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US20050116054A1 - Automotive HVAC device - Google Patents

Automotive HVAC device Download PDF

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Publication number
US20050116054A1
US20050116054A1 US10/987,064 US98706404A US2005116054A1 US 20050116054 A1 US20050116054 A1 US 20050116054A1 US 98706404 A US98706404 A US 98706404A US 2005116054 A1 US2005116054 A1 US 2005116054A1
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United States
Prior art keywords
flap
temperature
opening
air
casing
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
Application number
US10/987,064
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English (en)
Inventor
Gerald Richter
Thomas Klotten
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Visteon Global Technologies Inc
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Visteon Global Technologies Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Visteon Global Technologies Inc filed Critical Visteon Global Technologies Inc
Publication of US20050116054A1 publication Critical patent/US20050116054A1/en
Assigned to VISTEON GLOBAL TECHNOLOGIES, INC. reassignment VISTEON GLOBAL TECHNOLOGIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RICHTER, GERALD, KLOTTEN, THOMAS
Assigned to JPMORGAN CHASE BANK, N.A., AS ADMINISTRATIVE AGENT reassignment JPMORGAN CHASE BANK, N.A., AS ADMINISTRATIVE AGENT SECURITY AGREEMENT Assignors: VISTEON GLOBAL TECHNOLOGIES, INC.
Assigned to JPMORGAN CHASE BANK reassignment JPMORGAN CHASE BANK SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VISTEON GLOBAL TECHNOLOGIES, INC.
Assigned to WILMINGTON TRUST FSB, AS ADMINISTRATIVE AGENT reassignment WILMINGTON TRUST FSB, AS ADMINISTRATIVE AGENT ASSIGNMENT OF SECURITY INTEREST IN PATENTS Assignors: JPMORGAN CHASE BANK, N.A., AS ADMINISTRATIVE AGENT
Assigned to VISTEON GLOBAL TECHNOLOGIES, INC. reassignment VISTEON GLOBAL TECHNOLOGIES, INC. RELEASE BY SECURED PARTY AGAINST SECURITY INTEREST IN PATENTS RECORDED AT REEL 022575 FRAME 0186 Assignors: WILMINGTON TRUST FSB, AS ADMINISTRATIVE AGENT
Abandoned legal-status Critical Current

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Classifications

    • 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
    • B60H1/00671—Damper doors moved by rotation; Grilles
    • B60H1/00678—Damper doors moved by rotation; Grilles the axis of rotation being in the door plane, e.g. butterfly doors
    • 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
    • B60H1/00671—Damper doors moved by rotation; Grilles
    • 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
    • B60H2001/00721—Air deflecting or air directing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F24F13/10—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers
    • F24F13/14—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre
    • F24F13/1426—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre characterised by actuating means
    • F24F2013/1473—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers built up of tilting members, e.g. louvre characterised by actuating means with cams or levers

Definitions

  • the invention relates to a heating, ventilating and air conditioning device for vehicles. More specifically, the invention relates to such a device having a temperature flap that reduces the variance of the mixed air in the outlet channel from an associated temperature/rotational position of the flap curve.
  • a traditional device for heating, ventilating and air conditioning includes a fan, which produces an inlet air stream flowing into the casing of the device through a heat exchanger assembly (in form of an evaporator) located in the associated inlet casing. Downstream of the evaporator there is an air temperature control valve in the form of a temperature flap, which is rotatably supported at an inlet opening into an inlet channel of the device casing. At the inlet opening, the inlet channel divides into a through channel—the cold air channel—for the undisturbed air flow and an air heating channel—the hot air channel—, which passes another heat exchanger assembly, in the form of a heater core, where the air stream is heated.
  • a fan which produces an inlet air stream flowing into the casing of the device through a heat exchanger assembly (in form of an evaporator) located in the associated inlet casing. Downstream of the evaporator there is an air temperature control valve in the form of a temperature flap, which is rotatably supported at an inlet opening into
  • the through channel and the air heating channel subsequently join to form an outlet channel, which finally leads into the passenger compartment.
  • the temperature of the air stream in the outlet channel can be adjusted between “cold” to “hot” in the passenger compartment by a control unit, which is connected to an actuation mechanism for rotating the temperature flap.
  • the output temperature of the air stream into the passenger compartment is also controlled by means of a temperature flap.
  • the temperature flap is rotatably supported in the device casing.
  • an evaporator and an air heating heat exchanger are provided, whereby the inflowing air is cooled by the evaporator and the flowing air can be optionally heated by the heat exchanger.
  • the heat exchanger can be provided with a baffle to establish a heating chamber that can be closed by means of the temperature flap.
  • the temperature flap can divide the air flowing in from the evaporator into two streams.
  • a first inflowing air stream can flow almost undisturbedly through the cold air channel and then to the outlet channel.
  • the second air stream passing the heat exchanger, can flow through the hot air channel. Both air streams are directed to the outlet channel where mixing occurs.
  • a mixing temperature of the outlet air results.
  • the hot air channel is closed (0% of the rotational position) by the temperature flap, only cooled air or fresh air (ventilating) enters through the cold air channel into the outlet channel.
  • the temperature of the undisturbed air stream represents the 0%-temperature point “cold” of the air.
  • the temperature flap can be connected to an actuation assembly that adjusts the rotational positions of the temperature flap through control commands of an actuatable control device.
  • the problem of the known devices is that for heating, ventilating and air conditioning the control curve is a relatively deep temperature dip, particularly in the regions between 10%- and 50%-rotational positions, due to the pressure drop different between the cold air channel and the hot air channel. On the part of the hot air channel the portion of the hot air stream is not sufficient to raise the output temperature in the outlet channel in the mentioned region of the rotational positions.
  • baffles are provided in the device casing to reduce the pressure drop on the part of the cold air channel.
  • baffles produce an additional disturbing effect of reducing the air flow in the HVAC device and also disturbingly raise the noise level, which is particularly due to the impact of the air flow onto the baffles.
  • U.S. Pat. No. 4,452,301 Another device for heating, ventilating and air conditioning, inclusive of controlling the output temperature for conditioning the air in the passenger compartment of vehicles, is described in U.S. Pat. No. 4,452,301.
  • a manually actuatable temperature flap is provided which is movable in both the air conditioning and heating modes to regulate the air flow rate through a heating heat exchanger and to control the temperature of the air delivered by the device into the passenger compartment.
  • An air temperature control unit is provided that includes an air guide flap that is arranged on the face side transverse to the temperature flap and can be moved with it and is itself rotatable relative to the temperature flap so that the air flow rate, particularly through the heating heat exchanger, can be adjusted for various positions.
  • the air guide flap is connected to a guide element and is rotatable in a guide way made in the casing.
  • the rotation point is a notch which in the end allows to tilt the air guide flap onto the temperature flap when the hot air channel is closed.
  • the cam-track controlled air guide flap when the hot air channel is opened, has to throttle the air stream on the part of the cold air channel and thereby to raise the portion of the hot air stream in the outflowing mixed air stream, simultaneously reducing the portion of the undisturbed cold air stream.
  • a double cam control curve which performs the air guide flap control, causes the air guide flap to carry out motions assigned to the position of the temperature flap.
  • a predetermined cam control curve is used, which is defined either for the air conditioning mode or the heating mode, so that heat transfers are achieved that are intended to produce a linear relationship between the air temperature measured in the outlet channel and the temperature flap position in both the air conditioning and the heating modes.
  • a problem is that in the low rotational positions, particularly between the 0%-(ventilating) and 30%-(air conditioning) positions of the temperature flap, there is a deep temperature dip in the associated control curve. Additionally, the load of the notch in the air guide flap can be sufficiently high to create a danger or fracture after an extended time of operation. On the whole, the device has a complicated structure susceptible to failures due to the use of a relatively great number of parts.
  • U.S. Pat. No. 2,933,100 which is intended to produce a largely constant airflow in the outlet region of the channel.
  • An associated control unit includes two neighboring perforated plates which largely extend over a transverse section of the channel. Both perforated plates have openings of approximately the same width. One of the plates can be transversely moved over the surface of the other plate, which is rigidly attached to the channel. Under normal conditions, the openings of both plates are coincident and allow the inflowing air stream to pass.
  • the residual portion of the channel section and the control unit is a rigidly attached sensor arrangement, which is an air flow pressure sensor.
  • the sensor arrangement is connected to a spring-supported elbow lever for the actuation of the movable perforated plate in such a way that at a too high pressure in the sensor arrangement the movable perforated plate in such a way that at a too high pressure in the sensor arrangement the movable perforated plate is moved by means of the sensor arrangement.
  • the resulting openings are reduced due to shifting of the opening in both perforated plates relative to each other. This makes possible to reduce the air flow pressure.
  • a problem with this construction is the sensor arrangement allows control of the pressure conditions for an optimal air supply with a largely constant outlet air flow in only one channel which, however, is not sufficient to eliminate the temperature dip of the control curve in the lower temperature regions and flap positions.
  • a flow distributing device is known from U.S. Pat. No. 3,735,809 that includes a channel with a cam, a heat exchanging casing (which is spatially attached to the channel within the cam such that a free air flow connection path is created) a slide plate rotatably supported at the casing, a first plate with a plurality of first holes attached to channel, a second plate with plurality of second holes, a device to connect the second plate to slide plate, and an apparatus connected to the slide plate functioning to hold the slide plate in a first or second position and to move the slide plate therebetween.
  • the slide plate closes the free air flow connection path, when the slide plate is in a first position.
  • the air powerfully flows through the casing with the slide plate covering a portion of the casing.
  • the air flow is passed through that free air flow connection path and an uppermost surface of the first plate touches the bottom surface of the slide plate.
  • a problem is that the air stream is passed through the heat exchanger assembly by means of a rotatably supported plate or by means of a single plate to which a perforated plate is rotatably attached or is guided through a perforated plate or by means of a perforated plate.
  • an air stream regulating valve for an HVAC device is described.
  • the valve is provided in an air distribution apparatus and has a first open position, a closed position and a second open position, and includes means to maintain a relatively constant volume of the air flow for air inlet pressure changes.
  • the valve can be cylindrical or flat and supports the temperature control of the mixing chamber.
  • the airflow is controlled within the HVAC channel by a reciprocating or rotating perforated cylinder or by two flat slide plates, including a reciprocating plate and a fixed plate.
  • a vertical movement of the plates, which creates alignment of the openings in all plates, is produced by an actuatable bolt, which is moved through holes in the fixed plate and vertical slots in the movable plate.
  • the invention is aimed at a device for heating, ventilating and air conditioning in a vehicle that is configured in such a way that the design structure of the temperature flap is improved and thereby the temperature dip of the outlet air in the outlet channel in relation to the associated temperature/rotational position is significantly reduced.
  • the temperature flap is established as temperature valve flap that includes a rotational plate with at least one flap opening and at least one closing element assigned to the flap opening.
  • an opening mechanism actuates the dosing element and releases the flap opening depending on the rotational position of the temperature valve flap.
  • the opening mechanism can be established considering the casing.
  • the temperature valve flap is provided with at least one flap opening that is variable in cross-section and closable.
  • the effective cross-sectional area of the hot air channel can be varied continuously, as well as diaphragm-like.
  • the opening mechanism can be designed such that, depending on the respective position of the temperature valve flap, it displaces the dosing element and, depending on the direction of displacement, opens or closes the flap opening. In this manner, the temperature of the air stream in the outlet channel, depending on the rotational positions, largely follows an approximately linear temperature/rotational position curve C.
  • the rotating plate of the temperature valve flap can preferably have a rectangular base plate, in which there is a preferably rectangular flap opening.
  • each of the opposing side edge regions of the base plate there can be preferably parabola-like holding element, whereby both holding elements equally directed and equally shaped and offset from the edge by a given distance a, are attached in the side edge regions at a right angle to the base plate.
  • the holding elements may preferably be in connection to only a portion of the base plate, whereas the residual portion is provided with the flap opening arranged in the base plate preferably parallel to the rotational axis in transverse direction and vertical to the holding elements offset inwards.
  • the closing element can belong, which in the 0%-rotational position (“hot”) of the temperature valve flap closes the flap opening.
  • the dosing element is provided with a covering plate that corresponds in its area at least to the passage cross-sectional area of the flap opening and completely seals the flap opening. Face-sidedly on either narrow side of the covering plate there is a side strip that is provided with a spring arc ending in a band matched with the plane of the covering plate attached to the side edge regions at the distance a.
  • the rotational plate, the flap opening and also the covering plate can be designed different from a rectangular shape. Non-rectangular flap opening passage sections enable to reach a “softer” opening process of the flap opening so that a given opening characteristics can be realized.
  • the opening mechanism can be provided with two projections, particularly designed as cams, essentially functioning as opening elements, which are attached to the casing at the level of the spring arcs, whereby for a sliding movement of the covering plate of the dosing element on the base plate a pressure support exerted by the cams onto the edge-side spring arcs is sufficient.
  • the cams are preferably designed flat and have a thickness smaller than the distance a of the holding elements offset inwards in the side edge regions of the base plate.
  • the contour of the cams is designed such that it predetermines at which time how fast the covering plate is slideable in direction away from the flap opening, in order to obtain a controlledly branching off hot air partial stream from the hot air channel directed at least into the end region of the cold air channel.
  • the cams are shaped such that on rotations of the temperature valve flap, in connection with the force action onto the spring arcs, the temperature dip is reduceable according to the temperature/rotational position curve C and that in the region of the 10%-to 50%-rotational positions of the temperature valve flap the effective passage cross-sectional area of the flap opening can act sufficiently.
  • the cams can, for example, be similar to a bell-like shape in a longitudinal section adapted to the range of rotation and attached to the casing, whereby the bell edges contacting the spring arcs are the pressure actuators for the spring arcs.
  • Linking, or the attachment, respectively, of the cams within the casing is also predetermined depending on the location and design of the spring arcs.
  • the opening mechanism can also have other mechanical opening elements or else electrical and/or magnetic opening elements, which are established as opening elements corresponding with the closing element(s) and can be connected to them.
  • variable flap opening makes it possible that before the hot air stream and the cold air stream are brought together in the outlet channel, optionally, at least one hot air partial stream related to the flap opening passage cross-sectional area branches off from the original hot air stream and is entered into the cold air stream.
  • the branching off hot air stream pretempers the cold air stream so that the temperature of the outlet air stream in the outlet channel is adapted to a largely linear temperature/rotational position curve (C) by valve control.
  • FIG. 1 is a schematic representation of a device for heating, ventilating and air conditioning in vehicles according to the state-of-the-art and showing both end positions of the temperature flap;
  • FIG. 2 is a schematic representation of a device in a 25%-rotational position of the temperature flap seen in FIG. 1 ;
  • FIG. 3 is a schematic representation of a device embodying the principles of the invention for heating, ventilating and air conditioning in vehicles with a temperature valve flap in a 25%-rotational position and with a partially open flap opening;
  • FIG. 4 is a schematic representation of the device seen in FIG. 3 with a temperature valve flap in a 50%-rotational position with an open flap opening;
  • FIG. 5 is a schematic representation of the device seen in FIG. 3 with the temperature valve flap in a 75%-rotational position and with a closed flap opening;
  • FIG. 6 a is a perspective view of the temperature valve flap with a spring-assisted dosing element for the flap opening and being in a dosed condition;
  • FIG. 6 c is a perspective view of the dosing element seen in FIG. 6 a;
  • FIG. 7 is a perspective view of the temperature valve flap in a 0%-rotational position and showing the opening mechanism for the flap opening without cam contact;
  • FIG. 8 is a perspective of the temperature valve flap in an approximately 50%-rotational position and showing the opening mechanism with cam contact;
  • FIG. 9 is a graph of an ideal linear temperature/rotational position curve (control curve) A, a control curve B of the state-of-the-art and an improved control curve C according the temperature valve flap of the present invention.
  • a device 100 for heating, ventilating and air conditioning (HVAC device) in vehicles is shown in FIGS. 1 and 2 and includes, according to the state-of-the-art, a casing 102 with at least one fan 103 , two heat exchanger assemblies (an evaporator assembly 104 , a heating core assembly 105 ).
  • An air entry channel 106 is divided into a cold air channel 107 and a hot air channel 108 , which are subsequently brought together leading into an outlet channel 109 .
  • a temperature flap 140 which in the region of the hot air channel 108 and the cold air channel 107 is rotatably arranged between the end positions 111 , 112 to close the hot air channel 108 or the cold air channel 107 and provide for the temperature-dependent air flow distribution in the outlet channel 109 .
  • FIG. 1 especially shows the extreme end position 111 , 112 of the known temperature flap 140 .
  • FIG. 2 shows the temperature flap 140 in the 25%-rotational position, designated at 135 .
  • the temperature flap 10 shown in FIGS. 7, 8 , includes a rotational plate 39 with at least one flap opening 13 defined therein and at least one dosing element 16 assigned to the flap opening 13 .
  • a casing-connected opening mechanism 14 In the region of the closing element 16 , there is a casing-connected opening mechanism 14 .
  • the opening mechanism 14 actuates the closing element 16 so that, optionally, a partial hot air stream 42 branching off from the remaining hot air stream 43 can flow through the passage cross-sectional area of the flap opening 13 , at least into the end region of the cold air channel 7 and subsequently into the outlet channel 9 .
  • the temperature valve flap 10 is provided, by analogy with FIG. 1 , with a flap opening 13 that is dosed at least in the end positions 11 , 12 .
  • the opening mechanism 14 is designed such that, depending on the actual rotational position of the temperature valve flap 10 , it opens and closes the flap opening 13 .
  • the temperature of the air stream in the outlet channel 9 depends on the rotational positions 11 , 35 , 36 , 37 , 12 and largely follows an approximately linear temperature/rotational position curve C, as shown in FIG. 9 .
  • the temperature valve flap 10 includes, as shown in FIG. 6 a , essentially the rotational plate 39 provided with a flap opening 13 and the associated closing element 16 .
  • the rotational plate 39 of the temperature valve flap 10 as shown in FIG. 6 b , of a preferably rectangular base plate 15 , that defines therein a preferably rectangular flap opening 13 .
  • Each of the opposing side edge regions 19 , 20 of the base plate 15 there is a parabola-like or otherwise shaped holding element 17 , 18 .
  • Both holding elements 17 , 18 are equally offset from the edge of the base plate 15 by a given distance a and are attached to the side edge regions 19 , 20 at a right angle to the base plate 15 .
  • In the apex regions 21 , 22 of the holding elements 17 , 18 are pivots 24 , 25 directed outwards on the same rotational axis 23 .
  • the pivots 24 , 25 project from the side edges 19 , 20 and rotationally fit into associated rotation holes (not shown) in the casing 2 .
  • the holding elements 17 , 18 preferably are connected to only a portion of the base plate 15 , while the residual portion is provided with the preferably rectangular flap opening 13 .
  • the flap opening is preferably arranged in the base plate 15 generally parallel to the rotational axis 23 in transverse direction and vertical to the holding elements 17 , 18 offset inwards.
  • alternative designs from that illustrated for the holding elements 17 , 18 and the associated pivots 24 , 25 can be employed.
  • the rotationally supported rotational plate 39 is provided with the closing element 16 in the 0%-rotational position 11 of the temperature valve flap 10 and dosing the flap opening 13 in FIG. 6 a .
  • the dosing element 16 includes a covering plate 26 , which is sized to the passage cross-sectional area of the flap opening 13 so as to completely seal the flap opening 13 in the end rotational positions 11 , 12 .
  • Face-sidedly on either narrow side of the covering plate 26 are side strips 27 and 28 .
  • the side strips are provided with a spring arc 29 , 30 and end in a band 31 , 32 matched with the plane of the covering plate 26 and attached to the side edge regions 19 , 20 of the base plate 15 at the distance a.
  • FIGS. 7 and 8 the design of the opening mechanism 14 is shown.
  • the 0%-rotational position 11 is shown and in FIG. 8 the 50%-rotational position 36 is shown after a rotation 44 from the 0%-rotational position 11 of the temperature valve flap 10 according to the invention.
  • the opening mechanism 14 includes opening elements in the form of two projections, particularly the cams 33 , 34 , which can be attached to the casing 2 generally at the level of the spring arcs 29 , 30 .
  • the cams 33 , 34 are flat and have a thickness smaller than the distance a by which the holding elements 17 , 18 are offset inwards from the side edge regions 19 , 20 of the base plate 15 . To cause the sliding movement of the covering plate 26 of the dosing element 16 on the base plate 15 , the pressure exerted by the cams 33 , 34 onto the edge-side spring arcs 29 , 30 are sufficient.
  • the profile 41 of the cams 33 , 34 depends on the condition at which time how fast the covering plate 26 has to be pushed from the flap opening 13 in order to obtain a hot air partial stream actually branching off from the hot air channel 8 and directed to the cold air channel 7 .
  • the cams 33 , 34 are shaped such that for a rotation of the temperature valve flap 10 in connection with the force action onto the spring arcs 29 , 30 the dip in the temperature/rotational position curve C compared with the control curve B is significantly reduced. It is useful that the peripheral shape of the cams 33 , 34 is such that, preferably in the region of the 10%-to 50%-rotational positions of the temperature valve flap 10 , the effective flap opening 13 is opened so as to be effective. After the 75%-rotational position, the flap opening 13 may already be closed again, following the comparison between the temperature/rotational position curve C and the ideal temperature/rotational position curve A.
  • the cams 33 , 34 can, for example, have a shape similar to a shape bell-like in the longitudinal section turned in view, whereby the contour of the bell edges 41 contacting the spring arcs 29 , 30 is the pressure actuator onto the spring arcs 29 , 30 .
  • the cams 33 , 34 could alternatively have a cylindrical or semi-cylindrical shape.
  • a useful linking, or attachment, respectively, of the cams 33 , 34 within the casing 2 in relation to the location and design of the spring arcs 29 , 30 is provided.
  • FIG. 9 three temperature/rotational position curves (control curves) A, B, C are shown in comparison.
  • One of the representations refers to an ideal linear temperature/rotational position curve (control curve) A, for which the temperature (as percentage) in the outlet channel 9 and the rotational position (as percentage) are proportional to one another.
  • control curve B of the existing state-of-the-art with the traditional temperature flap 140 and the improved control curve C with the temperature valve flap 10 of the invention are also shown therein.
  • the temperature valve flap 10 of the invention is movable between the 0%-cold end position 11 and in the 100%-hot end position 12 , whereby the 0%-rotational position 11 is assigned to the 0%-temperature point and the 100%-rotational position 12 is assigned to the 100%-temperature point on the control curves A, B, C.
  • the flap opening 13 is closed in the end positions 11 , 12 .
  • the 0%-temperature point can correspond, for example, to a real temperature of 10° C. (“cold”), the 100%-temperature point to a real temperature of 50° C. (“hot”).
  • the hot air channel 8 is closed and completely sealed by the temperature valve flap 10 .
  • the spring arcs 29 , 30 approach the cams 33 , 34 , which are fixed to the casing 2 .
  • the spring arcs 29 , 30 are pressed in the direction of the base plate 15 as the rotation continues. With the pressing of the spring arcs 29 , 30 , the covering plate 26 is slidingly pushed from its closing position.
  • the passage cross-sectional area of the flap opening 13 is thus increasingly opened approximately in the region from the 25%-rotational position 35 ( FIG. 3 ) to the 50%-rotational position 36 ( FIG. 4 , FIG. 8 ). With this opening of the flap opening 13 , the effective cross-sectional area of the hot air channel 8 increases gradually. A branching off hot air portion will flow through the flap opening 13 from the hot air passing on the rear side 38 of the temperature valve flap 10 and be added to the flowing cold air of the cold air channel 7 to be mixed with it.
  • the output temperature of the mixed/outlet air entering the passenger compartment therefore, is for lower rotational positions higher compared with the know constructions.
  • the temperature course is raised when compared with the known temperature dip of the control curve B (especially for low rotational positions), and approaches the ideal linear control curve A to a greater extent.
  • the flap opening 13 can be closed in the 75%-rotational position 37 of the temperature valve flap 10 , where it is not necessary to change the control curve C.
  • the control curve C approximately corresponds to the control curve A.
  • the dosing element 16 by modification of the opening mechanism described above, can be actuated by a different opening mechanism, particularly a cam control device or connection device, which optionally can also be a different closing element pushing device.
  • the rotational position-dependent switchable flap opening 13 of the temperature valve flap 10 can also be considered as a small-scale valve automatically controlled internally within a controllable large-scale valve actuatable from the exterior.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Air-Flow Control Members (AREA)
US10/987,064 2003-11-14 2004-11-12 Automotive HVAC device Abandoned US20050116054A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEDE10354539.5-16 2003-11-14
DE10354539A DE10354539B4 (de) 2003-11-14 2003-11-14 Einrichtung zum Heizen, Ventilieren und Klimatisieren in Fahrzeugen

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US20050116054A1 true US20050116054A1 (en) 2005-06-02

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US10/987,064 Abandoned US20050116054A1 (en) 2003-11-14 2004-11-12 Automotive HVAC device

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US (1) US20050116054A1 (fr)
DE (1) DE10354539B4 (fr)
FR (1) FR2862255A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090036048A1 (en) * 2007-07-31 2009-02-05 Behr America, Inc. Air mixing apparatus for hvac system
US20140141706A1 (en) * 2012-03-13 2014-05-22 Visteon Global Technologies, Inc. Air intake with single door and throttling function
JP2015507138A (ja) * 2012-02-14 2015-03-05 ピールブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ Ｐｕｍｐ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ 機械式のクーラントポンプ
US9682608B2 (en) 2013-01-30 2017-06-20 Hanon Systems Supplemental heating and cooling sources for a heating, ventilation and air conditioning system
US9914339B2 (en) 2013-01-30 2018-03-13 Hanon Systems Supplemental thermal storage
US10202019B2 (en) 2013-01-30 2019-02-12 Hanon Systems HVAC blower

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US20090036048A1 (en) * 2007-07-31 2009-02-05 Behr America, Inc. Air mixing apparatus for hvac system
US9145041B2 (en) * 2007-07-31 2015-09-29 Mahle International Gmbh Air mixing apparatus for HVAC system
JP2015507138A (ja) * 2012-02-14 2015-03-05 ピールブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ Ｐｕｍｐ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ 機械式のクーラントポンプ
US20140141706A1 (en) * 2012-03-13 2014-05-22 Visteon Global Technologies, Inc. Air intake with single door and throttling function
US9789745B2 (en) * 2012-03-13 2017-10-17 Hanon Systems Air intake with single door and throttling function
US9682608B2 (en) 2013-01-30 2017-06-20 Hanon Systems Supplemental heating and cooling sources for a heating, ventilation and air conditioning system
US9914339B2 (en) 2013-01-30 2018-03-13 Hanon Systems Supplemental thermal storage
US10202019B2 (en) 2013-01-30 2019-02-12 Hanon Systems HVAC blower

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FR2862255A1 (fr) 2005-05-20
DE10354539A1 (de) 2005-06-23

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