is an opening provided in the side wall 200 of the ventilation passage 10 for introducing the air cooled by the evaporator 4 and having a higher relative humidity into the collected air passage 41. The collected air passage 41 is a passage for taking out the air cooled by the evaporator 4 from the collected air outlet 40 and introducing the air into the inflow space 261 of the housing portion 25.

  The recovered air outlet 40 is provided between the evaporator 4 and the heater core 5 on the side wall 200 of the ventilation passage 10. Further, the collected air outlet 40 is provided at a position including a height range in which the heater core 5 is projected perpendicularly to the evaporator 4 (hereinafter, referred to as “heater core projection range HS”). At least a part of the collected wind outlet 40 may be provided in a position including the heater core projection range HS. The position including the heater core projection range HS includes not only the side of the evaporator 4 but also the position between the evaporator 4 and the heater core 5 on the side wall 200 of the ventilation passage 10. The side wall 200 of the ventilation path 10 is a wall that intersects the gravity direction when the air conditioner 1 is mounted on a vehicle, and includes not only a wall in the vehicle width direction but also a wall in the vehicle front-rear direction. Contains.

  In the space of the heater core projection range HS in the ventilation passage 10, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than the space above and below the space. Therefore, the effect of the opening degree of the air mix door 17 is reduced by providing the recovery air outlet 40 at a position including the heater core projection range HS on the side wall 200 of the air passage 10, and the recovery air passage 40 is recovered from the recovery air passage 40. It is possible to supply a stable amount of collected air to the accommodation portion 25 through 41. This will be described later in detail based on the simulation performed by the inventor.

  Further, the collected air intake 40 is provided on the side wall 200 of the lower ventilation passage 12. The lower ventilation passage 12 circulates the inside air when the inside / outside air two-layer mode or the inside air mode is performed. The air that circulates inside air has a high absolute humidity due to sweating of passengers. Therefore, by providing the recovery air outlet 40 on the side wall 200 of the lower ventilation passage 12 in which the inside air is circulated, the air having high absolute humidity and relative humidity is supplied from the recovery air outlet 40 to the accommodation portion 25 through the recovery air passage 41. It is possible to supply.

  Further, as shown in FIG. 4, the recovery air outlet 40 is provided on one side wall 200 of the ventilation passage 10 and the other side wall 200 of the ventilation passage 10. The recovered air intake 40 provided on one side wall 200 of the ventilation passage 10 is called a first recovered air intake 401, and the recovered air intake 40 provided on the other side wall 200 of the ventilation passage 10 is referred to as a second recovered air. It will be called an outlet 402. In addition, the collected wind passage 41 that communicates the first collected wind outlet 401 and the containing portion 25 is called a first collected wind passage 411, and the collected wind passage 41 that communicates between the second collected wind outlet 402 and the containing portion 25. Will be referred to as the second recovery air passage 412. In this way, the collection wind passage 41 of the present embodiment is provided outside the one side wall 200 of the air conditioning case 2 with the first collection wind passage 411 and the other side wall 200 of the air conditioning case 2. The second recovery wind passage 412 is provided. Thereby, the temperature of the conditioned air blown from each of the blowout openings provided on the right side in the vehicle width direction of the air conditioning case 2 and the temperature of the conditioned air blown from each of the blowout openings provided on the left side of the vehicle width, and The balance of air volume is maintained.

  One end of the warm air passage 42 is opened to the downstream side of the heater core 5 in the ventilation passage 10, and the other end thereof is connected to the housing portion 25. The warm air passage 42 is a passage for introducing the air heated by the heater core 5 and having a low relative humidity into the inflow space 261 of the housing portion 25.

  The exhaust passage 43 has one end connected to the housing portion 25 and the other end opening to the outside of the housing portion 25. The exhaust passage 43 is a passage for exhausting air from the outflow space 262 of the housing portion 25.

  The humidified air passage 44 has one end connected to the housing portion 25 and the other end connected to a face outlet (not shown) provided in the vehicle compartment. The other end of the humidified air passage 44 may be connected to a humidified air outlet (not shown) provided in the vehicle compartment separately from the face outlet. The humidified air passage 44 is a passage for blowing out the air humidified in the accommodation space 26 toward the passenger compartment.

  In the inflow space 261 of the housing portion 25, a collected wind door 51 for communicating and blocking the collected air passage 41 and the housing space 26, and for communicating and blocking the warm air passage 42 and the housing space 26. A warm air door 52 is provided. Further, in the outflow space 262 of the housing portion 25, an exhaust door 53 for communicating and blocking the exhaust passage 43 and the housing space 26, and for communicating and blocking the humidification air passage 44 and the housing space 26. A humidifying air door 54 is provided.

  As shown in FIG. 3, when the collected wind door 51 and the exhaust door 53 are in the open state and the warm air door 52 and the humidified air door 54 are in the closed state, the collected wind passage 41 and the accommodation space 26 communicate with each other, and the exhaust passage 43 and the accommodation space 26 communicate with each other. Further, the warm air passage 42 and the accommodation space 26 are shut off, and the humidified air passage 44 and the accommodation space 26 are shut off.

  In this state, the air introduced into the accommodation space 26 from the recovery air passage 41 flows through the moisture absorbent 6 from the air inflow surface 61 of the moisture absorbent 6. As a result, the moisture contained in the air introduced into the accommodation space 26 from the recovery air passage 41 is adsorbed by the hygroscopic material 6. Then, the air that has passed through the hygroscopic material 6 and has reduced humidity is discharged from the exhaust passage 43 to the outside of the air conditioning case 2.

  On the other hand, when the warm air door 52 and the humidified air door 54 are open and the collected air door 51 and the exhaust door 53 are closed, the warm air passage 42 and the accommodation space 26 communicate with each other, and the humidified air passage 44 and the accommodation space 26 communicate with each other. 26 communicates. Further, the collected air passage 41 and the accommodation space 26 are shut off, and the exhaust passage 43 and the accommodation space 26 are shut off.

  In this state, the air introduced into the accommodation space 26 from the warm air passage 42 flows through the moisture absorbent 6 from the air inflow surface 61 of the moisture absorbent 6. As a result, the moisture contained in the hygroscopic material 6 is released to the air introduced into the accommodation space 26 from the warm air passage 42. The air that has passed through the hygroscopic material 6 and has increased in humidity passes through the humidified air passage 44 and is blown into the vehicle compartment from the face outlet or the humidified air outlet. As a result, the air conditioner 1 of the present embodiment can humidify the vehicle interior without supplying water.

  Next, the significance of providing the recovered air outlet 40 of the recovered air passage 41 at a position on the side wall 200 of the lower ventilation passage 12 between the evaporator 4 and the heater core 5 and including the heater core projection range HS will be described.

  FIG. 8 is a graph showing the relationship between the internal pressure of the ventilation passage 10 measured at the positions P1 to P4 shown in FIGS. 5 to 7 and the opening degree of the air mix door 17 based on the simulation. The positions of P2 and P3 shown in FIGS. 5 to 7 are positions in the ventilation path 10 including the heater core projection range HS. The positions of P1 and P4 shown in FIGS. 5 to 7 are positions in the ventilation path 10 that do not include the heater core projection range HS.

  In the graph of FIG. 8, the relationship between the internal pressure of the ventilation passage 10 and the opening degree of the air mix door 17 measured at the positions P1 and P4 is indicated by broken lines. The relationship between the internal pressure of the ventilation passage 10 and the opening degree of the air mix door 17 measured at the positions P2 and P3 is shown by a solid line.

  It can be seen from the graph of FIG. 8 that at any of the positions P1 to P4, the smaller the opening degree of the air mix door 17, the lower the internal pressure. However, at the positions of P2 and P3, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than that at the positions of P1 and P4. Even when the opening degree of the air mix door 17 is 0% and the internal pressure is the lowest, the internal pressures at the positions P2 and P3 are higher than the internal pressures at the positions P1 and P4.

  The above reason will be described. FIG. 5 shows a state in which the opening degree of the air mix door 17 is 0%. In this state, the air mix door 17 covers substantially the entire airflow inflow surface of the heater core 5 and opens the passages above and below the heater core 5. Therefore, almost all of the air that has passed through the evaporator 4 bypasses the heater core 5 and flows. At this time, the positions of P2 and P3 are higher in internal pressure than the positions of P1 and P4 because the air mix door 17 closes the heater core 5 on the downstream side.

  FIG. 6 shows a state in which the opening degree of the air mix door 17 is 50%. In this state, the air mix door 17 opens almost half of the airflow inflow surface of the heater core 5 and covers the other half. Therefore, the air that has passed through the evaporator 4 separately flows into the air that passes through the heater core 5 and the air that bypasses the heater core 5. At this time, the positions of P2 and P3 have a higher internal pressure than the positions of P1 and P4 due to the ventilation resistance of the heater core 5 on the downstream side.

  FIG. 7 shows a state in which the opening degree of the air mix door 17 is 100%. In this state, the air mix door 17 opens substantially the entire airflow inflow surface of the heater core 5 and closes the passages above and below the heater core 5. Therefore, almost all of the air that has passed through the evaporator 4 flows through the heater core 5. At this time, the air mix door 17 opens the heater core 5 on the downstream side of the positions of P2 and P3. On the other hand, on the downstream side of P1 and P4, the air mix door 17 closes the passage. Therefore, the positions of P1 and P4 have a higher internal pressure than the positions of P2 and P3 because the air mix door 17 closes the passage on the downstream side. Therefore, as described with reference to FIGS. 5 to 8, the positions of P2 and P3 have a smaller change in the internal pressure according to the opening degree of the air mix door 17 than the positions of P1 and P4. ..

  FIG. 9 shows the amount of collected wind flowing through the collected wind passage 41 and the opening degree of the air mix door 17 when the collected wind outlet 40 is provided on the side wall 200 of the ventilation passage 10 corresponding to each of the positions P1 to P4. It is a graph showing a relationship. In the graph of FIG. 9, in the case where the collected air outlet 40 is provided on the side wall 200 of the ventilation passage 10 corresponding to the position of P1 or P4, the amount of collected wind flowing through the collected air passage 41 and the opening degree of the air mix door 17 are shown. The relationship with and is shown by the broken line. Further, in the graph of FIG. 9, when the collected air outlet 40 is provided on the side wall 200 of the ventilation passage 10 corresponding to the position of P2 or P3, the amount of collected air flowing through the collected air passage 41 and the air mix door 17 are reduced. The relationship with the opening is shown by a solid line.

  As shown in FIG. 9, the amount of collected wind flowing through the collected wind passage 41 corresponds to the internal pressure of the ventilation passage 10 shown in FIG. 8. That is, compared with the case where the collected air outlet 40 is provided on the side wall 200 of the air passage 10 corresponding to the positions P1 and P4, the collected air outlet 40 is provided on the side wall 200 of the air passage 10 corresponding to the positions P2 and P3. In the case where is provided, the change in the amount of collected air according to the opening degree of the air mix door 17 is smaller. Therefore, by providing the recovery wind outlet 40 in a position including the heater core projection range HS on the side wall 200 of the ventilation passage 10, the influence of the opening degree of the air mix door 17 is reduced, and the recovery wind passage 40 is recovered from the recovery wind passage 40. It is possible to supply a stable amount of collected air to the accommodation portion 25 through 41.

  Further, as shown in FIG. 8 and FIG. 9, when the opening degree of the air mix door 17 is 0%, the internal pressure is low regardless of which position of P1 to P4 the recovery wind outlet 40 is provided. The volume of collected wind is the lowest. However, even in that case, the amount of collected wind when the collected wind outlet 40 is provided at the positions P2 and P3 is smaller than the amount of collected wind when the collected wind outlet 40 is provided at positions P1 and P4. It is big. Therefore, by providing the recovered air intake 40 at a position including the heater core projection range HS on the side wall 200 of the ventilation passage 10, it is possible to secure a minimum recovered air flow with a relatively large air flow.

  The operating range indicated by the arrows in FIGS. 8 and 9 is a range in which the humidifier is generally assumed to be used by an occupant. It is considered that the humidifier is often used from late autumn to winter to early spring. In that case, it is assumed that the air mix door 17 operates in the range of the operation range shown in FIGS. 8 and 9.

  The air conditioner 1 of the present embodiment described above has the following operational effects.

  (1) In the present embodiment, the recovery air outlet 40 of the recovery air passage 41 is provided in the side wall 200 of the lower ventilation passage 12 at a position between the evaporator 4 and the heater core 5 and including the heater core projection range HS. ing.

  According to this, in the space of the heater core projection range HS in the ventilation passage 10, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than the space above and below the space. Therefore, it is possible to reduce the influence of the opening degree of the air mix door 17 and supply the recovered air of a stable air volume from the recovered air outlet 40 to the accommodation portion 25 through the recovered air passage 41. Therefore, the air conditioner 1 can hold the moisture in the moisture absorbent 6 in a stable manner, and can stably blow out the humidified air from the humidifier to the occupant.

  In addition, even when the opening degree of the air mix door 17 is 0%, the internal pressure of the space in the heater core projection range HS is higher than the internal pressure of the space above and below the space. Therefore, it is possible to secure the minimum recovered air volume with a relatively large air volume by providing the recovered air outlet 40 at a position including the heater core projection range HS on the side wall 200 of the ventilation passage 10. Therefore, the flow passage cross-sectional areas of the collected wind outlet 40 and the collected wind passage 41 can be reduced, and the size of the air conditioner 1 can be reduced.

  (2) In the present embodiment, the collected wind outlet 40 is a first collected wind outlet 401 provided on one side wall 200 of the air conditioning case 2 and a second collected wind outlet 40 provided on the other side wall 200 of the air conditioning case 2. It has a recovery wind outlet 402.

  According to this, the air-conditioning air blown out from each of the air outlet cases provided on the right side in the vehicle width direction of the air-conditioning case 2 and the air-conditioning air blown from each air outlet opening provided on the left side of the vehicle width direction. The balance of temperature and air volume can be maintained.

  (3) In the present embodiment, the ventilation passage 10 in the air conditioning case 2 is divided by the partition plate 13 into an upper ventilation passage 11 on the upper side in the gravity direction and a lower ventilation passage 12 on the lower side in the gravity direction. Here, the collection wind outlet 40 is provided on the side wall 200 on the side of the lower ventilation passage 12.

  The lower ventilation passage 12 circulates the inside air when the inside / outside air two-layer mode or the inside air mode is performed. The air that circulates inside air has a high absolute humidity due to sweating of passengers. Therefore, by providing the recovery air outlet 40 on the side wall 200 of the lower ventilation passage 12 in which the inside air is circulated, the air having high absolute humidity and relative humidity is supplied from the recovery air outlet 40 to the accommodation portion 25 through the recovery air passage 41. It is possible to supply.

  (4) In the present embodiment, the air conditioner 1 further includes the warm air passage 42, the exhaust passage 43, and the humidified air passage 44.

  According to this, in the accommodating portion 25, it is possible to cause the moisture absorption material 6 to adsorb moisture from the collected air introduced from the collected air passage 41 and then to discharge the air through the exhaust passage 43. Further, the moisture introduced from the warm air passage 42 into the housing portion 25 can be desorbed from the hygroscopic material 6. The humidified air is blown out from the accommodation portion 25 into the vehicle compartment through the humidified air passage 44. Accordingly, the air conditioning case 2 can have the function of a non-water supply humidifier that can operate without water supply.

(Second embodiment)
The second embodiment will be described. In the second embodiment, the position of the heater core 5 is changed from that of the first embodiment, and the other points are the same as those of the first embodiment. Therefore, only the parts different from the first embodiment will be described.

  As shown in FIG. 10, in the second embodiment, the heater core 5 is provided in contact with the bottom wall 201 of the air conditioning case 2 or provided near the bottom wall 201. In addition, in 2nd Embodiment, the partition plate 13 is not provided and the ventilation path 10 is not partitioned into the upper ventilation path 11 and the lower ventilation path 12. That is, the air conditioner 1 does not set the inside / outside air two-layer mode. Further, one air mix door 17 is provided in the ventilation passage 10 between the evaporator 4 and the heater core 5.

  In the second embodiment as well, the collected air outlet 40 of the collected air passage 41 is provided in the side wall 200 of the ventilation passage 10 between the evaporator 4 and the heater core 5 at a position including the heater core projection range HS. In the space of the heater core projection range HS in the ventilation passage 10, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than that in the space above the space. Therefore, the effect of the opening degree of the air mix door 17 is reduced by providing the recovery air outlet 40 at a position including the heater core projection range HS on the side wall 200 of the air passage 10, and the recovery air passage 40 is recovered from the recovery air passage 40. It is possible to supply a stable amount of collected air to the accommodation portion 25 through 41.

  Even when the opening degree of the air mix door 17 is 0%, the internal pressure of the space in the heater core projection range HS is higher than the internal pressure of the space above the space. Therefore, it is possible to secure the minimum recovered air volume with a relatively large air volume by providing the recovered air outlet 40 at a position including the heater core projection range HS on the side wall 200 of the ventilation passage 10. Therefore, the flow passage cross-sectional areas of the collected wind outlet 40 and the collected wind passage 41 can be reduced, and the size of the air conditioner 1 can be reduced. Therefore, the second embodiment can also achieve the same effects as the first embodiment.

(Third Embodiment)
A third embodiment will be described. In the third embodiment, the configuration of the housing portion 25 is changed from that of the first embodiment, and the other points are the same as those of the first embodiment. Therefore, only the parts different from the first embodiment will be described.

  As shown in FIGS. 11 and 12, the housing portion 25 is configured integrally with the air conditioning case 2. The housing portion 25 has a tubular portion 27 formed in a tubular shape, a first conical portion 28 provided on one side of the tubular portion 27 in the axial direction, and a second conical portion provided on the other side of the tubular portion 27 in the axial direction. It is composed of a conical portion 29 and the like. The accommodating portion 25 is provided such that the apex 281 of the first conical portion 28 is lower than the apex 291 of the second conical portion 29 when the air conditioner 1 is mounted on the vehicle. The accommodating portion 25 is inclined with respect to the evaporator 4 so that the distance L1 between the apex 281 of the first conical portion 28 and the evaporator 4 is closer than the distance L2 between the apex 291 of the second conical portion 29 and the evaporator 4. Is provided.

  As shown in FIGS. 11 and 12, in the present embodiment, the collected air passage 41 and the warm air passage 42 are connected to the first conical portion 28. The exhaust passage 43 and the humidified air passage 44 are connected to the second conical portion 29. As shown in FIG. 12, the first conical portion 28 is provided with an opening 410 of the recovered air passage 41 and an opening 420 of the warm air passage 42. The second conical portion 29 is provided with an opening 430 of the exhaust passage 43 and an opening 440 of the humidified air passage 44.

  A first conical door 55 is provided inside the first conical portion 28 of the accommodation portion 25. A second conical door 56 is provided inside the second conical portion 29 of the accommodation portion 25. As shown in FIGS. 13 to 15, the first conical door 55 is formed in the shape of a conical umbrella and has an opening 550 in a part in the circumferential direction. The first conical door 55 is rotatably provided around the axis of the first conical portion 28. As shown in FIG. 12, when the opening 410 of the recovery wind passage 41 provided in the first conical portion 28 and the opening 550 of the first conical door 55 overlap each other, the recovery wind passage 41 and the accommodation space 26 are separated from each other. The warm air passage 42 and the accommodation space 26 are cut off by communication. On the other hand, when the opening 420 of the warm air passage 42 provided in the first conical portion 28 and the opening 550 of the first conical door 55 overlap, the warm air passage 42 communicates with the accommodation space 26, The collected air passage 41 and the accommodation space 26 are shut off from each other.

  Similarly to the first conical door 55, the second conical door 56 is also formed in the shape of a conical umbrella, and has an opening 560 in a part in the circumferential direction. The second conical door 56 is rotatably provided around the axis of the second conical portion 29. When the opening 440 of the humidified air passage 44 provided in the second conical portion 29 and the opening 560 of the second conical door 56 overlap with each other, the accommodation space 26 and the humidified air passage 44 communicate with each other and the accommodation space 26 and The exhaust passage 43 is shut off. On the other hand, when the opening 430 of the exhaust passage 43 provided in the second conical portion 29 and the opening 560 of the second conical door 56 overlap each other, the accommodation space 26 and the exhaust passage 43 communicate with each other and the accommodation space 26 and the humidified air passage 44 are cut off.

  The air inflow surface 61 of the hygroscopic material 6 is inclined with respect to the direction of the wind introduced from the collected air passage 41 into the accommodation space 26, and the direction of the air introduced into the accommodation space 26 from the warm air passage 42. It is housed in the housing space 26 in a state of being inclined with respect to.

  The first conical door 55 and the second conical door 56 are connected by a connecting member (not shown) and rotate in synchronization. Therefore, by the rotation of the first conical door 55 and the second conical door 56, the collected air passage 41 and the accommodation space 26 communicate with each other, and the exhaust passage 43 and the accommodation space 26 communicate with each other. At this time, the warm air passage 42 and the accommodation space 26 are shut off, and the humidified air passage 44 and the accommodation space 26 are shut off. In this state, the air introduced into the accommodation space 26 from the recovery air passage 41 spreads along the air inflow surface 61 of the hygroscopic material 6 and flows into the hygroscopic material 6 in a wide range. As a result, the moisture contained in the air introduced from the recovery air passage 41 into the accommodation space 26 is adsorbed over the entire moisture absorbent 6. Then, the air that has passed through the hygroscopic material 6 and has reduced humidity is discharged from the exhaust passage 43 to the outside of the air conditioning case 2.

  On the other hand, when the warm air passage 42 and the accommodation space 26 communicate with each other by the rotation of the first conical door 55 and the second conical door 56, the humidified air passage 44 and the accommodation space 26 communicate with each other. At this time, the collection air passage 41 and the accommodation space 26 are shut off, and the exhaust passage 43 and the accommodation space 26 are shut off. In this state, the air introduced into the accommodation space 26 from the warm air passage 42 spreads along the air inflow surface 61 of the hygroscopic material 6 and flows into the hygroscopic material 6 in a wide range. As a result, the moisture contained in the hygroscopic material 6 is released to the air introduced into the accommodation space 26 from the warm air passage 42. The air that has passed through the hygroscopic material 6 and has increased in humidity passes through the humidified air passage 44 and is blown into the vehicle compartment from the face outlet or the humidified air outlet. As a result, the air conditioner 1 of the present embodiment can humidify the vehicle interior without supplying water.

  The third embodiment described above can also achieve the same effects as the first and second embodiments. Further, in the third embodiment, the air conditioning case 2 and the housing portion 25 are integrally formed. Therefore, the size of the air conditioner 1 can be reduced.

(Fourth Embodiment)
A fourth embodiment will be described. The fourth embodiment is different from the second embodiment in the position and angle of the heater core 5.

  As shown in FIG. 16, in the fourth embodiment, the heater core 5 is provided in an inclined state with respect to the evaporator 4. Specifically, the heater core 5 is installed such that the upper end is closer to the evaporator 4 than the lower end. The heater core 5 is provided in contact with the bottom wall 201 of the air conditioning case 2 or provided near the bottom wall 201.

  In the fourth embodiment, similarly to the second embodiment, the partition plate 13 is not provided in the air conditioning case 2, and the ventilation passage 10 is not divided into the upper ventilation passage and the lower ventilation passage. That is, the air conditioner 1 of the fourth embodiment does not set the inside / outside air two-layer mode.

  A guide wall 70 for guiding the cool air is provided in the ventilation path 10 downstream of the air mix door 17. The guide wall 70 is provided on the downstream side of the air mix door 17 from a position substantially in the center of the ventilation passage 10 to an upper end portion of the heater core 5. Therefore, the cold air that has passed through the evaporator 4 flows through the passage between the guide wall 70 and the bottom wall 201 of the air conditioning case 2, and is guided to the heater core 5. In the fourth embodiment, a passage through which cool air flows from the evaporator 4 toward the heater core 5 when the air mix door 17 is removed is called a cold air passage 100. In FIG. 16, the range of the cold air passage 100 upstream of the air mix door 17 in the cold air passage 100 is indicated by the one-dot chain line range indicated by reference numeral 100a. The upper edge of the cold air passage 100 (that is, the upper edge of the alternate long and short dash line) upstream of the air mix door 17 is located at a position corresponding to the end of the guide wall 70 on the evaporator 4 side.

  In the fourth embodiment, the recovery wind outlet 40 of the recovery wind passage 41 is provided within the range of the alternate long and short dash line indicated by reference numeral 100a. That is, the collected air outlet 40 is provided on the upstream side of the air mix door 17 in the cold air passage 100 through which the cool air flows from the evaporator 4 toward the heater core 5.

  Next, the significance of providing the recovered air outlet 40 of the recovered air passage 41 in the cold air passage 100 will be described. 17 to 19 are schematic diagrams of the air conditioner 1 of the fourth embodiment. FIG. 17 shows a state where the opening degree of the air mix door 17 is 0%. FIG. 18 shows a state in which the opening degree of the air mix door 17 is 50%. FIG. 19 shows a state in which the opening degree of the air mix door 17 is 100%.

  FIG. 20 is a graph showing the relationship between the internal pressure of the ventilation passage 10 measured at the positions P5 and P6 shown in FIGS. 17 to 19 and the opening degree of the air mix door 17 based on the simulation. 17 to 19, P5 is a position above the cold air passage 100, and P6 is a position of the cold air passage 100.

  In the graph of FIG. 20, the relationship between the internal pressure of the space above the cold air passage 100 measured at the position P5 and the opening degree of the air mix door 17 is shown by a broken line, and the internal pressure of the cold air passage 100 measured at the position P6 and the air The relationship with the opening degree of the mix door 17 is shown by a solid line.

  From the graph of FIG. 20, it can be seen that the change in the internal pressure according to the opening degree of the air mix door 17 at the position P6 is smaller than that at the position P5. Further, the internal pressure at the position P6 becomes the minimum value when the opening degree of the air mix door 17 is 100%. On the other hand, the internal pressure at the position P5 becomes the minimum value when the opening degree of the air mix door 17 is 0%. At that time, the minimum value of the internal pressure at the position P6 is higher than the minimum value of the internal pressure at the position P5.

  The above reason will be described. As shown in FIG. 17, when the opening degree of the air mix door 17 is 0%, the air that has passed through the evaporator 4 flows to the outlet on the downstream side without passing through the heater core 5. At this time, since the air mix door 17 closes the cold air passage 100 on the upstream side of the heater core 5, the internal pressure at the position P6 becomes higher than the internal pressure at the position P5.

  As shown in FIG. 18, when the opening degree of the air mix door 17 is 50%, the air that has passed through the evaporator 4 is separated into air that passes through the heater core 5 and air that does not pass through the heater core 5, and the outlet on the downstream side. Flows to. At this time, due to the ventilation resistance of the heater core 5, the internal pressure at the position P6 becomes higher than the internal pressure at the position P5.

  As shown in FIG. 19, when the opening degree of the air mix door 17 is 100%, almost all of the air that has passed through the evaporator 4 passes through the heater core 5 and flows to the outlet on the downstream side. At this time, since the air mix door 17 closes the space above the cold air passage 100, the internal pressure at the position P5 becomes higher than the internal pressure at the position P6.

  As described with reference to FIGS. 17 to 20, the change in the internal pressure according to the opening degree of the air mix door 17 at the position P6 is smaller than that at the position P5. That is, in the cold air passage 100, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than that in the space above the cold air passage 100. Here, the amount of collected wind flowing through the collected wind passage 41 corresponds to the internal pressure of the ventilation passage 10. Therefore, compared with the case where the recovery wind outlet 40 is provided at the position P5, the case where the recovery wind outlet 40 is provided at the position corresponding to the position P6 is more dependent on the opening degree of the air mix door 17. The change in the amount of collected wind becomes small. Therefore, by providing the recovery air intake port 40 on the upstream side of the air mix door 17 in the cold air passage 100, the influence of the opening degree of the air mix door 17 is reduced, and the recovery air intake port 40 is accommodated through the recovery air passage 41. It is possible to supply a stable amount of collected air to the part 25.

  Further, when the opening degree of the air mix door 17 is viewed in the entire range of 0 to 100%, the minimum value of the internal pressure in the cold air passage 100 is higher than the minimum value of the internal pressure in the space above the cold air passage 100. Become. Therefore, by providing the collected air outlet 40 in the cold air passage 100, it is possible to secure the minimum collected air volume with a relatively large air volume. Therefore, the fourth embodiment can also achieve the same operational effects as those of the first to third embodiments.

(Fifth Embodiment)
A fifth embodiment will be described. The fifth embodiment differs from the first embodiment in that the position and angle of the heater core 5 are changed.

  As shown in FIG. 21, also in the fifth embodiment, the heater core 5 is provided in a state of being inclined with respect to the evaporator 4. Specifically, the heater core 5 is installed such that the upper end is closer to the evaporator 4 than the lower end. Further, the heater core 5 is provided at an intermediate position between the bottom wall 201 and the upper wall 202 in the ventilation passage 10 of the air conditioning case 2.

  In the fifth embodiment, similarly to the first embodiment, the ventilation passage 10 is divided into an upper ventilation passage 11 and a lower ventilation passage 12 by a partition plate 13. That is, the air conditioner 1 can set the inside / outside air two-layer mode in addition to the outside air mode and the inside air mode.

  An upper guide wall 71 for guiding the cool air is provided in the ventilation passage 10 on the upstream side of the air mix door 17 from a predetermined position on the downstream side of the evaporator 4 to a position corresponding to the upper end of the heater core 5. Has been. Further, in the ventilation passage 10, on the upstream side of the air mix door 17, from a predetermined position on the downstream side of the evaporator 4 to a position corresponding to the lower end of the heater core 5, a lower guide wall for guiding the cool air. 72 are provided. A cool air passage 100 is formed between the evaporator 4 and the heater core 5 and between the upper guide wall 71 and the lower guide wall 72 of the cool air flowing from the evaporator 4 toward the heater core 5. By this cold air passage 100, it is possible to flow a predetermined amount of air among the air that has passed through the evaporator 4 to the heater core 5. In FIG. 21, the range of the cold air passage 100 upstream of the air mix door 17 in the cold air passage 100 is indicated by the alternate long and short dash line indicated by reference numeral 100a.

  Also in the fifth embodiment, the recovery wind outlet 40 of the recovery wind passage 41 is provided within the range of the alternate long and short dash line indicated by reference numeral 100a. That is, the collected air outlet 40 is provided on the upstream side of the air mix door 17 in the cold air passage 100 through which the cool air flows from the evaporator 4 toward the heater core 5. In addition, in detail, it is preferable that the recovery air outlet 40 is provided in the cold air passage 100 below the partition plate 13 in the gravity direction.

  Next, the significance of providing the recovered air outlet 40 of the recovered air passage 41 in the cold air passage 100 will be described. 22 to 24 are schematic diagrams of the air conditioner 1 of the fifth embodiment. FIG. 22 shows a state in which the opening degree of the air mix door 17 is 0%. FIG. 23 shows a state in which the opening degree of the air mix door 17 is 50%. FIG. 24 shows a state in which the opening degree of the air mix door 17 is 100%.

  FIG. 25 is a graph showing the relationship between the internal pressure of the ventilation passage 10 measured at the positions of P7 to P10 shown in FIGS. 22 to 24 and the opening degree of the air mix door 17 based on the simulation. 22 to 24 are positions above the cold air passage 100, P8 and P9 are positions of the cold air passage 100, and P10 is a position below the cold air passage 100.

  In the graph of FIG. 25, the relationship between the internal pressure of the cold air passage 100 and the opening degree of the air mix door 17 measured at the positions P8 and P9 is shown by a solid line. Further, the relationship between the internal pressure of the space above or below the cold air passage 100 measured at the positions of P7 and P10 and the opening degree of the air mix door 17 is shown by a broken line.

  From the graph of FIG. 25, it can be seen that the positions of P8 and P9 have a smaller change in the internal pressure according to the opening degree of the air mix door 17 than the positions of P7 and P10. Further, the internal pressure at the positions of P8 and P9 becomes the minimum value when the opening degree of the air mix door 17 is 100%. On the other hand, the internal pressure at the positions of P7 and P10 becomes the minimum value when the opening degree of the air mix door 17 is 0%. At that time, the minimum value of the internal pressure at the positions of P8 and P9 is higher than the minimum value of the internal pressure at the positions of P7 and P10.

  The above reason will be described. As shown in FIG. 22, when the opening degree of the air mix door 17 is 0%, the air in the cold air passage 100 is stopped by the air mix door 17. On the other hand, the air in the space above and below the cold air passage 100 flows without passing through the heater core 5. At this time, since the air mix door 17 closes the cold air passage 100, the internal pressure at the positions P8 and P9 becomes higher than the internal pressure at the positions P7 and P10.

  As shown in FIG. 23, when the opening degree of the air mix door 17 is 50%, the air flowing through the cold air passage 100 flows through the heater core 5. On the other hand, the air in the space above and below the cold air passage 100 flows without passing through the heater core 5. At this time, due to the ventilation resistance of the heater core 5, the internal pressure at the positions of P8 and P9 becomes higher than the internal pressure at the positions of P7 and P10.

  As shown in FIG. 24, when the opening degree of the air mix door 17 is 100%, the air flowing through the cold air passage 100 flows through the heater core 5. On the other hand, the air in the space above and below the cold air passage 100 is stopped by the air mix door 17. At this time, since the air mix door 17 blocks the space above and below the cold air passage 100, the internal pressures at the positions P7 and P10 are higher than the internal pressures at the positions P8 and P9.

  As described with reference to FIGS. 22 to 25, the positions of P8 and P9 have a smaller change in the internal pressure according to the opening degree of the air mix door 17 than the positions of P7 and P10. That is, in the cold air passage 100, the change in the internal pressure according to the opening degree of the air mix door 17 is smaller than that in the space above and below the cold air passage 100. Here, the amount of collected wind flowing through the collected wind passage 41 corresponds to the internal pressure of the ventilation passage 10. Therefore, as compared with the case where the collected air outlet 40 is provided at the position of P7 and P10, the case where the collected air outlet 40 is provided at the position corresponding to the positions of P8 and P9 opens the air mix door 17. The change in the amount of collected wind depending on the degree becomes small. Therefore, by providing the recovery air intake port 40 on the upstream side of the air mix door 17 in the cold air passage 100, the influence of the opening degree of the air mix door 17 is reduced, and the recovery air intake port 40 is accommodated through the recovery air passage 41. It is possible to supply a stable amount of collected air to the part 25.

  Further, when the opening degree of the air mix door 17 is viewed in the entire range of 0 to 100%, the minimum value of the internal pressure in the cold air passage 100 is higher than the minimum value of the internal pressure in the space above and below the cold air passage 100. It becomes a value. Therefore, by providing the collected air outlet 40 in the cold air passage 100, it is possible to secure the minimum collected air volume with a relatively large air volume. Therefore, the fifth embodiment can also achieve the same effects as the first to fourth embodiments.

(Sixth Embodiment)
A sixth embodiment will be described. In the sixth embodiment, a part of the configuration of the recovery wind passage 41 is changed from the first to fifth embodiments.

  As shown in FIG. 26, in the sixth embodiment, the collection air passage 41 is inserted from the bottom wall 201 of the air conditioning case 2 to the inside of the air conditioning case 2. Also in the sixth embodiment, the collection wind outlet 40 of the collection wind passage 41 is provided within the range of the alternate long and short dash line indicated by reference numeral 100a. That is, the collected air outlet 40 of the collected air passage 41 is not limited to the side wall 200 of the ventilation passage 10 and may be provided on the upstream side of the air mix door 17 in the cold air passage 100. In addition, in detail, it is preferable that the recovery air outlet 40 is provided in the cold air passage 100 below the partition plate 13 in the gravity direction. The configuration of the sixth embodiment is effective when there is a mounting space below the air conditioning case 2. The sixth embodiment can also achieve the same effects as the first to fifth embodiments.

(Seventh embodiment)
The seventh embodiment will be described. Also in the seventh embodiment, a part of the configuration of the recovery wind passage 41 is changed from the first to sixth embodiments.

  As shown in FIG. 27, in the seventh embodiment, the collection air passage 41 is inserted from the side wall 200 of the air conditioning case 2 to the inside of the air conditioning case 2. Also in the seventh embodiment, the collection wind outlet 40 of the collection wind passage 41 is provided within the range of the alternate long and short dash line indicated by reference numeral 100a. That is, the collected air outlet 40 is provided on the upstream side of the air mix door 17 in the cold air passage 100 through which the cool air flows from the evaporator 4 toward the heater core 5. The configuration of the seventh embodiment is effective when the width of the heater core 5 is smaller than the width of the air conditioning case 2. The seventh embodiment can also achieve the same operational effects as those of the first to sixth embodiments.

(Other embodiments)
The present invention is not limited to the above-described embodiments, but can be appropriately modified within the scope described in the claims. Further, the above embodiments are not unrelated to each other, and can be appropriately combined unless a combination is clearly impossible. Further, in each of the above-described embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential unless explicitly specified as being essential and in principle considered to be essential. Yes. Further, in each of the above-described embodiments, when numerical values such as the number of components of the embodiment, numerical values, amounts, ranges, etc. are referred to, it is clearly limited to a particular number and in principle limited to a specific number. The number is not limited to the specific number, except in the case of being performed. Further, in each of the above-mentioned embodiments, when referring to the shapes of the components and the like, the positional relationship, etc., unless otherwise explicitly stated and in principle, the shape, the positional relationship, etc., the shape thereof, It is not limited to the positional relationship or the like.

  (1) In the above embodiment, the example in which the evaporator 4 is used as the cooling device that cools the air flowing through the ventilation path 10 of the air conditioning case 2 has been described. On the other hand, in other embodiments, the cooling device may use, for example, a gas-air heat exchanger that cools air using low-temperature air such as outside air, or a Peltier module.

  (2) In the above embodiment, an example in which the heater core 5 is used as a heating device that heats the air flowing through the ventilation passage 10 of the air conditioning case 2 has been described. On the other hand, in other embodiments, the heating device may use, for example, an electric heater or a Peltier module.

  (3) In the sixth and seventh embodiments described above, the collected air passage 41 is configured to be inserted from the bottom wall 201 or the side wall 200 of the air conditioning case 2 into the inside of the air conditioning case 2. On the other hand, in another embodiment, the recovery wind passage 41 may be configured to be inserted into the inside of the air conditioning case 2 from the upper wall 202 of the air conditioning case 2, for example.

  (4) When the collected air passage 41 is inserted from the bottom wall 201, the side wall 200, or the upper wall 202 of the air conditioning case 2 into the inside of the air conditioning case 2, the collected air outlet 40 is perpendicular to the cooling device 4. It is provided at a position including the height range HS where the heating device 5 is projected, or on the upstream side of the air mix door 17 in the cold air passage 100.

(Summary)
According to the first aspect described in part or all of the above-described embodiments, the air conditioner that performs air conditioning in the vehicle interior includes an air conditioning case, a cooling device, a heating device, an air mix door, a housing portion, and a collected wind. Equipped with a passage. The air conditioning case forms a ventilation path through which air flows. The cooling device cools the air flowing through the ventilation passage. The heating device is arranged on the downstream side of the cooling device and heats the air flowing through the ventilation passage. The air mix door is provided between the cooling device and the heating device, and adjusts the ratio between the amount of air that bypasses the heating device after passing through the cooling device and the amount of air that passes through the heating device. The accommodating portion accommodates a hygroscopic material capable of adsorbing and desorbing moisture contained in air. The collected air passage connects the housing with the collected air outlet provided between the cooling device and the heating device on the side wall of the ventilation passage. Here, the recovery air outlet is provided at a position on the side wall of the ventilation path that includes a height range in which the heating device is projected perpendicularly to the cooling device.

  According to the second aspect, the recovered air intake has a first recovered air intake provided on one side wall of the ventilation passage and a second recovered air intake provided on the other side wall of the ventilation passage. Have.

  According to this, the temperature and the air volume of the conditioned air blown from the blowout opening provided on the right side in the vehicle width direction of the air conditioning case and the conditioned air blown from the blowout opening provided on the left side in the vehicle width direction. Can keep the balance of.

  According to the third aspect, the air conditioner further includes a partition plate and an inside / outside air switching unit. The partition plate divides the ventilation passage in the air conditioning case into an upper ventilation passage on the upper side in the gravity direction and a lower ventilation passage on the lower side in the gravity direction. The inside / outside air switching unit can implement an inside / outside air two-layer mode in which the outside air is introduced into the upper ventilation passage and the inside air is introduced into the lower ventilation passage. Here, the recovery wind outlet is provided on the side wall of the lower ventilation passage.

  According to this, the air circulated in the inside air has a high absolute humidity due to sweating of an occupant. Therefore, by providing the recovery air intake port on the side wall of the lower ventilation passage in which the internal air circulation is performed, it is possible to supply air with high absolute humidity and relative humidity to the accommodation section from the recovery air intake port through the recovery air passage. is there.

  According to the fourth aspect, the air conditioner further includes a warm air passage, an exhaust passage, and a humid air passage. The warm air passage communicates the downstream side of the heating device with the housing, and introduces the air heated by the heating device into the housing. The exhaust passage discharges air from the housing portion. The humidified air passage blows out the air humidified in the accommodation portion toward the vehicle interior.

  According to this, in the accommodating portion, after the moisture is adsorbed by the hygroscopic material from the collected air introduced from the collected air passage, the air can be discharged through the exhaust passage. Further, it is possible to desorb the moisture from the hygroscopic material with respect to the air introduced into the accommodation portion from the warm air passage. The humidified air is blown out from the accommodation portion into the vehicle compartment through the humidified air passage. Accordingly, the air conditioning case can have the function of a non-supplying water humidifier that can operate without supplying water.

  According to the fifth aspect, the air conditioning case and the housing section are integrally configured.

  As a result, the size of the air conditioner can be reduced.

  According to a sixth aspect, an air conditioner that performs air conditioning in a vehicle compartment includes an air conditioning case, a cooling device, a heating device, an air mix door, a housing portion, and a collection wind passage. The air conditioning case forms a ventilation path through which air flows. The cooling device cools the air flowing through the ventilation passage. The heating device is arranged on the downstream side of the cooling device and heats the air flowing through the ventilation passage. The air mix door is provided between the cooling device and the heating device, and adjusts the ratio between the amount of air that does not pass through the heating device after passing through the cooling device and the amount of air that passes through the heating device. The accommodating portion accommodates a hygroscopic material capable of adsorbing and desorbing moisture contained in air. The collected air passage connects the housing with the collected air outlet provided upstream of the air mix door in the cool air passage through which the cool air flows from the cooling device to the heating device.

1 Air Conditioner 2 Air Conditioning Case 4 Evaporator 5 Heater Core 6 Moisture Absorbing Material 10 Ventilation Path 17 Air Mix Door 25 Housing 40 Recovery Wind Outlet 41 Recovery Wind Passage

Claims (5)

An air conditioner for air conditioning in a vehicle,
An air-conditioning case (2) forming an air passage (10) through which air flows,
A cooling device (4) for cooling the air flowing through the ventilation passage,
A heating device (5) arranged downstream of the cooling device for heating the air flowing through the ventilation passage;
An air mix door (17) provided between the cooling device and the heating device, which adjusts a ratio of an air amount that bypasses the heating device after passing through the cooling device and an air amount that passes through the heating device;
A storage section (25) for storing a hygroscopic material (6) capable of adsorbing and desorbing water contained in air;
A recovery wind outlet (40) provided between the cooling device and the heating device on the side wall (200) of the ventilation passage, and a recovery wind passage (41) that communicates with the accommodating portion,
The said collection wind extraction port is an air conditioner provided in the side wall of the said ventilation path in the position containing the height range (HS) which projected the said heating apparatus perpendicularly to the said cooling apparatus. The recovery wind outlet is
A first recovery air outlet (401) provided on one of the side walls of the ventilation passage;
The air conditioner according to claim 1, further comprising a second recovery air outlet (402) provided on the other side wall of the air passage. A partition plate (13) for partitioning the ventilation passage in the air conditioning case into an upper ventilation passage (11) on the upper side in the gravity direction and a lower ventilation passage (12) on the lower side in the gravity direction;
An inside / outside air switching unit (16) capable of performing an inside / outside air two-layer mode for introducing outside air into the upper ventilation passage and introducing inside air into the lower ventilation passage,
The air conditioner according to claim 1 or 2, wherein the recovery air outlet is provided on the side wall of the lower ventilation passage. A warm air passageway (42) that connects the downstream side of the heating device and the accommodation part and introduces the air heated by the heating device into the accommodation part;
An exhaust passage (43) for exhausting air from the accommodation portion,
The air conditioner according to any one of claims 1 to 3, further comprising: a humidified air passage (44) that blows out the air humidified in the accommodation portion toward a vehicle interior.   The air conditioner according to any one of claims 1 to 4, wherein the air conditioning case and the housing portion are integrally configured.

Images