JP4946791B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner including a cold air passage through which cool air that has passed through a cooling heat exchanger flows without passing through a heat exchanger for cooling, and a cold air bypass passage provided alongside the cold air passage.

  The vehicle air conditioner according to the first prior art has a cold air bypass door in addition to the air mix door (see, for example, Patent Document 1). The cold air bypass door adjusts the amount of cold air flowing from the cold air bypass passage to the face outlet according to the opening degree. In this way, the air temperature is adjusted, and cold air is mainly blown from the face air outlet and warm air is mainly blown from the foot air outlet, so that a so-called cold head heat condition can be obtained, Various modes such as a vent mode in which cold air is blown out only from the outlet can be set.

  Such a vehicle air conditioner has tanks above and below the evaporator. As a result, sound generation is greatest in the upper tank where the refrigerant inflow portion is located, and the cold air bypass passage is often disposed in the vicinity of the upper tank due to restrictions due to the configuration of the evaporator. Thereby, the refrigerant passing sound generated from the upper side of the evaporator is sequentially radiated into the vehicle interior via the evaporator, the cold air bypass door and the cold air side air mix door, and each air outlet, particularly the face air outlet. Therefore, a large refrigerant passing sound was radiated from the face outlet, giving the passengers an uncomfortable feeling.

  As countermeasures against such a refrigerant passing sound problem, for example, (1) reducing the capacity of the expansion valve, (2) rectifying the refrigerant immediately after expansion, as countermeasures on the refrigerant passing sound source side (evaporator side), ( There are four measures such as 3) damping of the evaporator and (4) damping of the unit case. However, there is a problem that the contradiction to the countermeasures on the generation source side is large with the contradiction to the cooling performance, the high cost, and the weight increase.

The vehicle air conditioner according to the second prior art is the remaining configuration excluding the cold air bypass door from the vehicle air conditioner according to the first prior art, and the refrigerant passing sound generated from the expansion valve and the evaporator. Is prevented from being transmitted to the occupant so that the opening corresponding to the face outlet is closed for a predetermined time from the time of activation (see, for example, Patent Document 2).
Japanese Patent Laid-Open No. 3-96426 JP 2002-36869 A

  The condition that the refrigerant passing sound becomes the largest is when the vehicle air conditioner is started when the temperature in the passenger compartment after the vehicle is left is high, and when the blower speed is low and the ventilation sound is low. In this state, the vehicle air conditioner is normally used in the maximum cooling (MaxCool) state of the face mode, so the cold air bypass door, the air mix door, and the face door are fully opened. At the time of such maximum cooling, there is a problem that especially the refrigerant passing sound becomes loud.

  On the other hand, in the second prior art described above, the opening corresponding to the face outlet is closed, so that cold air is sent to the head of the occupant despite the high cabin temperature during maximum cooling. There is no problem.

  Further, if the second conventional technique is applied to the first conventional technique, the opening corresponding to the face outlet is only closed. There is a problem of not being sent.

  In the second prior art, even when the maximum cooling state is required at the time of startup, the foot core is used in the maximum heating (MaxHot) state in order to isolate the refrigerant passing sound, and the sound insulation effect by the heater core is achieved. It has gained. Even though the refrigerant passing noise can be reduced by this, there is a problem that warm air is given to the passenger's feet despite the high cabin temperature.

  Therefore, the present invention has been made in view of the above-described problems, and provides a vehicle air conditioner that has a cold air bypass passage and can reduce refrigerant passing sound without causing discomfort to the occupant. For the purpose.

  The present invention employs the following technical means in order to achieve the aforementioned object.

The present invention includes an air conditioning case (10) that forms an air passage;
A blower (15) for blowing air into the air conditioning case;
A cooling heat exchanger (9) which is provided in the air conditioning case and has an inflow portion (29) to which a refrigerant is supplied and which cools the air blown by the blower;
A heating heat exchanger (16) provided in the air conditioning case for heating the cold air from the cooling heat exchanger;
A cold air passage (17) provided in the air conditioning case and through which the cold air that has not passed through the heating heat exchanger flows;
A hot air side air mix door (20) which is provided in the air conditioning case and adjusts the amount of air passing through the heat exchanger for heating;
A cold air side air mix door (21) that is provided in the air conditioning case and adjusts the amount of air passing through the cold air passage;
A mixing chamber (23) provided in the air conditioning case, in which the hot air from the heating heat exchanger and the cold air from the cold air passage are mixed;
A face opening (19) for guiding the conditioned air that has passed through the mixing chamber to the passenger's head and chest in the passenger compartment;
A foot opening (25) for guiding the conditioned air that has passed through the mixing chamber to the feet of passengers in the passenger compartment;
A door (26) for adjusting the amount of air blown from the face opening;
A door (28) for adjusting the amount of air blown from the foot opening;
A passage that is provided inside the air conditioning case and is arranged in parallel to the cold air passage and allows cold air that has not passed through the heat exchanger for heating to pass toward the face opening, and exchanges heat with the face opening. A cold air bypass passage (18) provided on a path connecting the inflow portion of the vessel,
A cold air bypass door (22) that is provided in the air conditioning case and adjusts the amount of air passing through the cold air bypass passage;
According to the air conditioning requirements in the passenger compartment, the air flow rate of the blower and the opening of the face opening door, foot opening door, hot air side air mix door, cold air side air mix door and cold air bypass door are individually adjusted. Control means (4) for
The control means
According to the air-conditioning request, in the blow-out mode where at least the foot opening is in the open state, the blow-off mode is maintained and the cold air bypass is maintained until the predetermined release condition is satisfied from the start of the vehicle air conditioner (1). Adjust the opening of the door to an opening that prevents the refrigerant passing sound generated from the inflow part of the cooling heat exchanger from being transmitted to the face opening,
When the release condition is satisfied, the opening adjustment of the cold air bypass door is released, and the opening adjustment according to the air conditioning request in the vehicle interior is executed.

  According to the present invention, the cold air bypass passage is provided on a path connecting the face opening and the inflow portion of the cooling heat exchanger. Since the refrigerant passing sound becomes louder when the refrigerant flows into the cooling heat exchanger, the inflow portion becomes the main generation source of the refrigerant passing sound. The refrigerant passing sound generated from such an inflow portion is easily transmitted to the face opening through the cold air bypass passage. In the present invention, in the configuration in which the inflow portion and the face opening portion are in the positional relationship as described above, the control means adjusts the opening degree of the cold air bypass door until the release condition is satisfied. Thus, until the release condition is satisfied, the cold air bypass door prevents the refrigerant transmission sound generated from the inflow portion from being transmitted to the face opening.

  In addition, the control means adjusts the opening degree of the cold air side air mix door according to the air conditioning requirements in the passenger compartment regardless of whether the release condition is satisfied. Cold wind is given to the passenger's head and chest. Therefore, until the release condition is satisfied, the amount of cold air is limited by the opening of the cold air bypass door, but cold air is sent to the face opening through the cold air side air mix door. As a result, the refrigerant passing sound is prevented from being transmitted by the cold air bypass door until the release condition is satisfied from the start-up even during maximum cooling, and the cold air is sent by the cold air side air mix door, so that the refrigerant transmitted to the occupant The passing sound can be blocked and cool air can be given to the passenger's head and chest. Therefore, it is possible to provide a comfortable environment for the passenger.

  Further, the present invention can be realized by simply controlling the opening degree of the cold air bypass door without changing the mechanical configuration of the existing vehicle air conditioner. Therefore, the present invention can be easily realized.

  In the invention, it is preferable that the release condition is when a predetermined time has elapsed since the start of the vehicle air conditioner.

  According to the present invention, since the release condition is when a predetermined time has elapsed since the start of the vehicle air conditioner, the sound insulation is exhibited when the refrigerant passage sound at the start increases, and the refrigerant passage sound is small. When it becomes, the opening degree of the cold air bypass door can be fully opened. Thus, the opening degree of the cold air bypass door can be adjusted in the direction in which the opening of the cold air bypass door is closed only during a period when the refrigerant passing sound is large.

  Furthermore, the present invention is characterized in that the release condition is when the rotational speed of the blower is equal to or higher than a predetermined rotational speed.

  According to the present invention, since the release condition is when the rotational speed of the blower is equal to or higher than a predetermined rotational speed, the sound insulation is exhibited when the refrigerant passing sound increases, and the cold air bypass is performed when the refrigerant passing sound is reduced. The opening of the door can be fully opened. Thus, the opening degree of the cold air bypass door can be adjusted in the direction in which the opening of the cold air bypass door is closed only during a period when the refrigerant passing sound is large.

Furthermore, the present invention further includes temperature detection means for detecting the temperature of the air cooled by the cooling heat exchanger,
The release condition is characterized in that the temperature detected by the temperature detecting means is equal to or lower than a predetermined temperature.

  According to the present invention, the cancellation condition is when the temperature detected by the temperature detecting means is equal to or lower than a predetermined temperature, so that when the refrigerant passing sound increases, the sound insulation is exhibited and the refrigerant passing sound is reduced. In addition, the opening degree of the cold air bypass door can be fully opened. Thus, the opening degree of the cold air bypass door can be adjusted in the direction in which the opening of the cold air bypass door is closed only during a period when the refrigerant passing sound is large.

  Furthermore, the present invention is characterized in that the control means adjusts the opening degree of the cold air bypass door to an opening degree that closes the cold air bypass passage until the release condition is satisfied.

  According to the present invention, the control means adjusts the opening degree so as to close the cold air bypass door until the release condition is satisfied, so that it is possible to reliably prevent the refrigerant passing sound from being transmitted through the cold air bypass passage. it can.

Further, in the present invention, the cooling heat exchanger has an inflow portion at an upper end (9a) in the vertical direction (Y1, Y2) (Y1),
The cold air bypass door is provided facing the upper end of the cooling heat exchanger,
The cold air side air mix door is provided to face the intermediate portion (9b) in the vertical direction of the cooling heat exchanger,
The hot air side air mix door is provided so as to be opposed to the lower end (9c) in the vertical direction (9c) of the cooling heat exchanger.

  According to the present invention, the cold air bypass door is provided to face the upper end of the cooling heat exchanger. Since the inflow portion is provided at the upper end of the cooling heat exchanger, the cold air bypass door can reliably prevent the refrigerant passing sound generated by the inflow portion from being transmitted to the face opening. Moreover, since a refrigerant | coolant flows in into the heat exchanger for cooling from an inflow part, the upper side of a heat exchanger for cooling can cool more the air which passes rather than the lower side. Therefore, since the cold wind bypass door faces the upper end of the cooling heat exchanger, the most cooled air can be sent to the face opening.

  The hot air side air mix door is provided to face the lower end of the cooling heat exchanger. As described above, air is not cooled on the lower side of the cooling heat exchanger than on the upper side. As a result, the high-temperature air that has passed through the warm air side air mix door can be efficiently heated by the heat exchanger for heating.

  Furthermore, the present invention is characterized in that the maximum amount of air that can pass through the cold air bypass passage is smaller than that of the cold air passage.

  According to the present invention, the maximum amount of air that can be passed through the cold air bypass passage is smaller than that of the cold air passage. Even if it adjusts so that the opening degree of a cold wind bypass door may be closed by this, cold air can be sent from a face opening part by adjusting the opening degree of a cold wind side air mix door.

Further, according to the present invention, the cold air bypass door includes a door body (22a) formed in a plate shape,
The cold air bypass door is configured by a butterfly door provided with a rotation shaft (22b) at an intermediate portion of the door body in the door width direction.

  According to the present invention, since the cold air bypass door is configured as a butterfly door, the distance from the rotating shaft to the end is small, so the opening degree can be adjusted with a small driving force.

Further, according to the present invention, the cold air bypass door includes a door body (22c) formed in a plate shape,
The cold air bypass door is configured by a cantilever door provided with a rotation shaft (22d) at one end in the door width direction of the door body.

  According to the present invention, since the cold air bypass door is configured as a cantilever door, the opening degree of the cold air bypass door can be adjusted with a simple configuration.

  In addition, the code | symbol in the bracket | parenthesis of each above-mentioned means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

  Hereinafter, a plurality of embodiments for carrying out the present invention will be described with reference to the drawings. Portions corresponding to the matters described in the preceding forms in each embodiment are denoted by the same reference numerals, and overlapping description may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view schematically showing a vehicle air conditioner 1 according to the present embodiment. The vehicle air conditioner 1 is an auto air conditioner that automatically controls the temperature in the passenger compartment to maintain an air conditioning request set by the passenger, for example, the set temperature. The vehicle air conditioner 1 includes an air conditioner unit 2 for air conditioning a vehicle interior, a refrigeration cycle apparatus 3 in which a refrigerant that absorbs and cools air blown in the air conditioner unit 2 flows, an air conditioner unit 2 and a refrigeration cycle apparatus 3 And an air conditioning control device 4 for controlling the air conditioner.

  First, the refrigeration cycle apparatus 3 will be described. The refrigeration cycle apparatus 3 constitutes a cycle formed so that the refrigerant circulates from the discharge side of the compressor 5 to the evaporator 9 through the condenser 6, the receiver 7, and the expansion valve 8 which is a decompression means. Yes. The refrigerant flow path on the discharge side of the compressor 5 is provided with a pressure sensor (not shown) that detects the pressure of the refrigerant in the refrigeration cycle.

  The compressor 5 is driven by an engine (not shown) mounted on the vehicle. The compressor 5 may have a fixed discharge capacity or a variable discharge capacity. The compressor 5 includes a variable capacity mechanism (not shown) when the discharge capacity is variable, and is configured such that the discharge capacity is variably controlled by a command given from the air conditioning control device 4. When the capacity variable mechanism is constituted by an electromagnetic valve mechanism, for example, the discharge capacity of the compressor 5 is varied by the supplied control current. This discharge capacity changes according to the control current supplied to the capacity variable mechanism, and the capacity increases as the control current increases, and the refrigerant discharge flow rate also increases. Accordingly, the compressor 5 is configured to be able to continuously change the discharge capacity in the range of about 0% to 100%.

  The refrigerant in the refrigeration cycle apparatus 3 is compressed to high temperature and high pressure by the compressor 5, and the high-pressure gas refrigerant discharged from the compressor 5 is introduced into the condenser 6, where the gas refrigerant is cooled by an electric fan for cooling ( The heat is exchanged with the outside air blown by an air (not shown) to be dissipated and condensed. The refrigerant that has passed through the condenser 6 is separated into a liquid-phase refrigerant and a gas-phase refrigerant in the receiver 7, and the liquid-phase refrigerant is stored in the receiver 7.

  The high-pressure liquid refrigerant from the receiver 7 is decompressed to a low-pressure gas-liquid two-phase state by the expansion valve 8, and the decompressed low-pressure refrigerant is supplied to the evaporator 9. The evaporator 9 has an inflow portion 29 to which the refrigerant is supplied from the expansion valve 8, and the low-pressure refrigerant supplied from the expansion valve 8 absorbs heat from the blown air and is evaporated in the evaporator 9. Since the evaporator 9 is housed in the air conditioning case 10 constituting the air conditioner unit 2, the evaporator 9 cools the air in the air conditioning case 10. The gas refrigerant evaporated in the evaporator 9 is again sucked into the compressor 5 and compressed.

  The evaporator 9 has an inflow portion 29 on one end Y1 of the predetermined vertical direction Y1, Y2 or on the end 9a (inlet side tank) of the upper Y1, which is one of the vertical directions in this embodiment. Therefore, the expansion valve supplies the refrigerant from the inflow portion 29 of the end 9 a on the upper Y1 side of the evaporator 9. The opening degree of the expansion valve 8 is automatically adjusted so that the refrigerant superheat degree at the outlet of the evaporator 9 is maintained at a predetermined value. Of the refrigeration cycle apparatus 3, the compressor 5, the condenser 6, the receiver 7, and the like are disposed in an engine room (not shown).

  Next, the air conditioner unit 2 will be described. The air conditioning case 10 constituting the air conditioner unit 2 is used as a front seat air conditioning unit that is provided in an instrument panel (not shown) in front of the vehicle and air-conditions a region on the front seat side of the vehicle interior. In FIG. 1, the thickness dimension of the air conditioning case 10 is omitted for easy understanding. The air conditioning case 10 forms an air passage through which air is blown toward the passenger in the vehicle interior, and an inside / outside air switching box 13 having an inside air introduction port 11 and an outside air introduction port 12 at the most upstream portion of the air passage. It has. An inside / outside air switching door 14 is rotatably arranged in the inside / outside air switching box 13. The inside / outside air switching door 14 is driven by a servo motor (not shown), and an inside air mode for introducing inside air (vehicle compartment air) from the inside air introduction port 11 and outside air (outside the vehicle compartment) from the outside air introduction port 12. It is possible to switch between the outside air mode for introducing air).

  On the downstream side of the inside / outside air switching box 13, a blower 15 for generating an air flow toward the vehicle interior is disposed. The blower 15 is a blower that blows air into the air conditioning case 10, and is configured to drive a centrifugal blower fan by a motor. On the downstream side of the blower 15, an evaporator 9 that constitutes the refrigeration cycle apparatus 3 and cools the air flowing in the air passage is disposed. The evaporator 9 is a cooling heat exchanger that cools air blown by the blower 15. The temperature of the evaporator 9 is detected by an evaporator temperature sensor (not shown) constituted by, for example, a fin sensor. The temperature of the air cooled by the evaporator 9, that is, the air temperature downstream of the evaporator 9, is detected by a post-evaporator temperature sensor (not shown) that functions as temperature detecting means.

  A heater core 16 for heating the air cooled by the evaporator 9 is disposed on the downstream side of the evaporator 9 in the air conditioning case 10. The heater core 16 is a heating heat exchanger that heats the air that has passed through the evaporator 9 using engine cooling water or the like as a heat source, and a cold air passage 17 and a cold air flow through which air that does not pass through the heater core 16 flows to the side. A bypass passage 18 is formed. The temperature of engine coolant that is a heat source of the heater core 16 is detected by a water temperature sensor (not shown).

  The cold air passage 17 is formed in a portion on the upper Y1 side of the heater core 16. The cold air passage 17 does not pass through the heater core 16 but allows the cold air that has passed through the evaporator 9 to pass therethrough. The cold air passage 17 is provided on a path connecting a face opening 19 described later and an intermediate portion 9b in the vertical directions Y1 and Y2 of the evaporator 9. Therefore, the cold air passage 17 mainly passes the cold air that has passed through the intermediate portion 9b of the evaporator 9 in the vertical direction Y1, Y2. The path connecting the face opening 19 and the intermediate portion 9b in the vertical direction Y1, Y2 of the evaporator 9 is not limited to a straight line connecting the face opening 19 and the intermediate portion 9b of the evaporator 9, and air smoothly flows. It may be a flowing smooth curve. Therefore, the cold air that has passed through the cold air passage 17 is configured to flow mainly toward the face opening 19.

  The cold air bypass passage 18 is provided in parallel with the cold air passage 17. The cold air bypass passage 18 does not pass through the heater core 16 but allows the cold air that has passed through the evaporator 9 to pass toward the face opening 19. The cold air bypass passage 18 is provided on a path connecting the face opening 19 and the inflow portion 29 of the evaporator 9. Therefore, the cold air bypass passage 18 is formed so that the cold air that has passed through the upper portion Y1 of the evaporator 9 passes mainly. The path connecting the face opening 19 and the inflow portion 29 of the evaporator 9 is not limited to a straight line connecting the face opening 19 and the inflow portion 29 of the evaporator 9, but is a smooth curve through which air smoothly flows. May be. Accordingly, the cold air that has passed through the cold air bypass passage 18 is configured to mainly flow toward the face opening 19.

  The cold air bypass passage 18 is provided close to the inner wall of the upper Y1 of the air conditioning case 10. Further, the cold air bypass passage 18 is set so that the maximum amount of air that can pass through the cold air passage 17 is smaller, for example, the opening area is about half.

  A warm air side air mix door 20 is rotatably disposed between the evaporator 9 and the heater core 16 in the air conditioning case 10. The warm air side air mix door 20 is provided to face the end 9c of the lower portion Y2 of the evaporator 9.

  The hot air side air mix door 20 is driven by a servo motor (not shown), and is configured such that its rotational position and opening degree can be adjusted continuously. The warm air side air mix door 20 includes a door main body 20a formed in a plate shape, and is configured by a cantilever door provided with a rotating shaft 20b at an end portion of the upper Y1 in the door width direction of the door main body 20a. The hot air side air mix door 20 is formed of a rotating shaft 20b and a door main body 20a having a rectangular planar shape by a resin material such as polypropylene and nylon. A seal material (not shown) made of, for example, a rubber-based elastic material is arranged in a frame shape on the outer peripheral edge of the door body 20a. The rotating shaft 20b, the door main body 20a, and the sealing material can be integrally formed in one mold.

  The cold air passage 17 is provided with a cold air side air mix door 21 that adjusts the amount of air passing through the cold air passage 17. The cold air bypass passage 18 is provided with a cold air bypass door 22 that adjusts the amount of air passing through the cold air bypass passage 18. The cold air side air mix door 21 is provided to face the intermediate portion 9b of the evaporator 9 in the vertical direction Y1, Y2. The cold air bypass door 22 is provided to face the end portion 9 a of the upper Y 1 of the evaporator 9. Therefore, the cold air bypass door 22 is provided to face the inflow portion 29 of the evaporator 9.

  Since the cold air bypass door 22 and the cold air side air mix door 21 have the same configuration, only the cold air bypass door 22 will be described, and the description of the cold air side air mix door 21 will be omitted. The cold air bypass door 22 is driven by a servo motor (not shown), and is configured such that its rotational position and opening degree can be adjusted continuously. The cold air bypass door 22 includes a door body 22a formed in a plate shape, and is configured as a butterfly door in which a rotation shaft 22b is provided at an intermediate portion of the door body 22a in the door width direction. The cold air bypass door 22 is formed with a rotating shaft 22b and a rectangular door main body 22a made of a resin material such as polypropylene and nylon. A seal material (not shown) made of, for example, a rubber-based elastic material is arranged in a frame shape on the outer peripheral edge of the door main body 22a. The rotating shaft 22b, the door main body 22a, and the sealing material can be integrally formed in one mold.

  In the air conditioning case 10, a mixing chamber 23 that mixes the warm air from the heater core 16 and the cold air from the cold air passage 17 and the cold air bypass passage 18 is provided. The air sent to the mixing chamber 23 is the hot air side air mix door 20, the cold air side air mix door 21, and the cold air bypass door 22 (hereinafter, these three doors are collectively referred to as "air mix doors 20 to 22"). Is adjusted by adjusting each opening. Therefore, the amount of air passing through the heater core 16 (warm air amount) is adjusted by adjusting the opening degree of the hot air side air mix door 20. Further, the amount of air passing through the cold air passage 17 (cold air amount) is adjusted by adjusting the opening degree of the cold air side air mix door 21.

  Further, the amount of air passing through the cold air bypass passage 18 (cold air amount) is adjusted by adjusting the opening degree of the cold air bypass door 22. Thus, by adjusting the amount of hot air and the amount of cold air, the temperature of the air in the mixing chamber 23 is adjusted, and the temperature of the air blown out into the passenger compartment is adjusted. Further, by adjusting the opening degree of the cold air bypass door 22, only the amount of cold air sent to the face opening 19 can be individually adjusted.

  A defroster (DEF) opening connected to a defroster outlet (not shown) for blowing conditioned air toward the window glass of the vehicle is provided at the most downstream portion of the air passage in the air conditioning case 10 on the downstream side of the mixing chamber 23. Part 24, a face (FACE) opening 19 connected to a face air outlet (not shown) for blowing air-conditioned air toward the head and chest of the occupant, and a foot air outlet (air drawing) for blowing air-conditioned air toward the feet of the passenger A foot (FOOT) opening 25 connected to a not-shown is provided.

  Inside the openings 19, 24 and 25, blowout doors 26 to 28 for adjusting the blowout amount are rotatably attached and driven by actuators (not shown) such as servo motors. Thus, the amount of conditioned air blown from the openings 19, 24, 25 can be individually adjusted.

  The air outlet mode includes a face (FACE) mode in which only the face opening 19 is opened, a foot (FOOT) mode in which only the foot opening 25 is opened, and a bilevel (B) which is an intermediate mode between the face mode and the foot mode. / L) mode, a differential (DEF) mode in which only the defroster opening 24 is opened, and a foot differential (F / D) mode that serves both as a foot mode and a differential mode. The opening and closing of the outlet doors 26 to 28 of the parts 19, 24, and 25 are controlled, and switching of these outlet modes is performed.

  Since the hot air side air mix door 20 is a temperature adjusting means for adjusting the temperature of air blown into the vehicle interior by adjusting the air volume ratio, opening and closing of the cold air side air mix door 21 and the cold air bypass door 22 and hot air The opening and closing of the side air mix door 20 is reversed. In the maximum cooling state in which the blowing temperature is lowered in the face mode or the like, the cold air side air mix door 21 and the cold air bypass door 22 are fully opened, and the hot air side air mix door 20 is fully closed. In the maximum heating state in which the blowing temperature is increased in the foot mode or the like, the cold air side air mix door 21 and the cold air bypass door 22 are fully closed, and the hot air side air mix door 20 is fully opened.

  Next, the air conditioning control device 4 will be described. The air-conditioning control device 4 is a control means of the vehicle air-conditioning device 1 and controls the air-conditioning unit 2 and the refrigeration cycle device 3, for example, the drive output of the compressor 5 that discharges the refrigerant to the evaporator 9 side. The air-conditioning capacity is controlled by varying. Moreover, the air-conditioning control apparatus 4 adjusts individually the air flow rate of the blower 15 and the opening degree of the air mix doors 20 to 22 according to the air-conditioning request in the passenger compartment. The air conditioning control device 4 includes a microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The ROM is an electric control unit that stores a control program for air-conditioning control and performs various calculations and processes based on the control program.

  The air conditioning control device 4 includes various sensors (not shown), for example, an inside air sensor, an outside air sensor, a solar radiation sensor, a pressure sensor, an evaporator temperature sensor, an after-evaporator temperature sensor, and various sensor detection signals from a water temperature sensor, An operation signal is input from an air conditioning control panel (not shown). The air conditioning control panel is disposed in the vicinity of an instrument panel (not shown) in front of the driver's seat in the passenger compartment, and has a plurality of switches operated by passengers including the driver.

  Multiple switches on the air conditioning control panel include a temperature setting switch that outputs a signal of the set temperature in the passenger compartment, a switch that outputs a signal for manually setting the inside air mode and the outside air mode, the aforementioned face mode, bi-level mode, foot Mode, foot defroster mode, and blowing mode switch for outputting a signal for manually setting the defroster mode, an air volume setting switch for outputting a signal for manually setting on / off of the blower 15 and air volume switching of the blower 15, and the compressor 5 An air conditioner switch that switches between an operating state and a stopped state.

  The air conditioning control device 4 is electrically connected with a servo motor and a motor that form electric drive means of each device, and the operation of these devices is controlled by an output signal of the air conditioning control device 4. The air-conditioning control device 4 uses the detected air temperature downstream of the evaporator 9 (or the post-evaporator temperature) and the target air temperature downstream of the evaporator 9 (the target post-evaporator temperature) obtained from the set temperature by the set temperature switch. Based on the above, the control current supplied to the capacity variable mechanism of the compressor 5 is obtained by PID control, the control value of the compressor 5 is determined, and the capacity control is performed. That is, feedback control is performed so that the air temperature on the output side of the evaporator 9 becomes the target air temperature, and control is performed so that the temperature of the conditioned air blown into the vehicle interior becomes an appropriate temperature.

  Next, the air conditioning control process by the air conditioning control device 4 will be described. FIG. 2 is a flowchart showing the air conditioning control processing of the air conditioning control device 4. This flow is started when the ignition switch is turned on and power is supplied to the air conditioning control device 4 to start up. In step a1, execution of a control program stored in advance is started, a part of the stored contents of a data processing memory such as a RAM is initialized, and the process proceeds to step a2.

  In step a2, various data are read into the data processing memory, and the process proceeds to step a3. Therefore, in step a2, operation signals from various switches on the air conditioning control panel and detection signals from various sensors are input.

  In step a3, based on the data read in step a2, the target blowing temperature TAO is calculated by the arithmetic expression stored in the control program, and the process proceeds to step a4.

  In step a4, the blower control voltage to be applied to the motor of the blower 15 is calculated based on the target blowing temperature TAO obtained in step a3, and when the air volume of the blower 15 is determined, the process proceeds to step a5. The blower control voltage is obtained by obtaining a blower control voltage suitable for each target blowing temperature TAO based on a predetermined control characteristic pattern.

  In step a5, the drive output of the compressor 5 is calculated based on the read data and the target blowing temperature TAO, and the process proceeds to step a6. In step a6, each opening degree (%) of the air mix doors 20 to 22 is calculated based on the target blowing temperature TAO obtained in step a3, the stored data, and the calculation formula stored in the control program, and step a7. Move on.

  In step a7, a control signal is output to the blower 15 so as to be the blower control voltage calculated in step a4, and the process proceeds to step a8. In step a8, a control signal is output to the compressor 5 so that the drive output calculated in step a5 is obtained, and the process proceeds to step a9.

  In step a9, a control signal is output to the servomotors of the outlet doors 26 to 28 so as to be in the set outlet mode, and the process proceeds to step a10.

  In step a10, it is determined whether or not a predetermined release condition is satisfied. If satisfied, the process proceeds to step a11. If not satisfied, the process proceeds to step a12. At least one release condition is stored in the ROM, and one release condition is set in advance. The cancellation condition is set based on a parameter having a correlation with the generation state of the refrigerant passing sound from the time of starting the vehicle air conditioner 1. The release condition of the present embodiment is whether or not a predetermined time has elapsed from a start time, for example, a predetermined time of a period of 30 seconds to 60 seconds. Therefore, when the predetermined time is set to 30 seconds, the release condition is satisfied after 30 seconds from the start, and when the predetermined time is set to 60 seconds, the release condition is satisfied after 60 seconds from the start. .

  In step a12, since the release condition is not satisfied, the cold air bypass door 22 is closed, and the cold air side air mix door 21 and the hot air side air mix door 20 are opened to the opening calculated in step a6. A control signal is output to the servo motors 20 to 22, and the process returns to step a10. Therefore, the process of step a12 is repeated until the release condition is satisfied.

  In step a11, since the release condition is satisfied, a control signal is output to the servo motors of the air mix doors 20 to 22 so that the opening calculated in step a6 is reached, and this flow ends.

  Such processing shown in FIG. 2 is repeatedly executed in the power-on state. Accordingly, the opening degree of the cold air bypass door 22 is adjusted to be closed so as to prevent the refrigerant passing sound from being transmitted to the face opening 19 until the release condition is satisfied from the time of startup. Therefore, the refrigerant passing sound can be reliably reduced at the maximum cooling time when the vehicle interior temperature at which the refrigerant passing sound is the highest is high (for example, after the vehicle is left in the sun). If the release condition is satisfied, the cold air bypass door 22 is controlled so as to have the opening calculated in step a6. Therefore, after the cold air bypass door 22 is completely shut for several seconds after starting, the open state is a normal control state. Can be transferred to.

  FIG. 3 is a cross-sectional view schematically showing the vehicle air conditioner 1 that does not satisfy the release condition during maximum cooling. In FIG. 3, the thickness dimension of the air conditioning case 10 is omitted for easy understanding as in FIG. 1. The state of the vehicle air conditioner shown in FIG. 3 does not satisfy the release condition, and is the face mode during maximum cooling. Accordingly, the cold air bypass door 22 completely closes the cold air bypass passage 18, the cold air side air mix door 21 is fully open, the hot air side air mix door 20 is fully closed, and the face opening of the outlet ports 26 to 28 is open. Only the air outlet door 26 provided in the section 19 is fully open, and the remaining air outlet doors 27 and 28 are fully closed.

  As described above, since the main generation source of the refrigerant passing sound is the inflow portion 29, when the vehicle air conditioner 1 is activated, the refrigerant passing sound (indicated by a phantom line in FIG. 3) is sent from the upper Y1 of the evaporator 9 to the blower 15. Is transmitted toward the cold air bypass door 22 and the cold air side air mix door 21 provided to face the evaporator 9. Since the cold air bypass door 22 is closer to the evaporator 9 than the cold air side air mix door 21, the refrigerant passing sound is first blocked by the cold air bypass door 22. The refrigerant passing sound partially blocked by the cold air bypass door 22 is propagated toward the cold air side air mix door 21.

  Moreover, since the cold wind bypass door 22 is provided along the path | route which connects the inflow part 29 of the evaporator 9, and the face opening part 19, the cold wind side air mix door 21 is provided in the remaining path | route. Therefore, the propagation path of the refrigerant passing sound is a path that bypasses the cold air passage 17 where the cold air side air mix door 21 is fully opened and reaches the face opening 19. Therefore, since the passage of the refrigerant passes to reach the face opening 19, a part of the refrigerant is blocked by the cold air side air mix door 21 that is bypassed. As a result, the refrigerant passing sound generated at the inflow portion 29 of the evaporator 9 is blocked by the cold air bypass door 22, and the waveform toward the face opening 19 is reduced.

  FIG. 4 is a graph showing an example of the measurement result of the refrigerant passing sound. The horizontal axis of the graph indicates the analysis frequency, and the vertical axis of the graph indicates the sound pressure level. In FIG. 4, the sound generated from the vehicle air conditioner 1 after leaving the vehicle for a long time, that is, after the hot soak, at the time before satisfying the release condition (after 10 seconds from the start), the vehicle air conditioner 1 Is stopped, the vehicle air conditioner 1 is activated and the cold air bypass door 22 is closed (the state shown in FIG. 3), the vehicle air conditioner 1 is activated and the cold air is It is the result measured in the 3rd state (state of the prior art) which has opened bypass door 22. FIG.

  As shown in FIG. 4, since the stopped first state is a reference state in which no refrigerant passing sound is generated, the sound pressure level is the lowest. Further, when the second state and the third state are compared, the sound pressure level is clearly lower over the entire analysis frequency in the second state in which the cold air bypass door 22 is closed. Therefore, by closing the cold air bypass door 22 until the release condition is satisfied, the transmission of the refrigerant passing sound to the passenger can be suppressed.

  As described above, in the vehicle air conditioner 1 according to the present embodiment, the cold air bypass passage 18 is provided on a path connecting the face opening 19 and the inflow portion 29 provided on the upper Y1 side of the evaporator 9. Since the refrigerant passing sound becomes louder when the refrigerant flows into the evaporator 9, the inflow portion 29 becomes the main source of the refrigerant passing sound. In such a configuration, the air conditioning control device 4 adjusts the opening degree of the cold air bypass door 22 until the release condition is satisfied. Thus, until the release condition is satisfied, the cool air bypass door 22 prevents the refrigerant transmission sound generated from the inflow portion 29 from being transmitted to the face opening portion 19.

  Further, the air conditioning control device 4 adjusts the opening degree of the cold air side air mix door 21 according to the air conditioning requirement in the passenger compartment, regardless of whether or not the release condition is satisfied. Cold air is applied from the face opening 19 to the occupant's head and chest through the mix door 21. Therefore, until the release condition is satisfied, the amount of cold air is limited by the opening degree of the cold air bypass door 22, but cold air is sent to the face opening 19 via the cold air side air mix door 21. As a result, the refrigerant passing sound is prevented from being transmitted by the cold air bypass door 22 until the release condition is satisfied from the time of startup even at the time of maximum cooling, and the cold air is sent by the cold air side air mix door 21, so The refrigerant passing sound that is transmitted can be prevented, and cool air can be given to the passenger's head and chest. Therefore, it is possible to provide a comfortable environment for the passenger.

  Further, the present embodiment can be realized by simply controlling the opening degree of the cold air bypass door 22 without changing the mechanical configuration of the existing vehicle air conditioner 1. Therefore, the vehicle air conditioner 1 of the present embodiment can be easily realized simply by changing the program stored in the air conditioning control device 4.

  In the present embodiment, the cold air bypass door 22 is provided on the upper Y1 side of the cold air side air mix door 21. Since the inflow portion 29 is provided on the upper Y1 side of the evaporator 9 like the cold air side air mix door 21, it is possible to reliably prevent the refrigerant passing sound generated by the inflow portion 29 from being transmitted to the face opening portion 19. Moreover, since a refrigerant | coolant flows in into the evaporator 9 from the inflow part 29, the upper Y1 side of the evaporator 9 can cool more than the lower Y2 side passes. Therefore, since the cold air bypass door 22 faces the end 9 a on the upper Y1 side of the evaporator 9, the most cooled air can be sent to the face opening 19.

  The warm air side air mix door 20 is provided to face the end portion 9 c of the lower portion Y <b> 2 of the evaporator 9. As described above, the air is not cooled on the lower Y2 side of the evaporator 9 than on the upper Y1 side. As a result, the high-temperature air that has passed through the warm air side air mix door 20 can be efficiently heated by the heater core 16.

  In the present embodiment, the cold air bypass passage 18 has a smaller maximum amount of air that can pass through the cold air passage 17. Thus, even if the opening degree of the cold air bypass door 22 is adjusted to be closed, the cold air can be sent from the face opening 19 by adjusting the opening degree of the cold air side air mix door 21. Therefore, it is possible to prevent the passenger from feeling uncomfortable with a decrease in the air volume until the release condition is satisfied.

In particular, the condition that the refrigerant passing sound is anxious is that the blower speed at which the ventilation sound of the vehicle air conditioner 1 itself is low is low, and in this state, the operation is performed with a low overall ventilation resistance. The reduction in the amount of air flow by closing the cold air bypass door 22 is only 10 m ³ / h when the blower speed is 240 m ³ / h, and this reduction is negligible.

  Moreover, in this Embodiment, since the cold wind bypass door 22 is comprised with a butterfly door, since the distance from the rotating shaft 22b to an edge part is small, it can adjust an opening degree with a small driving force.

  In the present embodiment, the release condition is when a predetermined time has elapsed since the start of the blower 15, so that the opening degree of the cold air bypass door 22 can be fully opened when the refrigerant passing sound is reduced. . Thereby, the opening degree of the cold wind bypass door 22 can be adjusted only during the time when the refrigerant passing sound is loud.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 5 is a simplified cross-sectional view of the vehicle air conditioner 1A that does not satisfy the release condition during maximum cooling. In FIG. 5, the thickness dimension of the air conditioning case 10 is omitted for easy understanding as in FIG. 1.

  In the present embodiment, the configuration of the cold air bypass door 22 is different from the above-described embodiment. The cold air bypass door 22 includes a door body 22c formed in a plate shape, and is configured as a cantilever door provided with a rotating shaft 22d at one end in the door width direction of the door body 22c. The rotating shaft 22d is provided on the upper Y1 side of the cold air bypass passage 18. The remaining configuration of the cold air bypass door 22 is the same as the configuration of the cold air bypass door 22 of the above-described embodiment.

  As shown in FIG. 5, when the release condition is not satisfied, that is, when there is a possibility that the refrigerant passing sound is more than a predetermined value, in the face mode at the maximum cooling, the cold air bypass door 22 is closed, The cold air side air mix door 21 is set to an opening at which the cold air is most guided to the face opening 19, and the hot air side air mix door 20 is closed. As a result, the refrigerant passing sound (indicated by the phantom line in FIG. 5) generated at the inflow portion 29 of the evaporator 9 is blocked by the cold air bypass door 22 and the waveform toward the face opening 19 is reduced.

  Thus, in this Embodiment, since the cold wind bypass door 22 is comprised by the cantilever door, the opening degree of the cold wind bypass door 22 can be adjusted more accurately. In other words, as compared with the case of the butterfly door, the cantilever door can adjust a large amount of air passing with less opening adjustment.

  The rotating shaft 22d of the cold air bypass door 22 is provided on the upper Y1 side of the cold air bypass passage 18, and the cold air bypass passage 18 is formed close to the inner wall of the upper Y1 of the air conditioning case 10. As a result, the cold air bypass door 22 is fully opened, so that the cold air side air mix door 21 can be disposed along the air conditioning case 10. Therefore, even when the cold air bypass door 22 is fully opened, the cold air bypass door 22 is not disposed in the cold air bypass passage 18, so that the cold air can be efficiently guided to the face opening 19.

  Further, since the rotating shaft 22d of the cold air bypass door 22 is provided on the upper Y1 side of the cold air bypass passage 18, the cold air having passed through the cold air bypass door 22 is cooled by the cold air passage 17 provided in the lower Y2 of the cold air bypass door 22. Can lead to. Thus, the cool air can be efficiently sent to the face opening 19 along with the cool air that has passed through the cool air passage 17 having a large amount of passage.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 6 is a simplified cross-sectional view of the vehicle air conditioner 1B that does not satisfy the release condition during maximum cooling. In FIG. 6, the thickness dimension of the air conditioning case 10 is omitted for easy understanding as in FIG. 1.

  The present embodiment is characterized in that the opening degree is set in advance without closing the cold air bypass door 22 until the release condition is satisfied. The predetermined opening degree of the cold air bypass door 22 is set to a sound insulation opening degree that can achieve the effect of insulating the refrigerant passing sound. The sound insulation opening degree of the cold air bypass door 22 is a source of the positional relationship between the cold air bypass door 22 and the face opening 19, the shape of the duct connected to the face opening 19, and the refrigerant passing sound of the evaporator 9, for example. Set based on position. In the present embodiment, the sound insulation opening is, for example, 45 degrees or less with respect to the fully closed position.

  By setting the sound insulation opening degree of the cold air bypass door 22 in this way, as shown in FIG. 6, when the release condition is not satisfied, the cold air bypass door 22 is set as the sound insulation opening degree in the face mode at the maximum cooling. The cold air side air mix door 21 is set to an opening degree at which the cold air is most guided to the face opening 19, and the hot air side air mix door 20 is closed. As a result, the refrigerant passing sound (indicated by the phantom line in FIG. 6) generated on the upper Y1 side to which the expansion valve 8 of the evaporator 9 is connected is efficiently blocked by the cold air bypass door 22 and is a waveform toward the face opening 19. Has been reduced.

  As described above, in this embodiment, by setting the opening degree of the cold air bypass door 22 to the sound insulation opening degree until the release condition is satisfied, the refrigerant passing sound is reduced, and the cold air is reduced to the cold air bypass door 22 and the cold air side air mix. It can be sent to the face opening 19 via the door 21. Therefore, the occupant can obtain a refreshing feeling by the cold air without obtaining an unpleasant feeling by the refrigerant passing sound.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 7 is a cross-sectional view schematically showing the vehicle air conditioner 1C that does not satisfy the release condition during maximum cooling. In FIG. 7, the thickness dimension of the air conditioning case 10 is omitted for easy understanding as in FIG. 1.

  The present embodiment is characterized in that the cold air bypass door 22 is closed until the release condition is satisfied, and the cold air side air mix door 21 is set to a predetermined opening degree. The predetermined opening degree of the cold air side air mix door 21 is set to a sound insulation opening degree that can achieve the effect of insulating the refrigerant passing sound and can send the cold air to the face opening 19. Accordingly, the sound insulation opening degree of the cold air side air mix door 21 is smaller than the opening degree at the time of maximum cooling indicated by the wavy line in FIG. Is set. The sound insulation opening degree of the cold air side air mix door 21 is, for example, the positional relationship between the cold air side air mix door 21 and the face opening 19, the shape of the duct connected to the face opening 19, and the refrigerant of the evaporator 9. It is set based on the position that is the source of the passing sound.

  By setting the sound insulation opening of the cold air side air mix door 21 in this way, as shown in FIG. 7, when the release condition is not satisfied, the cold air bypass door 22 is closed in the face mode at the maximum cooling, The cold air side air mix door 21 is set to a sound insulation opening, and the hot air side air mix door 20 is closed. As a result, the refrigerant passing sound (indicated by phantom lines in FIG. 7) generated on the upper Y1 side to which the expansion valve 8 of the evaporator 9 is connected is efficiently blocked by the cold air bypass door 22 and the cold air side air mix door 21, The waveform toward the face opening 19 is reduced.

  As described above, in the present embodiment, the cold air bypass door 22 is closed until the release condition is satisfied, and the opening degree of the cold air side air mix door 21 is set to the sound insulation opening degree, thereby reducing the refrigerant passing sound and reducing the cold air side. Cold air can be sent to the face opening 19 via the air mix door 21. Therefore, the occupant can obtain a refreshing feeling by the cold air without obtaining an unpleasant feeling by the refrigerant passing sound.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a simplified cross-sectional view of the vehicle air conditioner 1D that does not satisfy the release condition during maximum cooling. In FIG. 8, the thickness dimension of the air conditioning case 10 is omitted for easy understanding as in FIG. 1.

  In the present embodiment, the cold air bypass door 22 is closed until the release condition is satisfied, and an air outlet door 26 (hereinafter sometimes referred to as “face air outlet door”) provided in the face opening 19 is opened in advance. It is characterized in that it is set in degrees. The predetermined opening of the face outlet 26 is set to a sound insulating opening that can achieve the effect of insulating the refrigerant passing sound and that allows the cool air to pass through the face opening 19. Therefore, the sound insulation opening of the face outlet 26 is smaller than the opening at the time of maximum cooling indicated by the wavy line in FIG. 8, so that the opening for improving the sound insulation effect, that is, the opening area through which the refrigerant passing sound passes is smaller. Is set. The sound insulation opening degree of the face outlet 26 is, for example, the positional relationship between the cold air side air mix door 21 and the face opening 19, the shape of the duct connected to the face opening 19, and the refrigerant of the evaporator 9. It is set based on the position that is the source of the passing sound.

  By setting the sound insulation opening of the face outlet 26 in this manner, as shown in FIG. 8, when the release condition is not satisfied, the cold air bypass door 22 is closed in the face mode at the maximum cooling, The cold air side air mix door 21 is set to an opening degree at which the cold air is most guided to the face opening 19, the hot air side air mix door 20 is closed, and the face air outlet door 26 is set to a sound insulation opening degree. As a result, the refrigerant passing sound (indicated by phantom lines in FIG. 8) generated on the upper Y1 side to which the expansion valve 8 of the evaporator 9 is connected is efficiently blocked by the cold air bypass door 22 and the face outlet door 26, The waveform toward the face opening 19 is reduced.

  As described above, in the present embodiment, the cool air bypass door 22 is closed until the release condition is satisfied, and the opening of the face outlet 26 is set to the sound insulation opening, thereby reducing the refrigerant passing sound and reducing the cold wind. The air can be sent to the face opening 19 via the cold air side air mix door 21 and the face outlet door 26. Therefore, the occupant can obtain a refreshing feeling by the cold air without obtaining an unpleasant feeling by the refrigerant passing sound.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In each of the above-described embodiments, the release condition is the time from the start-up, but is not limited to such a condition, and may be any release condition such that the refrigerant passing sound is equal to or lower than a predetermined volume. The release condition may be, for example, when the rotational speed of the blower 15 is equal to or higher than a predetermined rotational speed. The predetermined rotation speed is set according to the correlation between the generation state of the refrigerant passing sound and the rotation speed. Thereby, the opening degree of the cold air bypass door 22 can be fully opened when the refrigerant passing sound is reduced. Therefore, the opening degree of the cold air bypass door 22 can be adjusted only during the time when the refrigerant passing sound is loud.

  The release condition may be set when the temperature detected by temperature detecting means such as a post-evaporator temperature sensor becomes equal to or lower than a predetermined temperature. The predetermined temperature is set based on the correlation between the generation state of the refrigerant passing sound and the temperature. Thereby, when the refrigerant passing sound is reduced, the opening degree of the cold air bypass door 22 can be fully opened. Therefore, the opening degree of the cold air bypass door 22 can be adjusted only during the time when the refrigerant passing sound is loud.

  Further, the release condition may be a combination of the plurality of release conditions described above. When combining a plurality of release conditions, it may be controlled that the release conditions are satisfied if all the release conditions are satisfied, or may be controlled so that the release conditions are satisfied if a predetermined number of release conditions are satisfied. .

  In each of the above-described embodiments, the cold air bypass door 22 is configured by a single unit, but is not limited to a single unit and may be a plurality. When there are a plurality of cold air bypass doors 22, the opening of each cold air bypass door 22 is individually controlled so that the refrigerant passing sound is reduced and the amount of cold air sent to the face opening 19 can be secured. The

It is sectional drawing which simplifies and shows the vehicle air conditioner 1 of 1st Embodiment of this invention. 4 is a flowchart showing an air conditioning control process of the air conditioning control device 4. It is sectional drawing which simplifies and shows the vehicle air conditioner 1 of the state which does not satisfy cancellation | release conditions at the time of maximum cooling. It is a graph which shows an example of the measurement result of refrigerant passing sound. It is sectional drawing which simplifies and shows 1A of vehicle air conditioners of the state which does not satisfy cancellation | release conditions at the time of the maximum cooling of 2nd Embodiment of this invention. It is sectional drawing which simplifies and shows the vehicle air conditioner 1B of the state which does not satisfy the cancellation | release conditions at the time of the maximum cooling of 3rd Embodiment of this invention. It is sectional drawing which simplifies and shows 1 C of vehicle air conditioners of the state which does not satisfy the cancellation | release conditions at the time of the maximum cooling of 4th Embodiment of this invention. It is sectional drawing which simplifies and shows the vehicle air conditioner 1D of the state which is not satisfy | filling cancellation | release conditions at the time of the maximum cooling of 5th Embodiment of this invention.

Explanation of symbols

1, 1A, 1B, 1C, 1D ... Vehicle air conditioner 4 ... Air conditioner control device (control means)
9 ... Evaporator (cooling heat exchanger)
DESCRIPTION OF SYMBOLS 9a ... Upper end part of evaporator 9b ... Middle part of up-down direction of evaporator 9c ... Lower end part of evaporator 10 ... Air-conditioning case 15 ... Blower (blower)
16 ... Heater core (heat exchanger for heating)
17 ... Cool air passage 18 ... Cool air bypass passage 19 ... Face opening 20 ... Warm air side air mix door 21 ... Cool air side air mix door 22 ... Cool air bypass door 22a, 22c ... Door body 22b, 22d ... Rotating shaft 23 ... Mixing chamber 25 ... Foot opening 29 ... Inflow part

Claims (9)

An air conditioning case (10) forming an air passage;
A blower (15) for blowing air into the air conditioning case;
A cooling heat exchanger (9) provided in the air conditioning case, having an inflow portion (29) to which a refrigerant is supplied, and cooling air blown by the blower;
A heating heat exchanger (16) provided in the air conditioning case for heating the cold air from the cooling heat exchanger;
A cold air passage (17) provided in the air conditioning case and through which the cold air that has not passed through the heating heat exchanger flows;
A hot air side air mix door (20) which is provided in the air conditioning case and adjusts the amount of air passing through the heating heat exchanger;
A cold air side air mix door (21) provided in the air conditioning case for adjusting the amount of air passing through the cold air passage;
A mixing chamber (23) provided in the air conditioning case, in which hot air from the heat exchanger for heating and cold air from the cold air passage are mixed;
A face opening (19) for guiding the conditioned air that has passed through the mixing chamber to an occupant head chest in the passenger compartment;
A foot opening (25) for guiding the conditioned air that has passed through the mixing chamber to the feet of passengers in the passenger compartment;
A door (26) for adjusting the amount of air blown from the face opening;
A door (28) for adjusting the amount of air blown from the foot opening;
A passage that is provided in the air conditioning case and is provided in parallel with the cold air passage and allows cold air that has not passed through the heating heat exchanger to pass toward the face opening, the face opening And a cold air bypass passage (18) provided on a path connecting the inflow portion of the cooling heat exchanger,
A cold air bypass door (22) that is provided in the air conditioning case and adjusts the amount of air passing through the cold air bypass passage;
Depending on the air conditioning requirements in the passenger compartment, the air volume of the blower and the opening of the face opening door, the foot opening door, the hot air side air mix door, the cold air side air mix door, and the cold air bypass door are opened. Control means (4) for adjusting the degree individually,
The control means includes
In response to the air conditioning request, at least in the blowing mode in which the face opening is in an open state, the blowing mode is maintained and until a predetermined release condition is satisfied from the start of the vehicle air conditioner (1) Adjusting the opening of the cold air bypass door to an opening that prevents the refrigerant passing sound generated from the inflow portion of the cooling heat exchanger from being transmitted to the face opening,
When the release condition is satisfied, the opening adjustment of the cold air bypass door is released, and the opening adjustment according to the air conditioning request in the vehicle interior is executed.   The vehicle air conditioner according to claim 1, wherein the release condition is when a predetermined time has elapsed since the vehicle air conditioner was activated.   The vehicle air conditioner according to claim 1, wherein the release condition is when the rotational speed of the blower is equal to or higher than a predetermined rotational speed. Temperature detection means for detecting the temperature of the air cooled by the cooling heat exchanger,
2. The vehicle air conditioner according to claim 1, wherein the release condition is when the temperature detected by the temperature detecting means is equal to or lower than a predetermined temperature.   The said control means adjusts the opening degree of the said cold wind bypass door to the opening degree which closes the said cold wind bypass channel until the said cancellation | release conditions are satisfied, The any one of Claims 1-4 characterized by the above-mentioned. Vehicle air conditioner. The cooling heat exchanger has an inflow portion at an upper end (9a) in the vertical direction (Y1, Y2) (Y1),
The cold air bypass door is provided to face the upper end of the cooling heat exchanger,
The cold air side air mix door is provided to face the intermediate portion (9b) in the vertical direction of the cooling heat exchanger,
The said warm air side air mix door is provided facing the edge part (9c) below the said up-down direction (Y2) of the said heat exchanger for cooling, The any one of Claims 1-5 characterized by the above-mentioned. The vehicle air conditioner described in 1.   The vehicular air conditioner according to any one of claims 1 to 6, wherein the cold air bypass passage has a maximum amount of air that can pass through the cold air passage. The cold air bypass door includes a door body (22a) formed in a plate shape,
The vehicle according to any one of claims 1 to 7, wherein the cold air bypass door is configured by a butterfly door provided with a rotation shaft (22b) at an intermediate portion in the door width direction of the door main body. Air conditioner. The cold air bypass door includes a door body (22c) formed in a plate shape,
The said cold wind bypass door is comprised by the cantilever door by which a rotating shaft (22d) is provided in the one end part of the door width direction of the said door main body, The Claim 1 characterized by the above-mentioned. Vehicle air conditioner.

Images