JP6223710B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner mounted on, for example, an automobile.

  Conventionally, a vehicle air conditioner includes a casing that houses a heat exchanger for cooling and a heat exchanger for heating. An air mix damper for adjusting the temperature, a blowing direction switching damper for switching the blowing direction, and the like are disposed in the casing. By operating each damper, conditioned air having a desired temperature can be generated and supplied to each part of the passenger compartment (see, for example, Patent Document 1).

  The damper of Patent Document 1 includes a rotation shaft that is rotatably supported by the casing, and a closing plate portion that extends in a radial direction from the rotation shaft. The air passage can be opened and closed.

JP 2011-25959 A

  By the way, when the air flow is switched by the damper of Patent Document 1, when one air passage is closed and the other air passage is opened at the closing plate portion, the air flow flowing through the other air passage is the closing plate of the damper. May collide with the part. In this case, the airflow resistance increases and the air conditioning performance decreases, and noise is generated, so that the quietness in the passenger compartment cannot be maintained. In addition, the operability of the damper may be deteriorated.

  The present invention has been made in view of such points, and the object of the present invention is to suppress airflow resistance, reduce noise, and further improve the operability of the damper when the air flow is switched by the damper. It is to improve.

  In order to achieve the above object, in the present invention, the closing plate portion of the damper is adapted to follow the air flow.

1st invention accommodates the apparatus for an air conditioning inside, and the casing in which the 1st air passage and the 2nd air passage were formed,
A vehicle air conditioner including a damper disposed in the casing and configured to open and close the first air passage and the second air passage;
On the inner surface of the casing, the inclined surface where the upstream end opening of the first air passage opens and the inclined surface where the upstream end of the second air passage opens have the same inclination angle with respect to the vertical line. Formed,
The damper is rotatably supported by the casing at an intermediate position between an inclined surface where the upstream end opening of the first air passage opens and an inclined surface where the upstream end opening of the second air passage opens. a support shaft extending in Rutotomoni horizontally, and a closing plate part extending in the radial direction of the support shaft, the support shaft is disposed so as to be positioned above the said closing plate part, the closing plate part is The first air passage opening position that opens the upstream end opening of the first air passage and closes the upstream end opening of the second air passage by rotating together with the support shaft , and the first air. close the upstream end opening of the passage, and is switched to the second air passage opening position to open the upstream end opening of the second air passage,
When the closing plate portion is in the first air passage opening position, the obstruction plate portion follows the air flow in the first air passage, and when in the second air passage opening position, It is characterized by being formed along the flow of air.

  According to this configuration, when the damper is rotated so that the closing plate portion is in the first air passage opening position, the closing plate portion closes the second air passage and follows the air flow in the first air passage. Will be located. Therefore, the air flow in the first air passage does not collide with the blocking plate portion, the ventilation resistance is suppressed, the noise is reduced, and the operability is improved.

  In addition, when the damper is rotated so that the closing plate portion is at the second air passage opening position, the damper plate is located along the air flow in the second air passage, so that the airflow resistance is similarly reduced. In addition to being suppressed, noise is reduced and operability is improved.

Furthermore , when the damper is rotated so that the closing plate portion is at the first air passage opening position when the position of the damper is stationary when a force other than gravity is not applied, 2 When the damper is rotated so as to be in the open position of the air passage, the damper is rotated by substantially the same angle. Therefore, the operating force is substantially equal when rotating to any position.

  According to the first invention, when the closing plate portion is in the first air passage opening position, the second air passage is along the air flow in the first air passage and in the second air passage opening position. Since it is formed along the air flow in the air passage, when the air flow is switched by the damper, it is possible to suppress ventilation resistance, reduce noise, and operability by reducing the operation force of the damper Can be improved.

In addition , since the rotation angle to the first air passage opening position and the rotation angle to the second air passage opening position are substantially equal with respect to the stationary position in the free state of the damper, the rotation angle can be turned to any position. Also in the case of making them, the operating force can be made substantially equal, and the operability can be improved.

It is a figure which shows the internal structure of the vehicle air conditioner which concerns on embodiment of this invention. FIG. 2 is a view corresponding to FIG. 1 when in a defroster mode. FIG. 2 is a view corresponding to FIG. 1 when in a vent mode.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  FIG. 1 is a diagram showing an internal structure of a vehicle air conditioner 1 according to an embodiment of the present invention. The vehicle air conditioner 1 is mounted, for example, in a passenger compartment of an automobile, and includes a casing 10, an evaporator (air conditioning device) 11, a heater core (air conditioning device) 12, an air mix damper 13, and a heat damper. 14 and a differential / vent damper 15.

  In the description of this embodiment, the front side of the vehicle is simply referred to as “front”, the rear side of the vehicle is simply referred to as “rear”, the left side of the vehicle is simply referred to as “left”, and the right side of the vehicle is simply referred to as “right”. To do.

  The casing 10 is formed by molding a resin material, and is formed by integrating a plurality of divided casing constituent members using fastening members such as screws. The evaporator 10, the heater core 12, the air mix damper 13, the heat damper 14, and the differential / vent damper 15 are accommodated in the casing 10.

  An air inlet 10 a is formed at the front end of the side wall of the casing 10. A blower unit (not shown) is connected to the air introduction port 10a. Air-conditioning air blown from the blower unit is introduced into the casing 10 through the air inlet 10a. This air blowing unit is a part of the vehicle air conditioner 1.

  A defroster port 10 b and a vent port 10 c are formed in the upper wall portion of the casing 10. Further, a heat port 10 d is formed in the lower part of the casing 10. The defroster port 10b is mainly for supplying conditioned air to the inner surface of the windshield. Although not shown, the defroster port 10b is connected to a defroster nozzle provided at the front end of the instrument panel via a defroster duct. Yes. The vent port 10c is mainly for supplying conditioned air to the upper body of the front seat occupant, and is connected to a vent nozzle provided on the instrument panel via a vent duct (not shown). The heat port 10d is mainly for supplying conditioned air to the vicinity of the passenger's feet, and is connected to a heat duct (not shown).

  An air passage R is formed inside the casing 10. The upstream end of the air passage R is located at the front portion of the casing 10 and is constituted by the air inlet 10a. The downstream end of the air passage R is located at the rear part of the casing 10 and is composed of a defroster port 10b, a vent port 10c, and a heat port 10d.

  The air passage R communicates with a cold air generation passage R1 extending rearward from the air inlet 10a, a hot air generation passage R2 branched from the cold air generation passage R1 and extending downward, and the cold air generation passage R1 and the hot air generation passage R2. Air mix space R3, defroster passage (first air passage) R4, vent passage (second air passage) R5, and heat passage R6.

  The cold air generation passage R <b> 1 extends rearward from the front in the casing 10. The evaporator 11 is disposed in the cold air generation passage R1 so as to cross the cold air generation passage R1. The evaporator 11 is configured such that its air passage surface extends in the vertical direction. The evaporator 11 is configured by an evaporator that is an element of a refrigeration cycle apparatus, and is a tube-and-fin type heat exchanger. The entire amount of air-conditioning air flowing through the cold air generation passage R1 passes through the evaporator 11.

  The downstream side of the cold air generation passage R1 is bifurcated into two vertically, the upper downstream end is the upper opening 20 and the lower downstream end is the lower opening 21. The lower opening 21 is connected to the warm air generation passage R2. The upper opening 20 is connected to the air mix space R3.

  On the other hand, the hot air generation passage R2 is curved in a substantially U shape so that the downstream side extends upward after extending downward to the rear side. The downstream end of the warm air generation passage R2 is an opening 22. The cross-sectional area on the downstream side of the hot air generation passage R2 is narrower than the cross-sectional area on the upstream side, and the hot air generation passage R2 has a shape in which the downstream side is narrowed. Thereby, the wind speed of the warm air which flows into air mix space R3 can be raised.

  The heater core 12 is disposed in the hot air generation passage R2 so as to cross the hot air generation passage R2. The heater core 12 is inclined so that the air passage surface is positioned further toward the upper side. The heater core 12 is a tube and fin type heat exchanger configured to circulate cooling water of an engine (not shown). The entire amount of air-conditioning air flowing through the hot air generation passage R2 passes through the heater core 12.

  The air mix space R3 is located behind the cold air generation passage R1 and above the hot air generation passage R2. The downstream end opening 22 of the hot air generation passage R2 communicates with the lower part of the air mix space R3. The upper opening 20 of the cold air generation passage R1 communicates with the front side of the air mix space R3. Therefore, since the flow of the warm air flowing from the hot air generation passage R2 into the air mix space R3 and the flow of the cold air flowing from the cold air generation passage R1 into the air mix space R3 have an intersecting relationship, the air mix space R3 The hot air and the cold air are allowed to collide with each other and can be mixed well.

  The defroster passage R <b> 4 is formed in the upper wall portion of the casing 10. The upstream end of the defroster passage R4 is an opening 25 and communicates with the upper part of the air mix space R3. The upstream end opening 25 of the defroster passage R4 is disposed so as to overlap the downstream end opening 22 of the hot air generation passage R2 when viewed from the vertical direction. Further, the upstream end opening 25 of the defroster passage R4 opens in an inclined surface 30 that is inclined so as to be positioned on the front side as it goes down. The defroster passage R4 is inclined and extended so as to be positioned forward as it goes upward as a whole. The downstream end of the defroster passage R4 is a defroster port 10b, and is located in front of the upstream end opening 25 of the defroster passage R4.

  The vent passage R5 is formed at the rear side of the defroster passage R4 in the upper wall portion of the casing 10. The upstream end of the vent passage R5 is an opening 26, and communicates with a portion on the rear side of the upstream end opening 25 of the defroster passage R4 in the upper part of the air mix space R3. The upstream end opening portion 26 of the vent passage R5 opens to an inclined surface 31 that is inclined so as to be located on the rear side as it goes downward.

  The upstream end opening 26 of the vent passage R5 and the upstream end opening 25 of the defroster passage are formed so as to approach each other as they go upward. Further, an angle α1 formed between the inclined surface 30 formed with the upstream end opening 25 of the defroster passage and the vertical line, and an angle formed between the inclined surface 31 formed with the upstream end opening 26 of the vent passage R5 and the vertical line. α2 is set to be substantially the same.

  The upstream end of the heat passage R6 is an opening 27, and communicates with a portion below the upstream end opening 26 of the vent passage R5 in the rear portion of the air mix space R3. The heat passage R <b> 6 extends along the rear wall portion of the casing 10 to the vicinity of the lower end portion of the casing 10.

  The air mix damper 13 is a cantilever type having a rotating shaft 13a, a closing plate portion 13b extending in the radial direction from the outer surface of the rotating shaft 13a, and a sealing material 13c provided at the peripheral edge of the closing plate portion 13b. It is a plate damper. The rotation shaft 13 a extends in the left-right direction, and both end portions thereof are supported so as to be rotatable with respect to the left and right side walls of the casing 10. The rotation shaft 13a is located in the vicinity of the rear portion of the lower opening 21 of the cold air generation passage R1. The closing plate portion 13b is for opening and closing the upper opening 20 of the cold air generation passage R1 and the lower opening 21 of the cold air generation passage R1, and is formed larger than these openings 20, 21. It extends toward the front from the moving shaft 13a. The sealing material 13c is made of, for example, urethane foam, and is formed between the peripheral edge of the upper opening 20 of the cold air generation passage R1 and the peripheral edge of the closing plate portion 13b, and the lower opening of the cold air generation passage R1. The gap between the peripheral edge of the portion 21 and the peripheral edge of the closing plate 13b can be sealed.

  As shown in FIGS. 1 and 3, when the air mix damper 13 is rotated downward to fully close the lower opening 21 of the cold air generation passage R1, the upper opening 20 of the cold air generation passage R1 is fully opened. . In this state, the entire amount of cold air in the cold air generation passage R1 flows into the air mix space R3, so that the coldest conditioned air is obtained.

  As shown in FIG. 2, when the air mix damper 13 is rotated upward to fully close the upper opening 20 of the cold air generation passage R1, the lower opening 21 of the cold air generation passage R1 is fully opened. In this state, the entire amount of the cold air in the cold air generation passage R1 flows into the hot air generation passage R2 and is heated, and then flows into the air mix space R3, so that the hottest conditioned air is obtained.

  When the air mix damper 13 is set to the intermediate rotation position, both the upper opening 20 and the lower opening 21 of the cold air generation passage R1 are opened. In this state, according to the opening degree of the upper side opening part 20 and the lower side opening part 21, the inflow amount into the air mix space R3 of the cool air of the cool air generation passage R1 and the inflow amount into the hot air generation passage R2 are set. Is done. The temperature of the conditioned air generated in the air mix space R3 can be changed by the ratio of these inflow amounts.

  The air mix damper 13 can be operated by an actuator controlled by an air conditioning control device (not shown), or a temperature control lever or dial disposed in the passenger compartment and the air mix damper 13 are connected by an operation wire. A passenger can also perform manual operation.

  The heat damper 14 is a rotary damper having a rotating shaft 14a, a closing plate portion 14b provided in a radial direction away from the rotating shaft 14a, and a sealing material 14c provided at a peripheral portion of the closing plate portion 14b. . The rotation shaft 14 a extends in the left-right direction, and both end portions thereof are supported so as to be rotatable with respect to the left and right side wall portions of the casing 10. The rotation shaft 14a is located in the vicinity of the front portion of the downstream end opening 22 of the hot air generation passage R2. The blocking plate portion 14b is for opening and closing the upstream end opening 27 of the heat passage R6, and is formed larger than the upstream end opening 27. The sealing material 14 c is the same as the sealing material 13 c of the air mix damper 13.

  As shown in FIG. 1, when the heat damper 14 rotates upward to fully open the heat passage R6, the conditioned air hardly flows into the defroster passage R4 and the vent passage R5. On the other hand, as shown in FIGS. 2 and 3, when the heat damper 14 is rotated downward to fully close the heat passage R6, almost the entire amount of conditioned air flows to the defroster passage R4 and the vent passage R5.

  The differential / vent damper 15 is a cantilever type having a rotating shaft 15a, a closing plate portion 15b extending in the radial direction from the outer surface of the rotating shaft 15a, and a sealing material 15c provided at the peripheral edge of the closing plate portion 15b. It is a plate damper. The rotation shaft 15 a extends in the left-right direction, and both end portions thereof are supported so as to be rotatable with respect to the left and right side wall portions of the casing 10. The rotation shaft 15a is located in the vicinity of the upper portions of the inclined surfaces 30 and 31 between the upstream end opening 25 of the defroster passage R4 and the upstream end opening 26 of the vent passage R5. The blocking plate portion 15b is for opening and closing the upstream end opening 25 of the defroster passage R4 and the upstream end opening 26 of the vent passage R5, and is formed larger than the openings 25 and 26. The sealing material 15 c is the same as the sealing material 13 c of the air mix damper 13.

  The closing plate portion 15b is a flat plate formed along the inclined surfaces 30 and 31, and as shown in FIG. 2, the differential / vent damper 15 is rotated rearward to open the upstream end of the vent passage R5. When the portion 26 is fully closed, the upstream end opening 25 of the defroster passage R4 is fully opened. At this time, when the heat passage R6 is closed by the heat damper 14, a defroster mode is entered in which substantially the entire amount of conditioned air in the air mix space R3 flows into the defroster passage R4.

  Since the defroster mode is normally a mode that is selected during heating in order to clear the windshield fogging, the air mix damper 13 is rotated upward as shown in FIG. 2 to open the lower side of the cold air generation passage R1. The part 21 is fully opened. When the lower opening 21 of the cold air generation passage R1 is fully opened, the cold air in the cold air generation passage R1 flows in order toward the upstream end opening 25 of the defroster passage R4 through the hot air generation passage R2 and the air mix space R3 in order. . The mainstream flow of the conditioned air at this time is as shown by an arrow X in FIG. In this embodiment, the closing plate portion 15b of the differential / vent damper 15 in the defroster mode is formed along the arrow X, that is, the closing plate portion 15b is substantially parallel to the air flow indicated by the arrow X. Yes.

  As shown in FIG. 3, when the differential / vent damper 15 is rotated forward to fully close the upstream end opening 25 of the defroster passage R4, the upstream end opening 26 of the vent passage R5 is fully opened. At this time, when the heat passage R6 is closed by the heat damper 14, a vent mode is entered in which substantially the entire amount of the conditioned air in the air mix space R3 flows into the vent passage R5.

  Since the vent mode is normally a mode selected during cooling, the air mix damper 13 is rotated downward as shown in FIG. 3 to fully open the upper opening 20 of the cool air generation passage R1. When the upper opening 20 of the cold air generation passage R1 is fully opened, the cold air of the cold air generation passage R1 flows through the air mix space R3 toward the upstream end opening 26 of the vent passage R5. The mainstream flow of the conditioned air at this time is as shown by an arrow Y in FIG. In this embodiment, the closing plate portion 15b of the differential / vent damper 15 in the vent mode is formed along the arrow Y, that is, the closing plate portion 15b is substantially parallel to the air flow indicated by the arrow Y. Yes.

  In addition to the above-described defroster mode and vent mode, the conditioned air blowing mode can be switched to, for example, a differential / heat mode, a vent / heat mode, or the like. In the differential / heat mode, the heat damper 14 opens the heat passage R6 and the differential / vent damper 15 also opens the defroster passage R4. In the vent / heat mode, the heat damper 14 opens the heat passage R6 and the differential / vent damper 15 opens the vent passage R5.

  In this embodiment, the differential / vent damper 15 is manual. That is, the blow direction switch lever and dial disposed in the passenger compartment and the differential / vent damper 15 are connected by an operation wire (not shown) so that the occupant can manually operate.

  When the differential / vent damper 15 is in a free state, due to the weight of the closing plate portion 15b, the closing plate portion 15b stops at a rotational position extending vertically as shown by a solid line in FIG. The free state of the differential / bent damper 15 is a state in which an external force other than gravity, for example, an operating force by a blowing direction switching lever or a dial is not applied to the differential / vent damper 15 at all. The rotation angle from the stationary position to the defroster passage opening position (first air passage opening position) shown in FIG. 2 and the vent passage shown in FIG. 3 from the stationary position with reference to the stationary position of the differential / vent damper 15 in the free state. The rotation angle to the open position (second air passage open position) is set to be substantially equal. This is because the inclination angle with respect to the vertical line between the inclined surface 30 where the upstream end opening 25 of the defroster passage R4 opens and the inclined surface 31 where the upstream end opening 26 of the vent passage R5 opens is set equal. This is because the rotation shaft 15a is positioned at the intermediate portion between the inclined surfaces 30 and 31.

  Next, operation | movement of the vehicle air conditioner 1 comprised as mentioned above is demonstrated. The air-conditioning air blown from the blower unit flows into the cool air generation passage R <b> 1 in the casing 10 from the air inlet 10 a of the casing 10. At this time, as shown in FIG. 2, when the defroster mode is selected as the blowing mode, and the air mix damper 13 fully closes the upper opening 20 of the cold air generation passage R1, the main flow of the conditioned air is / It becomes the direction along the closing plate portion 15b of the vent damper 15. Thereby, since the flow of the conditioned air toward the defroster passage R4 does not collide with the closing plate portion 15b of the diff / vent damper 15, the airflow resistance is suppressed and the noise is reduced.

  Also, as shown in FIG. 3, when the vent mode is selected as the blowout mode and the air mix damper 13 fully closes the lower opening 21 of the cold air generation passage R1, the main flow of the conditioned air is changed to the differential mode. / It becomes the direction along the closing plate portion 15b of the vent damper 15. Thereby, since the flow of the conditioned air toward the vent passage R5 does not collide with the closing plate portion 15b of the differential / vent damper 15, the ventilation resistance is suppressed and the noise is reduced.

  Further, when the differential / vent damper 15 is rotated, the closing plate portion 15b is rotated so as to be in the defroster passage opening position shown in FIG. 2, and is rotated so as to be in the vent passage opening position shown in FIG. There are cases. At this time, when turning to either side, when viewed from the stationary position of the differential / vent damper 15, it is turned by substantially the same angle. Almost equal. Therefore, the operability by the passenger is improved.

  As described above, according to the vehicle air conditioner 1 according to this embodiment, when the closing plate portion 15b of the differential / vent damper 15 is in the defroster passage opening position, the airflow in the defroster passage R4 is aligned. In addition, since it is formed so as to follow the air flow in the vent passage R5 when it is in the vent passage opening position, when the air flow is switched by the differential / vent damper 15, the ventilation resistance can be suppressed and the noise can be reduced. In addition, the operability of the differential / vent damper 15 can be improved.

  Further, since the rotation angle to the defroster passage opening position and the rotation angle to the vent passage opening position are substantially equal with respect to the stationary position of the differential / vent damper 15 in the free state, the rotation angle is rotated to any position. In this case, the operating force can be made substantially equal, and the operability can be improved.

  The above-described embodiment is merely an example in all respects and should not be interpreted in a limited manner. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

  As described above, the vehicle air conditioner according to the present invention can be mounted on, for example, an automobile.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 10 Casing 11 Evaporator (air conditioning equipment)
12 Heater core (air conditioning equipment)
15 differential / vent damper 15a support shaft 15b closing plate part R4 defroster passage (first air passage)
R5 Vent passage (second air passage)

Claims (1)

A casing in which air conditioning equipment is housed and a first air passage and a second air passage are formed;
A vehicle air conditioner including a damper disposed in the casing and configured to open and close the first air passage and the second air passage;
On the inner surface of the casing, the inclined surface where the upstream end opening of the first air passage opens and the inclined surface where the upstream end of the second air passage opens have the same inclination angle with respect to the vertical line. Formed,
The damper is rotatably supported by the casing at an intermediate position between an inclined surface where the upstream end opening of the first air passage opens and an inclined surface where the upstream end opening of the second air passage opens. a support shaft extending in Rutotomoni horizontally, and a closing plate part extending in the radial direction of the support shaft, the support shaft is disposed so as to be positioned above the said closing plate part, the closing plate part is The first air passage opening position that opens the upstream end opening of the first air passage and closes the upstream end opening of the second air passage by rotating together with the support shaft , and the first air. close the upstream end opening of the passage, and is switched to the second air passage opening position to open the upstream end opening of the second air passage,
When the closing plate portion is in the first air passage opening position, the obstruction plate portion follows the air flow in the first air passage, and when in the second air passage opening position, An air conditioner for a vehicle characterized by being formed along the flow of air.

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