US20040194947A1 - Air conditioner for vehicle use - Google Patents
Air conditioner for vehicle use Download PDFInfo
- Publication number
- US20040194947A1 US20040194947A1 US10/793,514 US79351404A US2004194947A1 US 20040194947 A1 US20040194947 A1 US 20040194947A1 US 79351404 A US79351404 A US 79351404A US 2004194947 A1 US2004194947 A1 US 2004194947A1
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- US
- United States
- Prior art keywords
- air
- passage
- mixing door
- door
- hot air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00007—Combined heating, ventilating, or cooling devices
- B60H1/00021—Air flow details of HVAC devices
- B60H1/00028—Constructional lay-out of the devices in the vehicle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00664—Construction or arrangement of damper doors
- B60H1/00692—Damper doors moved by translation, e.g. curtain doors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S251/00—Valves and valve actuation
- Y10S251/901—Curtain type valves
Definitions
- the present invention relates to an air conditioner for vehicle use in which the blowing air temperature is adjusted when a ratio of the volume of a cold air to the volume of a hot air is adjusted.
- the air mixing type temperature adjusting system adjusts a ratio of the volume of a cold air to the volume of a hot air so as to adjust the blowing air temperature.
- FIG. 8A is a view showing a case in which the air mixing door is composed of a plate door.
- the air mixing door 30 composed of a one piece plate door, is rotated round the rotary shaft 31 , the area of the cold air passage 6 , which bypasses the heater core 5 , and the area of the hot air passage 7 , which is provided on the heater core 5 side, are adjusted so as to adjust a ratio of the volume of a cold air to the volume of a hot air.
- the broken line position 30 a of the air mixing door 30 is the maximum cooling position at which the cold air passage 6 is fully opened and the hot air passage 7 is fully closed
- the one-dotted chain line position 30 b is the maximum heating position at which the hot air passage 7 is fully opened and the cold air passage is fully closed.
- FIG. 9A is a view showing a case in which the air mixing door 40 is composed of a film door which is made of a flexible thin film member 40 a .
- the opening 40 b in which air passes through, is provided on the thin film member 40 a .
- the upper and the lower end portion of the thin film member 40 a are connected to the winding shafts 41 , 42 .
- the upper and the lower end portion of the thin film member 40 a are wound round the winding shafts 41 , 42 .
- the upper and the lower end portion of the thin film member 40 a are sent out (rewound) from the winding shafts 41 , 42 .
- the intermediate portion of the thin film member 40 a is guided by the intermediate guide portion 43 .
- the air mixing door 30 is rotated from the maximum cooling position 30 a to the intermediate temperature controlling position (shown by the solid line), the hot air passage 7 in the rotary direction of the plate door is opened, and at the same time, the passages (the passages in the perpendicular direction to the surface of FIG. 8A) on the right and the left of the plate door are opened. Therefore, the area of the hot air passage 7 is suddenly increased.
- the air mixing door 30 When the air mixing door 30 is rotated from the maximum heating position 30 b to the intermediate temperature controlling position (the solid line position), the cold air passage 7 in the plate door rotating direction is opened, and at the same time, the passages on the right and the left (the passages perpendicular to the surface of FIG. 8A) of the plate door are opened. Therefore, the area of the cold air passage 6 is suddenly increased.
- FIG. 8B The axis of abscissa of FIG. 8B represents a rotary angle of the air mixing door 30 .
- the rotary angle at the maximum cooling position 30 a is set at 0°
- the rotary angle at the maximum heating position 30 b is set at the maximum angle ⁇ .
- the blowing air temperature is suddenly changed with respect to the rotary angle of the air mixing door 30 in the regions ( 1 ) and ( 2 ) in the neighborhoods of the maximum cooling position 30 a and the maximum heating position 30 b . Further, the blowing air temperature is gradually changed in the intermediate temperature control region ( 3 ). Therefore, in the region ( 1 ) in the neighborhood of the maximum cooling region 30 a and in the region ( 2 ) in the neighborhood of the maximum heating region 30 b , it becomes difficult to control the blowing air temperature.
- the air mixing door 40 composed of a film door
- the following advantages can be provided.
- the thin film member 40 a moves across the cold air passage 6 and the hot air passage 7 , it is unnecessary to provide a rotary operation space, which is different from the case in which the plate door is used. Therefore, the dimensions of the case 2 can be reduced.
- the air mixing door 40 composed of the film door is advantageous in that the blowing air temperature control characteristic can be improved as compared with the case in which the plate door is used.
- “O” on the axis of abscissa represents the maximum cooling position at which the opening 40 b on the thin film member 40 a overlaps the cold air passage 6 so that the cold air passage 6 can be fully opened, and at the same time the film portion of the thin film member 40 a overlaps the hot air passage 7 so that the hot air passage 7 can be fully closed.
- “O” on the axis of abscissa represents the maximum cooling position at which the opening 40 b on the thin film member 40 a overlaps the cold air passage 6 so that the cold air passage 6 can be fully opened, and at the same time the film portion of the thin film member 40 a overlaps the hot air passage 7 so that the hot air passage 7 can be fully closed.
- “L” on the axis of abscissa represents the maximum heating position at which the opening 40 b of the thin film member 40 a overlaps the hot air passage 7 so that the hot air passage 7 can be fully opened, and at the same time the film portion of the thin film member 40 a overlaps the cold air passage 6 so that the cold air passage 6 can be fully closed.
- the opening 40 b the area of which is predetermined, which is provided on the thin film member 40 a composing the film door, is moved and the passage areas of the cold air passage 6 and the hot air passage 7 are adjusted by the opening 40 b
- the opening 40 b on the thin film member 40 a is moved to the intermediate temperature control position between the maximum cooling position and the maximum heating position as shown in FIG. 9A and the blowing air temperature is adjusted at a value in the intermediate temperature region close to 25° C.
- the passage area in the case 2 is necessarily restricted by the opening area of the opening 40 b.
- the present invention has been accomplished to solve the above problems. It is an object of the present invention to provide an air mixing type air conditioner for vehicle use characterized in that: a pressure loss in the air passage in the intermediate temperature region can be reduced; and the blowing air temperature control characteristic is excellent.
- both an air mixing door ( 9 ) for the cold air for adjusting a passage area of the cold air passage ( 6 ); and an air mixing door ( 10 ) for the hot air for adjusting a passage area of the hot air passage ( 7 ) are composed of a sliding door for adjusting the passage area when the air mixing door ( 9 ) for the cold air and the air mixing door ( 10 ) for the hot air are slid in a direction perpendicular to the flow of air in both the passages ( 6 , 7 ), and while one of the air mixing door ( 9 ) for the cold air and the air mixing door ( 10 ) for the hot air is maintaining one of the passages ( 6 , 7 ) in a fully opened state, an operating position of the other door is adjusted so that a passage area of the other passage is adjusted and a temperature of the air blowing out into a vehicle compartment is adjusted.
- both air mixing doors ( 10 ) are composed of a sliding door which slides in a direction perpendicular to the air flowing direction in both passages ( 6 , 7 ). Therefore, it unnecessary to provide an operation space which is required for the plate door so that the plate door can be rotated. Accordingly, the air conditioner can be made smaller.
- each air mixing door ( 10 ) is slid in a direction perpendicular to the direction of air flow, the passage area of each passage ( 6 , 7 ) is adjusted. Therefore, only the passage opening corresponding to the operating position (sliding distance) of each air mixing door ( 10 ) is always formed in each passage ( 6 , 7 ). A flow of air passes only in this passage opening and flows into each passage ( 6 , 7 ).
- each air mixing door ( 10 ) is opened from the fully closed state of each passage ( 6 , 7 ), the passage area is not suddenly increased, which is unlike the passage area of the rotary plate type door. Therefore, it is possible to linearly change a rate of flow of air of each passage ( 6 , 7 ) corresponding to the position at which each air mixing door ( 10 ) is operated. As a result, it is possible to provide a linear controlling characteristic of controlling the blowing air temperature. Therefore, the controlling operation can be easily performed.
- a maximum cooling state is set when the cold air passage ( 6 ) is fully opened by the air mixing door ( 9 ) for the cold air and the hot air passage ( 7 ) is fully closed by the air mixing door ( 10 ) for the hot air
- a maximum heating state is set when the cold air passage ( 6 ) is fully closed by the air mixing door ( 9 ) for the cold air and the hot air passage ( 7 ) is fully opened by the air mixing door ( 10 ) for the hot air
- a state in which both passages are simultaneously fully opened, in which the cold air passage ( 6 ) is fully opened by the air mixing door ( 9 ) for the cold air and the hot air passage ( 7 ) is fully opened by the air mixing door ( 10 ) for the hot air is set in an intermediate temperature control region formed between the maximum cooling state and the maximum heating state.
- the sliding door composing the air mixing door ( 9 ) for the cold air or the air mixing door ( 10 ) for the hot air can be concretely composed of a flexible thin film member ( 9 a , 10 a ).
- the length of the thin film member ( 9 a , 10 a ) from one end portion in the opening portion of the cold air passage ( 6 ) or the hot air passage ( 7 ) is changed, and the passage area of the cold air passage ( 6 ) or the hot air passage ( 7 ) is changed.
- the thin film members ( 9 a , 10 a ) are not slid on the member (the case 2 in this embodiment) composing both the passages ( 6 , 7 ), and the length of the thin film member ( 9 a , 10 a ) from one end portion is changed, so that the passage area can be changed.
- the other end portion of the thin film member ( 9 a , 10 a ) is connected to the winding shaft ( 9 c , 10 c ) and the winding shaft ( 9 c , 10 c ) is moved being rotated in a direction so that the winding shaft ( 9 c , 10 c ) can be separated from, or come close to, one end portion of the thin film member ( 9 a , 10 a ), the other end portion of the thin film member ( 9 a , 10 a ) is wound by the winding shaft ( 9 c , 10 c ) or leaves the winding shaft ( 9 c , 10 c ).
- FIG. 1 is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of an embodiment of the present invention.
- FIG. 2 is a perspective view showing an outline of the air mixing door (film door) of an embodiment of the present invention.
- FIG. 3 is a plan view showing an operating mechanism of the air mixing door shown in FIG. 2.
- FIG. 4 is a sectional view of FIG. 3.
- FIG. 5 is a block diagram showing an electric control section of an embodiment of the present invention.
- FIG. 6A is a plan view showing a fully opened state of the air mixing door (film door) shown in FIG. 2.
- FIG. 6B is a plan view showing a fully closed state of the air mixing door (film door) shown in FIG. 2.
- FIGS. 7A-7F are schematic illustrations for explaining operation of the air mixing door (film door) of an embodiment of the present invention.
- FIG. 8A is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of the prior art.
- FIG. 8B is a temperature control characteristic diagram of the air conditioner body unit portion shown in FIG. 8A.
- FIG. 9A is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of another prior art.
- FIG. 9B is a plan view of the thin film member shown in FIG. 9A.
- FIG. 9C is a temperature control characteristic diagram of the air conditioner body unit portion shown in FIG. 9A.
- FIG. 1 is a longitudinally sectional view showing an air conditioner body unit 1 in the indoor air conditioner unit of the air conditioner for vehicle use of an embodiment of the present invention.
- the indoor air conditioner unit of the air conditioner for vehicle use is divided into two main portions.
- One is a blower unit not shown in this embodiment, and the other is an air conditioner body unit 1 .
- the air conditioner body unit 1 is arranged inside the instrument panel, which is located in the front portion of a vehicle compartment, at the substantial center in the lateral direction of a vehicle body. That is, the air conditioner body unit 1 is arranged according to the layout in which the unit is arranged at the center. On the other hand, the blower unit 1 is arranged being offset at a position in the front of the passenger seat located on the side of the air conditioner body unit 1 in the lateral direction of the vehicle.
- the blower unit includes an inside air and outside air change-over box which is arranged in an upper portion of the blower unit.
- a centrifugal blower is arranged in a lower portion of this inside air and outside air change-over box. Inside air or outside air introduced into this inside air and outside air change-over box is sent to the air conditioner body unit 1 by the centrifugal blower.
- the air conditioner body unit 1 includes a case 2 made of resin.
- This case 2 is composed in such a manner that the right and left split case, which are divided on the split face (not shown) located at the center in the lateral direction of the vehicle, are connected to each other being integrated into one body by a fastening means such as an appropriate metallic spring clamp or screw.
- a fastening means such as an appropriate metallic spring clamp or screw.
- the air entrance space 3 into which air flows from the blower, is formed.
- Air blown out from the blower unit 1 flows in the case 2 from the front side to the rear side of the vehicle.
- the evaporator 4 and the heater core 5 are arranged in series in this order from the upstream side to the downstream side of air.
- This evaporator 4 composes the well known refrigerating cycle together with the compressor, condenser and decompressing means not shown in the drawing. That is, the evaporator 4 is a heat exchanger for cooling the air in the case 2 .
- the evaporator 4 includes a core portion for heat exchange which is composed of flat tubes, in which a refrigerant of low pressure, decompressed by the decompressing means, flows, and corrugated fins joined to these flat tubes. Air blown out from the blower passes in this core portion for heat exchange in the longitudinal direction of the vehicle.
- the heater core 5 is a heat exchanger for heating air in the case 2 while hot water (engine coolant) flowing inside is being used as a heat source.
- the heater core 5 includes a core portion for heat exchange composed of flat tubes, in which hot water flows, and corrugated fins joined to the flat tubes. Air blown out from the blower passes in this core portion for heat exchange in the longitudinal direction of the vehicle.
- the cold air passage 6 is formed on the upper side of the heater core 5 .
- This cold air passage 6 is used when a cold air flows bypassing the heater core 5 .
- the hot air passage 7 is formed on the lower side of the cold air passage 6 .
- This hot air passage 7 is a passage in which a hot air to be heated by the heater core 5 flows.
- the profiles of the openings of the cold air passage 6 and hot air passage 7 are rectangular.
- the sealing faces 8 a , 8 b , 8 c are formed in the opening circumferential edge portions of the cold air passage 6 and hot air passage 7 in such a manner that the sealing faces 8 a , 8 b , 8 c are integrated with the case 2 into one body.
- the air mixing door 9 for the cold air is arranged in the upstream portion of the cold air passage 6
- the air mixing door 10 for the hot air is arranged in the upstream portion of the heater core 5 (the hot air passage 7 ).
- Both the air mixing doors 9 , 10 are composed of a film door of the same structure in which the thin film member 9 a , 10 a is used.
- One end portion of the thin film member 9 a , 10 a of the air mixing door 9 , 10 is fixed onto the sealing face 8 a , 8 b , 8 c on the case 2 side by the appropriate fixing member 9 b , 10 b .
- the fixing member 9 b , 10 b can be composed of a pin-shaped member having an engaging head portion.
- the other end portion of the thin film member 9 a , 10 a is connected to the winding shaft 9 c , 10 c.
- operation is conducted as follows.
- the winding shaft 9 c , 10 c is rotated in the direction of arrow B (clockwise) in FIG. 2
- the other end portion of the thin film member 9 a , 10 a leaves the winding shaft 24 c , 25 c
- the other end portion of the thin film member 9 a , 10 a is moved together with the winding shaft 9 c , 10 c in the direction (to the right in FIG. 2) so that the other end portion of the thin film member 9 a , 10 a can be separated from one end portion (the fixed portion) of the thin film member 9 a , 10 a.
- the position of the other end portion of the thin film member 9 a , 10 a is changed in the direction of arrow A together with the winding shaft 9 c , 10 c , and the length (the sending length) of the thin film member 9 a , 10 a from one end portion is changed. Due to the foregoing, the cold air passage 6 and the hot air passage 7 are opened and closed.
- the door operating mechanism is composed of a worm gear mechanism.
- the exclusive actuator 11 , 12 is arranged for each winding shaft 9 c , 10 c .
- This actuator 11 , 12 is composed of a servo motor and drives the worm shaft 13 , 14 .
- This worm shaft 13 , 14 is arranged being perpendicular to each winding shaft 9 c , 10 c.
- the worm shaft 13 , 14 is arranged on the side of the opening of the cold air passage 6 or the hot air passage 7 so that the worm shaft 13 , 14 cannot obstruct the draft of the cold air passage 6 or the hot air passage 7 .
- the worm 13 a , 14 a which is formed into a screw, is formed all along the length of the worm shaft 13 , 14 in the moving range of the winding shaft 9 c , 10 c in the direction of arrow A.
- the worm wheel 9 d , 10 d is provided (shown in FIG. 3). This worm wheel 9 d , 10 d is meshed with the worm 13 a , 14 a.
- the racks 15 , 16 are provided being adjacent to the right and left outside in the ranges with which the thin film members 9 a , 10 a come into contact.
- the pinions 9 e , 10 e meshed with the racks 15 , 16 are provided at both end portions of the winding shaft 9 c , 10 c in the axial direction.
- the worm shaft 13 , 14 and the racks 15 , 16 are arranged in parallel with the winding shaft moving direction A.
- the worm 13 a , 14 a of the worm shaft 13 , 14 and the rack 15 , 16 are formed all over the length in the moving range of the winding shaft 9 c , 10 c in the direction of arrow A.
- any material can be used.
- a PET (polyethylene terephthalate) film or PPS (polyphenylene sulfide) film may be preferably used.
- the thickness of the thin film member 9 a , 10 a is, for example, approximately 200 ⁇ m.
- the specific arrangements of the air mixing door 9 for the cold air and the air mixing door 10 for the hot air with respect to the air conditioner unit 1 will be explained below.
- one end portion of the thin film member 9 a that is, the upper end portion is fixed to the sealing face 8 a of the upper end portion of the entrance opening portion of the cold air passage 6 by the fixing member 9 b
- the other end portion of the thin film member 9 a that is, the lower end portion is connected to the winding shaft 9 c . Therefore, the lower end portion of the thin film member 9 a is moved in the vertical direction (the direction of arrow A) together with the winding shaft 9 c.
- one end portion of the thin film member 10 a that is, the lower end portion is fixed to the sealing face 8 c of the lower end portion of the entrance opening portion of the hot air passage 7 by the fixing member 10 b
- the other end portion of the thin film member 10 a that is, the upper end portion is connected to the winding shaft 10 c . Therefore, the upper end portion of the thin film member 10 a is moved in the vertical direction (the direction of arrow A) together with the winding shaft 10 c.
- a ratio of the passage area of the cold air passage 6 to the passage area of the hot air passage 7 is adjusted, and a ratio of the volume of the cold air “a” flowing in the cold air passage 6 to the volume of the hot air “b” flowing in the hot air passage 7 is adjusted.
- the sealing face 8 b provided on the case side is located between the cold air passage 8 b and the hot air passage 7 .
- the winding shaft 9 c for the cold air is moved to the position of the sealing face 8 b located at the intermediate position in the vertical direction, the cold air passage 6 is fully closed by the thin film member 9 a for the cold air.
- the winding shaft 10 c for the hot air is moved to the position of the sealing face 8 b , the hot air passage 7 is fully closed by the thin film member 10 a for the hot air.
- the air mixing portion 17 is formed on the downstream side (the rear side of the vehicle) of the cold air passage 6 .
- the cold air “a” sent from the cold air passage 6 and the hot air “b” sent from the hot air passage 7 are mixed with each other.
- the hot air passage 7 is bent upward on the downstream side (the rear side of the vehicle) of the heater core 5 . Therefore, the hot air “b” flows toward the air mixing portion 17 arranged in the upper portion of the heater core 5 .
- the blowing opening portion 18 is formed being adjacent to the air mixing portion 17 .
- Conditioned air the temperature of which has been adjusted in the air mixing portion 17 , is blown out from this blowing opening portion 18 .
- the blowing opening portion 18 the following opening portions are provided. There are provided a foot opening portion from which conditioned air is blown out toward the feet of the passenger, a face opening portion from which conditioned air is blown out toward the upper half of the body of the passenger and a defroster opening portion from which conditioned air is blown out toward the inner face of the windshield.
- the plurality of blowing opening portions 18 are changed over so that they can be opened and closed according to the blowing mode door not shown in the drawing.
- FIG. 5 is a block diagram of the electric control section of this embodiment.
- the air conditioner control unit 20 is composed of a well known microcomputer, which includes CPU, ROM and RAM, and peripheral circuits.
- the control program for controlling the air conditioner is stored in ROM. According to the control program, various calculations and processing are conducted.
- the sensor detecting signals sent from a group of sensors 21 and the operation signals sent from the air conditioner panel 22 are inputted onto the input side of the air conditioner control unit 20 .
- the group of sensors 21 include: a well known outside air temperature sensor 21 a ; an inside air temperature sensor 21 b ; a sunshine sensor 21 c ; an evaporator blowing air temperature sensor 21 d ; and a hot water (engine coolant) temperature sensor 21 c.
- the air conditioner panel 22 includes: a well known temperature setting switch 22 a ; an inside and outside air changeover switch 22 b ; a blowing mode switch 22 c ; a air volume changeover switch 22 d ; and an air conditioner switch 22 e for turning on and off the operation of the refrigerating cycle compressor not shown in the drawing.
- the electromagnetic clutch 23 not shown, of the compressor, the blower drive motor 24 , not shown, of the blower unit, the actuator 25 , not shown, for driving the inside and outside air changeover door, the actuator 26 , not shown, for driving the blowing mode changeover door, the actuator 11 for driving the winding shaft 9 c of the air mixing door 9 for the cold air and the actuator 12 for driving the winding shaft 10 c of the air mixing door 10 for the hot air are connected to the output side of the air conditioner control unit 20 . Operation of these devices is controlled by the output signals sent out from the air conditioner control unit 20 .
- the air conditioner control unit 20 reads in the detection signals sent from the group of sensors 41 and the operation signals sent from the air conditioner panel 42 and calculates the target blowing temperature TAO of air blowing out from the blowing opening portion 18 into the vehicle compartment.
- This target blowing temperature TAO is the temperature of a air blown out into the vehicle compartment which is necessary for maintaining the temperature in the vehicle compartment at the setting temperature T set which has been set by the temperature setting switch 22 a irrespective of the fluctuation of the air conditioning heat load.
- TAO is calculated according to this setting temperature T set and also according to the outside temperature T am , the inside temperature T r and the quantity of sunshine T s which are detected by the sensors 21 a to 21 c.
- the air conditioning control unit 20 individually determines the operating position of the air mixing door 9 for the cold air and the operating position of the air mixing door 10 for the hot air according to the target blowing temperature TAO, the evaporator blowing air temperature T e and the hot water temperature T w and controls the operating positions of the air mixing door 9 for the cold air and the air mixing door 10 for the hot air. In this way, the temperature of the air blown out into the vehicle compartment can be controlled so that it can become the target blowing temperature TAO.
- FIG. 6A shows a state in which the thin film member 9 a , 10 a is wound, by the winding shaft 9 c , 10 c , to the maximum when the winding shaft 9 c , 10 c of the air mixing door 9 for the cold air or the air mixing door 10 for the hot air is moved to a position closest to the fixing position of one end portion of the thin film member 9 a , 10 a .
- the cold air passage 6 and the hot air passage 7 are fully opened.
- FIG. 6B shows a state in which the thin film member 9 a , 10 a leaves (is rewound) the winding shaft 9 c , 10 c to the maximum when the winding shaft 9 c , 10 c of the air mixing door 9 for the cold air or the air mixing door 10 for the hot air is moved to a position most distant from the fixing position of one end portion of the thin film member 9 a , 10 a .
- the cold air passage 6 and the hot air passage 7 are fully closed by the thin film members 9 a , 10 a.
- the axis of abscissa represents the moving position of the winding shaft 9 c , 10 c
- the axis of ordinate represents the temperature of the air blown out into the vehicle compartment.
- the air mixing door 9 for the cold air or the air mixing door 10 for the hot air is operated at the operating position shown in FIG. 7B.
- the operation is conducted as follows.
- the winding shaft 9 c of the air mixing door 9 for the cold air is moved to the passage fully opened position “0”, by the actuator 11 , so as to fully open the cold air passage 6 .
- the winding shaft 10 c of the air mixing door 10 for the hot air is moved to the passage fully closed position “100” so as to fully close the hot air passage 7 . Due to the foregoing, all the cold air “a”, which has been cooled by the evaporator 4 , passes through the cold air passage 6 and blows out from the blowing opening portion 18 into the vehicle compartment, and the maximum cooling performance can be exhibited.
- FIG. 7C shows a state in which the target blowing temperature TAO rises and the operating positions of the air mixing door 9 for the cold air and the air mixing door 10 for the hot air are moved a little from the maximum cooling position to the temperature control region.
- the operation is conducted as follows.
- the winding shaft 9 c of the air mixing door 9 for the cold air is maintained at the passage fully opened position “0”, and the fully opened state of the cold air passage 6 is maintained.
- the winding shaft 10 c of the air mixing door 10 for the hot air is moved to an intermediate position “50” between the passage fully closed position “100” and the passage fully opened position “0”. Due to the foregoing, the thin film member 10 a of the air mixing door 10 for the hot air opens the hot air passage 7 by about 50%.
- FIG. 7D shows a state in which the temperature of the air blown into the vehicle compartment is raised higher than the state shown in FIG. 7C.
- both the winding shaft 9 c of the air mixing door 9 for the cold air and the winding shaft 10 c of the air mixing door 10 for the hot air are operated so that the winding shafts move to the passage fully opened position “0”. Accordingly, both the cold air passage 6 and the hot air passage 7 are fully opened. Due to the foregoing, compared with the state shown in FIG. 7C, a rate of the volume of the hot air “b” is increased, and the temperature of the air blown out into the vehicle compartment can be raised.
- the passage area in the case 2 can be maximized. Accordingly, a pressure loss of draft in the case 2 can be minimized.
- the state shown in FIG. 7D that is, the intermediate temperature control state is a control region most frequently used through the year. Therefore, the generation of blower noise, which is generated when the air conditioner is operated, and the consumption of electric power by the blower drive motor 24 can be effectively reduced.
- FIG. 7E shows a state in which the temperature of the air blown into the vehicle compartment is raised higher than the state shown in FIG. 7D.
- the winding shaft 10 c of the air mixing door 10 for the hot air is being maintained at the passage fully opened position “0”
- the winding shaft 9 c of the air mixing door 9 for the cold air is moved to the neighborhood of the intermediate position “50” between the passage fully closed position “100”, and the passage fully opened position “0”. Due to the above operation, the cold air passage 6 is half opened, and a volume of the cold air is decreased and a volume of the hot air is increased. Accordingly, the blowing air temperature can be raised.
- FIG. 7F shows a state which is set at the maximum heating state in which the temperature of the air blown out into the vehicle compartment is heated to the maximum temperature.
- the winding shaft 10 c of the air mixing door 10 for the hot air is being maintained at the passage fully opened position “0”
- the winding shaft 9 c of the air mixing door 9 for the cold air is moved to the passage fully closed position “100”. Due to the foregoing, the hot air passage 7 is fully opened and the cold air passage 6 is fully closed. Therefore, all blast, which has passed through the evaporator 4 , can be heated by the heater core 5 , and the maximum heating performance can be exhibited.
- both the air mixing door 9 for the cold air and the air mixing door 10 for the hot air are composed of a film door made of thin film member 9 a , 10 a , and the other end portion of the thin film member 9 a , 10 a is wound by the winding shaft 9 c , 10 c on the sealing faces 8 a to 8 c and sent out from the winding shaft 9 c , 10 c , so that the passage areas (the openings) of the cold air passage 6 and the hot air passage 7 are changed. Therefore, the passage areas of the cold air passage 6 and the hot air passage 7 can be substantially proportionally changed according to the changes in the operating position of the winding shafts 9 c , 10 c.
- one end portion of the thin film member 9 a , 10 a composing the air mixing door 9 for the cold air or the air mixing door 10 for the hot air is fixed to the case 2 side, and the other end portion of the thin film member 9 a , 10 a is wound by the winding shaft 9 c , 10 c on the sealing faces 8 a to 8 c on the case side or the other end portion of the thin film member 9 a , 10 a is sent out from the winding shaft 9 c , 10 c , so that the passage (opening) areas of the cold air passage 6 and the hot air passage 7 can be changed.
- the present invention is not limited to the above specific door structure, and the door structure can be deformed as follows.
- a sliding door is used, in which a flexible thin film member is slid on a sealing face on the case side so as to compose the air mixing door 9 for the cold air and the air mixing door 10 for the hot blast.
- the air mixing door 9 for the cold air and the air mixing door 10 for the hot air are composed of not a flexible thin film member but a solid sliding door. When this solid sliding door is slid on the sealing face provided on the case side, the passage areas of the cold air passage 6 and the hot air passage 7 are independently changed as shown in FIG. 7.
- the air mixing door 9 for the cold air and the air mixing door 10 for the hot air may be composed of a sliding door for adjusting the passage area when sliding door slides in a direction perpendicular to the direction of air flow in the cold air passage 6 and the hot air passage 7 .
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- Mechanical Engineering (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
Both an air mixing door (9) for the cold air for adjusting a passage area of the cold air passage (6); and an air mixing door (10) for the hot air for adjusting a passage area of the hot air passage (7) are composed of a sliding door for adjusting the passage area when the air mixing door (9) for the cold air and the air mixing door (10) for the hot air are slid in a direction perpendicular to the flow of air in both the passages (6, 7), and while one of the air mixing door (9) for the cold air and the air mixing door (10) for the hot air is maintaining one of the passages (6, 7) in a fully opened state, an operating position of the other door is adjusted so that a passage area of the other passage is adjusted and a temperature of the air blowing out into a vehicle compartment is adjusted.
Description
- 1. Field of the Invention
- The present invention relates to an air conditioner for vehicle use in which the blowing air temperature is adjusted when a ratio of the volume of a cold air to the volume of a hot air is adjusted.
- 2. Description of the Related Art
- Concerning the blowing air temperature adjusting system provided in an air conditioner for vehicle use, in a typical system, the air mixing type temperature adjusting system adjusts a ratio of the volume of a cold air to the volume of a hot air so as to adjust the blowing air temperature.
- Concerning the air mixing door which is a temperature adjusting means in this air mixing type air temperature adjusting system, a plate door type and a film door type air mixing door are well known.
- FIG. 8A is a view showing a case in which the air mixing door is composed of a plate door. When the
air mixing door 30, composed of a one piece plate door, is rotated round therotary shaft 31, the area of thecold air passage 6, which bypasses theheater core 5, and the area of thehot air passage 7, which is provided on theheater core 5 side, are adjusted so as to adjust a ratio of the volume of a cold air to the volume of a hot air. - In this connection, in FIG. 8A, the
broken line position 30 a of theair mixing door 30 is the maximum cooling position at which thecold air passage 6 is fully opened and thehot air passage 7 is fully closed, and the one-dottedchain line position 30 b is the maximum heating position at which thehot air passage 7 is fully opened and the cold air passage is fully closed. - FIG. 9A is a view showing a case in which the air mixing door40 is composed of a film door which is made of a flexible
thin film member 40 a. As shown in FIG. 9B, the opening 40 b, in which air passes through, is provided on thethin film member 40 a. The upper and the lower end portion of thethin film member 40 a are connected to the winding shafts 41, 42. When both the winding shafts 41, 42 are rotated being interlocked with each other, the upper and the lower end portion of thethin film member 40 a are wound round the winding shafts 41, 42. Alternatively, the upper and the lower end portion of thethin film member 40 a are sent out (rewound) from the winding shafts 41, 42. The intermediate portion of thethin film member 40 a is guided by the intermediate guide portion 43. - When both the winding shafts41, 42 are rotated, the
thin film member 40 a moves across thecold air passage 6 and thehot air passage 7. Therefore, an overlapping position, at which the opening 40 b of thethin film member 40 a overlaps thecold air passage 6 and thehot air passage 7, is changed, so that the passage (opening) areas of thecold air passage 6 and thehot air passage 7 can be adjusted. - In the former case of the
air mixing door 30 composed of the plate door, it is necessary to provide an operation space, in which the plate door is rotated, in thecase 2. Therefore, it is disadvantageous that the dimensions of thecase 2 are increased. - Further, the following problems may be encountered. When the
air mixing door 30 is rotated from themaximum cooling position 30 a to the intermediate temperature controlling position (shown by the solid line), thehot air passage 7 in the rotary direction of the plate door is opened, and at the same time, the passages (the passages in the perpendicular direction to the surface of FIG. 8A) on the right and the left of the plate door are opened. Therefore, the area of thehot air passage 7 is suddenly increased. - When the
air mixing door 30 is rotated from themaximum heating position 30 b to the intermediate temperature controlling position (the solid line position), thecold air passage 7 in the plate door rotating direction is opened, and at the same time, the passages on the right and the left (the passages perpendicular to the surface of FIG. 8A) of the plate door are opened. Therefore, the area of thecold air passage 6 is suddenly increased. - On the other hand, when the
air mixing door 30 is operated at the intermediate temperature controlling position exemplarily shown by the solid line in the view, as the right plate door passage and the left plate door passage (shown by the solid line) of thecold air passage 6 and thehot air passage 7 have already been opened, the areas of thecold air passage 6 and thehot air passage 7 are gradually changed with respect to the change in the rotary angle of the plate door. - As a result, the control characteristic of controlling the blowing air temperature by the air mixing door composed of the plate door is deteriorated as shown in FIG. 8B. The axis of abscissa of FIG. 8B represents a rotary angle of the
air mixing door 30. The rotary angle at themaximum cooling position 30 a is set at 0°, and the rotary angle at themaximum heating position 30 b is set at the maximum angle θ. - As shown in FIG. 8B, the following characteristic is provided. The blowing air temperature is suddenly changed with respect to the rotary angle of the
air mixing door 30 in the regions (1) and (2) in the neighborhoods of themaximum cooling position 30 a and themaximum heating position 30 b. Further, the blowing air temperature is gradually changed in the intermediate temperature control region (3). Therefore, in the region (1) in the neighborhood of themaximum cooling region 30 a and in the region (2) in the neighborhood of themaximum heating region 30 b, it becomes difficult to control the blowing air temperature. - On the other hand, in the latter case of the air mixing door40 composed of a film door, the following advantages can be provided. As the
thin film member 40 a moves across thecold air passage 6 and thehot air passage 7, it is unnecessary to provide a rotary operation space, which is different from the case in which the plate door is used. Therefore, the dimensions of thecase 2 can be reduced. - Further, as a current of air always flows in the
cold air passage 6 and thehot air passage 7 passing through only in the opening 40 b provided on thethin film member 40 a, the areas of thecold air passage 6 and thehot air passage 7 can be changed by a predetermined ratio with respect to the change in the moving position of thethin film member 40 a. Therefore, the blowing air temperature can be substantially linearly adjusted by the change in the position of the opening 40 b of thethin film member 40 a over all the region between the maximum cooling state to the maximum heating state. Accordingly, the air mixing door 40 composed of the film door is advantageous in that the blowing air temperature control characteristic can be improved as compared with the case in which the plate door is used. - In this connection, in FIG. 9C, “O” on the axis of abscissa represents the maximum cooling position at which the opening40 b on the
thin film member 40 a overlaps thecold air passage 6 so that thecold air passage 6 can be fully opened, and at the same time the film portion of thethin film member 40 a overlaps thehot air passage 7 so that thehot air passage 7 can be fully closed. In FIG. 9C, “L” on the axis of abscissa represents the maximum heating position at which the opening 40 b of thethin film member 40 a overlaps thehot air passage 7 so that thehot air passage 7 can be fully opened, and at the same time the film portion of thethin film member 40 a overlaps thecold air passage 6 so that thecold air passage 6 can be fully closed. - However, as the opening40 b, the area of which is predetermined, which is provided on the
thin film member 40 a composing the film door, is moved and the passage areas of thecold air passage 6 and thehot air passage 7 are adjusted by the opening 40 b, when the opening 40 b on thethin film member 40 a is moved to the intermediate temperature control position between the maximum cooling position and the maximum heating position as shown in FIG. 9A and the blowing air temperature is adjusted at a value in the intermediate temperature region close to 25° C., the passage area in thecase 2 is necessarily restricted by the opening area of the opening 40 b. - In the case where the
air mixing door 30 composed of the plate door is used, a current of air flows in thecold air passage 6 and thehot air passage 7 at all times. Therefore, it is possible to reduce a pressure loss of draft generated in thecase 2. However, in the case where the air mixing door 40 composed of the film door is used, the passage area in thecase 2 is restricted by the opening area of the opening 40 b at all times. Therefore, the pressure loss of draft is increased. - For the above reasons, the pressure loss generated in the air passage in the intermediate temperature region, which is most frequently used through the year, becomes larger than that of the plate door type. Accordingly, noise is increased in the operation of the blower and further the electric power consumption of the blower is increased.
- The present invention has been accomplished to solve the above problems. It is an object of the present invention to provide an air mixing type air conditioner for vehicle use characterized in that: a pressure loss in the air passage in the intermediate temperature region can be reduced; and the blowing air temperature control characteristic is excellent.
- In order to accomplish the above object, according to a first aspect of the present invention, both an air mixing door (9) for the cold air for adjusting a passage area of the cold air passage (6); and an air mixing door (10) for the hot air for adjusting a passage area of the hot air passage (7) are composed of a sliding door for adjusting the passage area when the air mixing door (9) for the cold air and the air mixing door (10) for the hot air are slid in a direction perpendicular to the flow of air in both the passages (6, 7), and while one of the air mixing door (9) for the cold air and the air mixing door (10) for the hot air is maintaining one of the passages (6, 7) in a fully opened state, an operating position of the other door is adjusted so that a passage area of the other passage is adjusted and a temperature of the air blowing out into a vehicle compartment is adjusted.
- According to this air mixing type air conditioner for vehicle use, both air mixing doors (10) are composed of a sliding door which slides in a direction perpendicular to the air flowing direction in both passages (6, 7). Therefore, it unnecessary to provide an operation space which is required for the plate door so that the plate door can be rotated. Accordingly, the air conditioner can be made smaller.
- Further, when each air mixing door (10) is slid in a direction perpendicular to the direction of air flow, the passage area of each passage (6, 7) is adjusted. Therefore, only the passage opening corresponding to the operating position (sliding distance) of each air mixing door (10) is always formed in each passage (6, 7). A flow of air passes only in this passage opening and flows into each passage (6, 7).
- Accordingly, when each air mixing door (10) is opened from the fully closed state of each passage (6, 7), the passage area is not suddenly increased, which is unlike the passage area of the rotary plate type door. Therefore, it is possible to linearly change a rate of flow of air of each passage (6, 7) corresponding to the position at which each air mixing door (10) is operated. As a result, it is possible to provide a linear controlling characteristic of controlling the blowing air temperature. Therefore, the controlling operation can be easily performed.
- Further, while one of the air mixing doors (9, 10) is maintained so that one of the passages (6, 7) can be fully opened, the operating position of the other door is adjusted. Due to the foregoing, the passage area of the other passage can be adjusted so that the temperature of the blowing air into the vehicle compartment can be adjusted. Therefore, in the intermediate temperature controlling region, both the cold air passage (6) and the hot air passage (7) can be fully opened at the same time.
- For the above reasons, compared with the conventional film door type air mixing door, the pressure loss of draft can be greatly reduced, and the noise generated by the blower can be very effectively reduced, and, further, the electric power consumption of the motor for driving the blower can be very effectively reduced.
- According to a second aspect of the present invention, a maximum cooling state is set when the cold air passage (6) is fully opened by the air mixing door (9) for the cold air and the hot air passage (7) is fully closed by the air mixing door (10) for the hot air, a maximum heating state is set when the cold air passage (6) is fully closed by the air mixing door (9) for the cold air and the hot air passage (7) is fully opened by the air mixing door (10) for the hot air, and a state in which both passages are simultaneously fully opened, in which the cold air passage (6) is fully opened by the air mixing door (9) for the cold air and the hot air passage (7) is fully opened by the air mixing door (10) for the hot air, is set in an intermediate temperature control region formed between the maximum cooling state and the maximum heating state.
- As described above, when the cold air passage (6) and the hot air passage (7) are fully opened at the same time, it is possible to effectively realize a reduction in the pressure loss of draft.
- According to a third aspect of the present invention, the sliding door composing the air mixing door (9) for the cold air or the air mixing door (10) for the hot air can be concretely composed of a flexible thin film member (9 a, 10 a).
- According to a fourth aspect of the present invention, when one end portion of the thin film member (9 a, 10 a) is fixed and the other end portion of the thin film member (9 a, 10 a) is moved in a direction so that the other end portion can be separated from or come close to one end portion, the length of the thin film member (9 a, 10 a) from one end portion in the opening portion of the cold air passage (6) or the hot air passage (7) is changed, and the passage area of the cold air passage (6) or the hot air passage (7) is changed.
- Due to the foregoing, while one end portion of the thin film member (9 a, 10 a) is being fixed, the length of the thin film member (9 a, 10 a) from one end portion is changed, so that the passage area can be changed. Therefore, the thin film members (9 a, 10 a) are not slid on the member (the
case 2 in this embodiment) composing both the passages (6, 7), and the length of the thin film member (9 a, 10 a) from one end portion is changed, so that the passage area can be changed. - Therefore, no sliding friction is caused between the thin film members (9 a, 10 a) and the passage side member (2), and a force of operating the thin film member can be reduced. The generation of noise caused by the sliding friction can be prevented.
- According to a fifth aspect of the present invention, when the other end portion of the thin film member (9 a, 10 a) is connected to the winding shaft (9 c, 10 c) and the winding shaft (9 c, 10 c) is moved being rotated in a direction so that the winding shaft (9 c, 10 c) can be separated from, or come close to, one end portion of the thin film member (9 a, 10 a), the other end portion of the thin film member (9 a, 10 a) is wound by the winding shaft (9 c, 10 c) or leaves the winding shaft (9 c, 10 c).
- Due to the foregoing, while the winding shaft (9 c, 10 c) is rotating and moving, the operating position of the other end portion of the thin film member (9 a, 10 a) can be positively moved.
- Incidentally, the reference numerals in parentheses, used to denote the above means, are intended to show the relationship of the specific means which will be described later in an embodiment of the invention.
- The present invention may be more fully understood from the description of preferred embodiments of the invention set forth below, together with the accompanying drawings.
- FIG. 1 is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of an embodiment of the present invention.
- FIG. 2 is a perspective view showing an outline of the air mixing door (film door) of an embodiment of the present invention.
- FIG. 3 is a plan view showing an operating mechanism of the air mixing door shown in FIG. 2.
- FIG. 4 is a sectional view of FIG. 3.
- FIG. 5 is a block diagram showing an electric control section of an embodiment of the present invention.
- FIG. 6A is a plan view showing a fully opened state of the air mixing door (film door) shown in FIG. 2.
- FIG. 6B is a plan view showing a fully closed state of the air mixing door (film door) shown in FIG. 2.
- FIGS. 7A-7F are schematic illustrations for explaining operation of the air mixing door (film door) of an embodiment of the present invention.
- FIG. 8A is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of the prior art.
- FIG. 8B is a temperature control characteristic diagram of the air conditioner body unit portion shown in FIG. 8A.
- FIG. 9A is a longitudinally sectional view showing an air conditioner body unit portion of the air conditioner for vehicle use of another prior art.
- FIG. 9B is a plan view of the thin film member shown in FIG. 9A.
- FIG. 9C is a temperature control characteristic diagram of the air conditioner body unit portion shown in FIG. 9A.
- Referring to the drawings, an embodiment of the present invention will be explained below. FIG. 1 is a longitudinally sectional view showing an air
conditioner body unit 1 in the indoor air conditioner unit of the air conditioner for vehicle use of an embodiment of the present invention. - The indoor air conditioner unit of the air conditioner for vehicle use is divided into two main portions. One is a blower unit not shown in this embodiment, and the other is an air
conditioner body unit 1. Arrows illustrated in FIG. 1, which are respectively directed to the front, rear, upper and lower, represent the directions of the airconditioner body unit 1 mounted on a vehicle. - The air
conditioner body unit 1 is arranged inside the instrument panel, which is located in the front portion of a vehicle compartment, at the substantial center in the lateral direction of a vehicle body. That is, the airconditioner body unit 1 is arranged according to the layout in which the unit is arranged at the center. On the other hand, theblower unit 1 is arranged being offset at a position in the front of the passenger seat located on the side of the airconditioner body unit 1 in the lateral direction of the vehicle. - As well known, the blower unit includes an inside air and outside air change-over box which is arranged in an upper portion of the blower unit. A centrifugal blower is arranged in a lower portion of this inside air and outside air change-over box. Inside air or outside air introduced into this inside air and outside air change-over box is sent to the air
conditioner body unit 1 by the centrifugal blower. - The air
conditioner body unit 1 includes acase 2 made of resin. Thiscase 2 is composed in such a manner that the right and left split case, which are divided on the split face (not shown) located at the center in the lateral direction of the vehicle, are connected to each other being integrated into one body by a fastening means such as an appropriate metallic spring clamp or screw. At the front portion in thiscase 2, theair entrance space 3, into which air flows from the blower, is formed. - Air blown out from the
blower unit 1 flows in thecase 2 from the front side to the rear side of the vehicle. In thecase 2, theevaporator 4 and theheater core 5 are arranged in series in this order from the upstream side to the downstream side of air. - This
evaporator 4 composes the well known refrigerating cycle together with the compressor, condenser and decompressing means not shown in the drawing. That is, theevaporator 4 is a heat exchanger for cooling the air in thecase 2. Theevaporator 4 includes a core portion for heat exchange which is composed of flat tubes, in which a refrigerant of low pressure, decompressed by the decompressing means, flows, and corrugated fins joined to these flat tubes. Air blown out from the blower passes in this core portion for heat exchange in the longitudinal direction of the vehicle. - The
heater core 5 is a heat exchanger for heating air in thecase 2 while hot water (engine coolant) flowing inside is being used as a heat source. As is well known, theheater core 5 includes a core portion for heat exchange composed of flat tubes, in which hot water flows, and corrugated fins joined to the flat tubes. Air blown out from the blower passes in this core portion for heat exchange in the longitudinal direction of the vehicle. - Next, explanations will be made into a temperature adjusting mechanism for adjusting the temperature of air blowing out into the vehicle compartment. When the
heater core 5, the height of which is approximately ½of the height of theevaporator 4, is arranged in a lower space of thecase 5, thecold air passage 6 is formed on the upper side of theheater core 5. Thiscold air passage 6 is used when a cold air flows bypassing theheater core 5. On the lower side of thecold air passage 6, thehot air passage 7 is formed. Thishot air passage 7 is a passage in which a hot air to be heated by theheater core 5 flows. - As shown in FIGS. 2, 3 and5, the profiles of the openings of the
cold air passage 6 andhot air passage 7 are rectangular. The sealing faces 8 a, 8 b, 8 c are formed in the opening circumferential edge portions of thecold air passage 6 andhot air passage 7 in such a manner that the sealing faces 8 a, 8 b, 8 c are integrated with thecase 2 into one body. - In the
case 2, theair mixing door 9 for the cold air is arranged in the upstream portion of thecold air passage 6, and theair mixing door 10 for the hot air is arranged in the upstream portion of the heater core 5 (the hot air passage 7). - Next, the specific structure of the
air mixing door 9 for the cold air and that of theair mixing door 10 for the hot air will be explained below referring to FIGS. 2 to 4. Both theair mixing doors thin film member - One end portion of the
thin film member air mixing door face case 2 side by the appropriate fixingmember member thin film member shaft - When the winding
shaft shaft thin film member shaft thin film member shaft thin film member - Specifically, operation is conducted as follows. When the winding
shaft thin film member thin film member shaft thin film member thin film member - On the other hand, when the winding
shaft thin film member thin film member shaft thin film member thin film member - Due to the foregoing, the position of the other end portion of the
thin film member shaft thin film member cold air passage 6 and thehot air passage 7 are opened and closed. - As described above, as the winding
shaft shaft - Specifically, as shown in FIGS. 3 and 4, the
exclusive actuator 11, 12 is arranged for each windingshaft actuator 11, 12 is composed of a servo motor and drives the worm shaft 13, 14. This worm shaft 13, 14 is arranged being perpendicular to each windingshaft - In this case, the worm shaft13, 14 is arranged on the side of the opening of the
cold air passage 6 or thehot air passage 7 so that the worm shaft 13, 14 cannot obstruct the draft of thecold air passage 6 or thehot air passage 7. On the outer circumferential face of the worm shaft 13, 14, theworm shaft shaft worm wheel worm wheel worm - On the other hand, on the sealing faces8 a, 8 b, 8 c formed in the circumferential edge of the cold air passage and the hot air passage, the racks 15, 16 are provided being adjacent to the right and left outside in the ranges with which the
thin film members pinions shaft - The worm shaft13, 14 and the racks 15, 16 are arranged in parallel with the winding shaft moving direction A. The
worm shaft - When the worm shaft13, 14 is driven by the
actuator 11, 12, as theworm worm wheel shaft pinions shaft shaft actuator 11, 12 is controlled, a quantity of rotation of each windingshaft shaft - In this connection, concerning the material of the
thin film member shaft thin film member - Next, referring to FIG. 1, the specific arrangements of the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air with respect to theair conditioner unit 1 will be explained below. In theair mixing door 9 for the cold air, one end portion of thethin film member 9 a, that is, the upper end portion is fixed to the sealingface 8 a of the upper end portion of the entrance opening portion of thecold air passage 6 by the fixingmember 9 b, and the other end portion of thethin film member 9 a, that is, the lower end portion is connected to the windingshaft 9 c. Therefore, the lower end portion of thethin film member 9 a is moved in the vertical direction (the direction of arrow A) together with the windingshaft 9 c. - On the other hand, in the
air mixing door 10 for the hot air, one end portion of thethin film member 10 a, that is, the lower end portion is fixed to the sealingface 8 c of the lower end portion of the entrance opening portion of thehot air passage 7 by the fixingmember 10 b, and the other end portion of thethin film member 10 a, that is, the upper end portion is connected to the windingshaft 10 c. Therefore, the upper end portion of thethin film member 10 a is moved in the vertical direction (the direction of arrow A) together with the windingshaft 10 c. - In the
air mixing door 9 for the cold air, when the windingshaft 9 c is moved in the vertical direction A, the position of the lower end portion of thethin film member 9 a is displaced, and the area of the passage (opening) of thecold air passage 6 is increased or decreased. In the same manner, in theair mixing door 10 for the hot air, when the windingshaft 10 c is moved in the vertical direction A, the position of the lower end portion of thethin film member 10 a is displaced, and the area of the passage (opening) of thehot air passage 7 is increased or decreased. - Due to the foregoing, a ratio of the passage area of the
cold air passage 6 to the passage area of thehot air passage 7 is adjusted, and a ratio of the volume of the cold air “a” flowing in thecold air passage 6 to the volume of the hot air “b” flowing in thehot air passage 7 is adjusted. - In this connection, in FIG. 1, the sealing
face 8 b provided on the case side is located between thecold air passage 8 b and thehot air passage 7. When the windingshaft 9 c for the cold air is moved to the position of the sealingface 8 b located at the intermediate position in the vertical direction, thecold air passage 6 is fully closed by thethin film member 9 a for the cold air. When the windingshaft 10 c for the hot air is moved to the position of the sealingface 8 b, thehot air passage 7 is fully closed by thethin film member 10 a for the hot air. - Inside the
case 2, theair mixing portion 17 is formed on the downstream side (the rear side of the vehicle) of thecold air passage 6. In thisair mixing portion 17, the cold air “a” sent from thecold air passage 6 and the hot air “b” sent from thehot air passage 7 are mixed with each other. In this connection, thehot air passage 7 is bent upward on the downstream side (the rear side of the vehicle) of theheater core 5. Therefore, the hot air “b” flows toward theair mixing portion 17 arranged in the upper portion of theheater core 5. - In the upper portion of the
case 2 on the rear side of the vehicle, theblowing opening portion 18 is formed being adjacent to theair mixing portion 17. Conditioned air, the temperature of which has been adjusted in theair mixing portion 17, is blown out from thisblowing opening portion 18. Specifically, as theblowing opening portion 18, the following opening portions are provided. There are provided a foot opening portion from which conditioned air is blown out toward the feet of the passenger, a face opening portion from which conditioned air is blown out toward the upper half of the body of the passenger and a defroster opening portion from which conditioned air is blown out toward the inner face of the windshield. The plurality of blowing openingportions 18 are changed over so that they can be opened and closed according to the blowing mode door not shown in the drawing. - FIG. 5 is a block diagram of the electric control section of this embodiment. The air
conditioner control unit 20 is composed of a well known microcomputer, which includes CPU, ROM and RAM, and peripheral circuits. The control program for controlling the air conditioner is stored in ROM. According to the control program, various calculations and processing are conducted. The sensor detecting signals sent from a group of sensors 21 and the operation signals sent from the air conditioner panel 22 are inputted onto the input side of the airconditioner control unit 20. - The group of sensors21 include: a well known outside
air temperature sensor 21 a; an inside air temperature sensor 21 b; asunshine sensor 21 c; an evaporator blowing air temperature sensor 21 d; and a hot water (engine coolant)temperature sensor 21 c. - The air conditioner panel22 includes: a well known
temperature setting switch 22 a; an inside and outsideair changeover switch 22 b; a blowing mode switch 22 c; a air volume changeover switch 22 d; and anair conditioner switch 22 e for turning on and off the operation of the refrigerating cycle compressor not shown in the drawing. - The electromagnetic clutch23, not shown, of the compressor, the
blower drive motor 24, not shown, of the blower unit, theactuator 25, not shown, for driving the inside and outside air changeover door, theactuator 26, not shown, for driving the blowing mode changeover door, the actuator 11 for driving the windingshaft 9 c of theair mixing door 9 for the cold air and theactuator 12 for driving the windingshaft 10 c of theair mixing door 10 for the hot air are connected to the output side of the airconditioner control unit 20. Operation of these devices is controlled by the output signals sent out from the airconditioner control unit 20. - Operation of the present embodiment, composed as described, above will be explained below. The air
conditioner control unit 20 reads in the detection signals sent from the group of sensors 41 and the operation signals sent from the air conditioner panel 42 and calculates the target blowing temperature TAO of air blowing out from theblowing opening portion 18 into the vehicle compartment. This target blowing temperature TAO is the temperature of a air blown out into the vehicle compartment which is necessary for maintaining the temperature in the vehicle compartment at the setting temperature Tset which has been set by thetemperature setting switch 22 a irrespective of the fluctuation of the air conditioning heat load. As well known, TAO is calculated according to this setting temperature Tset and also according to the outside temperature Tam, the inside temperature Tr and the quantity of sunshine Ts which are detected by thesensors 21 a to 21 c. - The air
conditioning control unit 20 individually determines the operating position of theair mixing door 9 for the cold air and the operating position of theair mixing door 10 for the hot air according to the target blowing temperature TAO, the evaporator blowing air temperature Te and the hot water temperature Tw and controls the operating positions of theair mixing door 9 for the cold air and theair mixing door 10 for the hot air. In this way, the temperature of the air blown out into the vehicle compartment can be controlled so that it can become the target blowing temperature TAO. - Referring to FIGS. 6 and 7, operational position control of the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air will be specifically explained as follows. FIG. 6A shows a state in which thethin film member shaft shaft air mixing door 9 for the cold air or theair mixing door 10 for the hot air is moved to a position closest to the fixing position of one end portion of thethin film member cold air passage 6 and thehot air passage 7 are fully opened. - On the other hand, FIG. 6B shows a state in which the
thin film member shaft shaft air mixing door 9 for the cold air or theair mixing door 10 for the hot air is moved to a position most distant from the fixing position of one end portion of thethin film member cold air passage 6 and thehot air passage 7 are fully closed by thethin film members - The position at which the winding
shaft shaft - In FIG. 7A, the axis of abscissa represents the moving position of the winding
shaft - In the case where the air conditioner is set at the maximum cooling state in which the air blown out into the vehicle compartment is cooled at the maximum according to the target blowing temperature TAO calculated by the air
conditioning control unit 20, theair mixing door 9 for the cold air or theair mixing door 10 for the hot air is operated at the operating position shown in FIG. 7B. - Specifically, the operation is conducted as follows. The winding
shaft 9 c of theair mixing door 9 for the cold air is moved to the passage fully opened position “0”, by the actuator 11, so as to fully open thecold air passage 6. At the same time, the windingshaft 10 c of theair mixing door 10 for the hot air is moved to the passage fully closed position “100” so as to fully close thehot air passage 7. Due to the foregoing, all the cold air “a”, which has been cooled by theevaporator 4, passes through thecold air passage 6 and blows out from theblowing opening portion 18 into the vehicle compartment, and the maximum cooling performance can be exhibited. - Next, FIG. 7C shows a state in which the target blowing temperature TAO rises and the operating positions of the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air are moved a little from the maximum cooling position to the temperature control region. Specifically, the operation is conducted as follows. The windingshaft 9 c of theair mixing door 9 for the cold air is maintained at the passage fully opened position “0”, and the fully opened state of thecold air passage 6 is maintained. On the other hand, the windingshaft 10 c of theair mixing door 10 for the hot air is moved to an intermediate position “50” between the passage fully closed position “100” and the passage fully opened position “0”. Due to the foregoing, thethin film member 10 a of theair mixing door 10 for the hot air opens thehot air passage 7 by about 50%. - Accordingly, a portion of the cold air, which has passed through the
evaporator 4, flows into thehot air passage 7 and becomes the hot air “b”. This hot air “b” is mixed with the cold air “a”. Therefore, the temperature of the air blowing into the vehicle compartment can be raised. - Next, FIG. 7D shows a state in which the temperature of the air blown into the vehicle compartment is raised higher than the state shown in FIG. 7C. Specifically, both the winding
shaft 9 c of theair mixing door 9 for the cold air and the windingshaft 10 c of theair mixing door 10 for the hot air are operated so that the winding shafts move to the passage fully opened position “0”. Accordingly, both thecold air passage 6 and thehot air passage 7 are fully opened. Due to the foregoing, compared with the state shown in FIG. 7C, a rate of the volume of the hot air “b” is increased, and the temperature of the air blown out into the vehicle compartment can be raised. - Further, since both the
cold air passage 6 and thehot air passage 7 are fully opened, the passage area in thecase 2 can be maximized. Accordingly, a pressure loss of draft in thecase 2 can be minimized. Especially, the state shown in FIG. 7D, that is, the intermediate temperature control state is a control region most frequently used through the year. Therefore, the generation of blower noise, which is generated when the air conditioner is operated, and the consumption of electric power by theblower drive motor 24 can be effectively reduced. - Next, FIG. 7E shows a state in which the temperature of the air blown into the vehicle compartment is raised higher than the state shown in FIG. 7D. Specifically, while the winding
shaft 10 c of theair mixing door 10 for the hot air is being maintained at the passage fully opened position “0”, the windingshaft 9 c of theair mixing door 9 for the cold air is moved to the neighborhood of the intermediate position “50” between the passage fully closed position “100”, and the passage fully opened position “0”. Due to the above operation, thecold air passage 6 is half opened, and a volume of the cold air is decreased and a volume of the hot air is increased. Accordingly, the blowing air temperature can be raised. - Next, FIG. 7F shows a state which is set at the maximum heating state in which the temperature of the air blown out into the vehicle compartment is heated to the maximum temperature. Specifically, while the winding
shaft 10 c of theair mixing door 10 for the hot air is being maintained at the passage fully opened position “0”, the windingshaft 9 c of theair mixing door 9 for the cold air is moved to the passage fully closed position “100”. Due to the foregoing, thehot air passage 7 is fully opened and thecold air passage 6 is fully closed. Therefore, all blast, which has passed through theevaporator 4, can be heated by theheater core 5, and the maximum heating performance can be exhibited. - In this connection, both the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air are composed of a film door made ofthin film member thin film member shaft shaft cold air passage 6 and thehot air passage 7 are changed. Therefore, the passage areas of thecold air passage 6 and thehot air passage 7 can be substantially proportionally changed according to the changes in the operating position of the windingshafts - As a result, when the operating positions of the winding
shafts motor 24 for driving the blower can be compatible with an improvement in the temperature control characteristic in the neighborhoods of the maximum cooling state and the maximum heating state. - According to the operating mechanisms of the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air of the present embodiment, the following effects can be provided. - (1) While one end portion of the
thin film member air mixing door 9 for the cold air or theair mixing door 10 for the hot air is being fixed to thecase 2, the other end portion of thethin film member shaft case 2 side, or alternatively, the other end portion of thethin film member shaft thin film members - Therefore, no sliding friction is generated between both the
thin film members case 2, and both thethin film members thin film members - (2) Since no sliding friction is caused on both the
thin film members thin film members thin film members - (3) Since no sliding friction is caused in both the
thin film members - (4) Since the
pinions shafts case 2 side, the windingshafts shafts - Finally, an explanation will be given of another embodiment.
- In the aforementioned embodiment, one end portion of the
thin film member air mixing door 9 for the cold air or theair mixing door 10 for the hot air is fixed to thecase 2 side, and the other end portion of thethin film member shaft thin film member shaft cold air passage 6 and thehot air passage 7 can be changed. However, it should be noted that the present invention is not limited to the above specific door structure, and the door structure can be deformed as follows. - For example, as described in Japanese Unexamined Patent Publication No. 2002-79819, the following constitution may be adopted. A sliding door is used, in which a flexible thin film member is slid on a sealing face on the case side so as to compose the
air mixing door 9 for the cold air and theair mixing door 10 for the hot blast. - To be specific, when the thin film member of the
air mixing door 9 for the cold air and the thin film member of theair mixing door 10 for the hot air are respectively slid on the sealing faces on the case side along the guide grooves formed on the case side, the passage (opening) areas of thecold air passage 6 and thehot air passage 7 can be independently changed as shown in FIG. 7. - Accordingly, even when the passage areas of the
cold air passage 6 and thehot air passage 7 are changed by theair mixing door 9 for the cold air and theair mixing door 10 for the hot air composed of the sliding door described in Japanese Unexamined Patent Publication No. 2002-79819, a pressure loss in draft in the intermediate temperature region can be reduced. Further, the temperature control characteristic in the neighborhoods of the maximum cooling state and the maximum heating state can be improved. - However, this variation is disadvantageous as follows. As the thin film member slides on the sealing face provided on the case side, a sliding resistance is generated between the thin film member and the sealing face provided on the case side.
- Alternatively, the following constitution may be adopted. The
air mixing door 9 for the cold air and theair mixing door 10 for the hot air are composed of not a flexible thin film member but a solid sliding door. When this solid sliding door is slid on the sealing face provided on the case side, the passage areas of thecold air passage 6 and thehot air passage 7 are independently changed as shown in FIG. 7. - After all, the
air mixing door 9 for the cold air and theair mixing door 10 for the hot air may be composed of a sliding door for adjusting the passage area when sliding door slides in a direction perpendicular to the direction of air flow in thecold air passage 6 and thehot air passage 7. - While the invention has been described by reference to specific embodiments chosen for purposes of illustration, it should be apparent that numerous modifications could be made thereto by those skilled in the art without departing from the basic concept and scope of the invention.
Claims (5)
1. An air conditioner for vehicle use comprising:
a cold air passage (6) in which a cold air flows;
a hot air passage (7) in which a hot air flows;
an air mixing door (9) for the cold air for adjusting a passage area of the cold air passage (6); and
an air mixing door (10) for the hot air for adjusting a passage area of the hot air passage (7),
wherein
both the air mixing door (9) for the cold air and the air mixing door (10) for the hot air are composed of a sliding door for adjusting the passage area when the air mixing door (9) for the cold air and the air mixing door (10) for the hot air are slid in a direction perpendicular to the flow of air in both the passages (6, 7), and
while one of the air mixing door (9) for the cold air and the air mixing door (10) for the hot air is maintaining one of the passages (6, 7) in a fully opened state, an operating position of the other door is adjusted so that a passage area of the other passage is adjusted and a temperature of the air blowing out into a vehicle compartment is adjusted.
2. An air conditioner for vehicle use according to claim 1 , wherein
a maximum cooling state is set when the cold air passage (6) is fully opened by the air mixing door (9) for the cold air and the hot air passage (7) is fully closed by the air mixing door (10) for the hot air,
a maximum heating state is set when the cold air passage (6) is fully closed by the air mixing door (9) for the cold air and the hot air passage (7) is fully opened by the air mixing door (10) for the hot air, and
a state in which both passages are simultaneously fully opened, in which the cold air passage (6) is fully opened by the air mixing door (9) for the cold air and the hot air passage (7) is fully opened by the air mixing door (10) for the hot air, is set in an intermediate temperature control region formed between the maximum cooling state and the maximum heating state.
3. An air conditioner for vehicle use according to claim 1 , wherein the sliding door composing the air mixing door (9) for the cold air or the air mixing door (10) for the hot air is composed of a flexible thin film member (9 a, 10 a).
4. An air conditioner for vehicle use according to claim 3 wherein, when one end portion of the thin film member (9 a, 10 a) is fixed and the other end portion of the thin film member (9 a, 10 a) is moved in a direction so that the other end portion can be separated from or come close to one end portion, the length of the thin film member (9 a, 10 a) from one end portion in the opening portion of the cold air passage (6) or the hot air passage (7) is changed, and the passage area of the cold air passage (6) or the hot air passage (7) is changed.
5. An air conditioner for vehicle use according to claim 4 wherein, when the other end portion of the thin film member (9 a, 10 a) is connected to the winding shaft (9 c, 10 c) and the winding shaft (9 c, 10 c) is moved being rotated in a direction so that the winding shaft (9 c, 10 c) can be separated from, or come close to, one end portion of the thin film member (9 a, 10 a), the other end portion of the thin film member (9 a, 10 a) is wound by the winding shaft (9 c, 10 c) or leaves the winding shaft (9 c, 10 c).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/455,853 US7779900B2 (en) | 2003-03-07 | 2009-06-08 | Air conditioner for vehicle use |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003061583A JP3956869B2 (en) | 2003-03-07 | 2003-03-07 | Air conditioner for vehicles |
JP2003-061583 | 2003-03-07 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/455,853 Division US7779900B2 (en) | 2003-03-07 | 2009-06-08 | Air conditioner for vehicle use |
Publications (1)
Publication Number | Publication Date |
---|---|
US20040194947A1 true US20040194947A1 (en) | 2004-10-07 |
Family
ID=33094807
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/793,514 Abandoned US20040194947A1 (en) | 2003-03-07 | 2004-03-04 | Air conditioner for vehicle use |
US12/455,853 Expired - Fee Related US7779900B2 (en) | 2003-03-07 | 2009-06-08 | Air conditioner for vehicle use |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/455,853 Expired - Fee Related US7779900B2 (en) | 2003-03-07 | 2009-06-08 | Air conditioner for vehicle use |
Country Status (2)
Country | Link |
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US (2) | US20040194947A1 (en) |
JP (1) | JP3956869B2 (en) |
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EP1630015A1 (en) * | 2004-08-27 | 2006-03-01 | Delphi Technologies, Inc. | Valve driving mechanism for an HVAC system |
US20060053815A1 (en) * | 2004-09-15 | 2006-03-16 | Denso Corporation | Air conditioner for vehicle use |
US20070137833A1 (en) * | 2005-12-19 | 2007-06-21 | Sungho Kang | Dual zone type air conditioner for vehicles |
US20090032758A1 (en) * | 2004-08-27 | 2009-02-05 | Stevenson Mark W | Valve driving mechanism for an hvac system |
US20090078392A1 (en) * | 2006-04-28 | 2009-03-26 | Behr Gmbh & Co. Kg | Motor vehicle air conditioning arrangement |
US20100000820A1 (en) * | 2006-09-19 | 2010-01-07 | Schlumberger Technology Corporation | Pressure-balanced electromechanical converter |
US20130008627A1 (en) * | 2011-07-06 | 2013-01-10 | Denso Corporation | Air conditioner for vehicle |
US20130160971A1 (en) * | 2011-12-26 | 2013-06-27 | Calsonic Kansei Corporation | Vehicle air conditioner |
US20150107815A1 (en) * | 2011-12-27 | 2015-04-23 | Denso Corporation | Vehicular air conditioner |
US10457112B2 (en) | 2017-06-19 | 2019-10-29 | Thermo King Corporation | Configurable evaporator unit air outlets for a secondary HVAC system |
USD877871S1 (en) | 2017-06-19 | 2020-03-10 | Thermo King Corporation | Evaporator unit |
US10611209B2 (en) | 2017-01-04 | 2020-04-07 | Denso International America, Inc. | HVAC unit |
US20220016954A1 (en) * | 2020-07-16 | 2022-01-20 | Air International (Us) Inc. | Hvac temperature stratification door systems and methods |
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DE502004004081D1 (en) * | 2004-03-03 | 2007-07-26 | Behr France Rouffach Sas | Air conditioning device, in particular for a Krafffahrzeug |
WO2009075275A1 (en) * | 2007-12-10 | 2009-06-18 | Calsonic Kansei Corporation | Vehicle air conditioner |
GB2471275B (en) * | 2009-06-22 | 2011-12-14 | Gbr Ind Ltd | Air cooler shield system |
US20120222851A1 (en) * | 2011-03-04 | 2012-09-06 | GM Global Technology Operations LLC | Hvac system damper |
US9447616B2 (en) * | 2013-08-12 | 2016-09-20 | Vinylast, Inc. | Window opening control device |
JP2015196451A (en) * | 2014-04-01 | 2015-11-09 | 株式会社デンソー | Air conditioning device |
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Also Published As
Publication number | Publication date |
---|---|
US20090250194A1 (en) | 2009-10-08 |
US7779900B2 (en) | 2010-08-24 |
JP3956869B2 (en) | 2007-08-08 |
JP2004268709A (en) | 2004-09-30 |
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Owner name: DENSO CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ITO, KOJI;TOKUNAGA, TAKAHIRO;OKUMURA, YOSHIHIKO;REEL/FRAME:015052/0533 Effective date: 20040220 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |