• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a vehicle (1), in particular a racing vehicle, having a drive unit having an internal combustion engine (4) with at least one heat-emitting component or a heat-dissipating module, the component or module being connected to at least one of a working gas, in particular air, flowed through space (6) is bordered, in particular at least partially surrounded by the space flowed through (6), wherein the space (6) has a flow inlet (7) and a flow outlet (8) and the flow outlet (7) in the region of an output-increasing device of the Vehicle (1) is arranged. In order to simplify the road holding of the vehicle (1) in the simplest possible way by utilizing the waste heat of components or assemblies, it is provided that the space (6) flows through at least one flow section between at least one flow inlet (7) and at least one flow outlet (8) having diffuser-like expanding flow cross-section.
    公开号:AT513886A1
    申请号:T50154/2013
    申请日:2013-03-07
    公开日:2014-08-15
    发明作者:Peter Dipl Ing Dr Schöggl
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 56556
    The invention relates to a vehicle, in particular racing vehicle, with a drive unit having an internal combustion engine, with at least one heat-emitting component or a heat-dissipating assembly, wherein the component or the assembly is adjacent to at least one of a working gas, in particular air, space, in particular at least is partially surrounded by the space flowed through, wherein the space has a flow inlet and a flow outlet and the flow outlet is arranged in the region of an output-increasing device of the vehicle. Furthermore, the invention relates to a method for increasing the output in a vehicle.
    In racing and sports vehicles accelerations, decelerations and cornering accelerations are achieved, which exceed the value of 1 g (= acceleration due to gravity) considerably. Such values are only possible if the limits of adhesion between the tires and the road surface are increased with aerodynamic aids. On the vehicle body strong downforce is generated. Front wing, rear wing and a special shaping of the actual vehicle body serve this purpose. A dominating role is played by the design of the vehicle underbody. The aim is to accelerate the air flowing under the vehicle floor as much as possible. The higher their speed, the stronger according to the Bernoulli law their suction power and the stronger the force exerted on the vehicle underbody downforce. To achieve the greatest possible acceleration of the underbody air, the kinetic energy of the exhaust gases is used in today's racing cars: The underbody is bent upwards at the rear of the vehicle and shielded to the side usually with vertical aerodynamic baffles and possibly divided in the middle. In this way creates a diffuser for the air flowing under the vehicle. Into this diffuser zone, the ends of the exhaust pipes are introduced with horizontal jet direction aiming backwards. The exiting at high velocity exhaust gases exert on the air under the subsoil a suction effect. They increase their speed and thus their suction on the underbody and thus the output of the vehicle.
    From the AT 510,623 Bl a vehicle with a thermal power plant for the recovery of heat from the exhaust system with a hot air turbine is known, which drives a compressor, the air as working gas in a 2/29 2
    Outlet system promotes ummantelnden space whose outlet is connected to the hot air turbine. The outlet opening of the exit flow path of the hot air turbine is arranged in the region of an output-increasing device, which is formed by a diffuser formed by the vehicle floor. Due to the increase in volume due to the supply of heat and the subsequent outflow of the working gas in the region of the diffuser, an additional output can be generated. The disadvantage, however, is that the hot air turbine must be started from the idle state by external means.
    The object of the invention is to improve the road holding of the vehicle in the simplest possible way by utilizing the waste heat of at least one component or at least one module.
    According to the invention this is achieved in that the space flowed through between at least one flow inlet and at least one flow outlet has at least one flow section with a diffuser-like widening flow cross-section.
    The heat-emitting component or the heat-dissipating assembly can be formed, for example, by the exhaust system of the internal combustion engine. The heat of the exhaust system can be used particularly effectively if the exhaust system has at least one exhaust manifold surrounded by at least one air-flowed space and / or at least one exhaust duct surrounded by at least one air-flowed space in the cylinder head of the internal combustion engine.
    The inlet opening of the flow inlet is directed in the direction of travel. In a preferred embodiment of the invention, it is provided that at least one vehicle radiator is arranged in the region of at least one flow inlet. The incoming air is preheated by the cooler. The vehicle radiator can be arranged outside the space upstream of the flow inlet or downstream of the inlet opening within the room.
    The space through which flows is preferably a jacket space which at least partially, preferably predominantly, surrounds the component or the assembly. Due to the dynamic pressure, air enters the room while driving and flows around the 3/29 3
    Mantelraumes the heat-emitting component or the heat-emitting assembly.
    Losses by line deflections can be avoided if possible, when the exhaust system and this at least partially surrounding shell space are flowed through in the same direction. The space through which it flows thus at least partially forms a heat exchanger together with the outlet system.
    The at least one outlet opening of the flow outlet of the flow-through space is arranged so that the resulting overpressure increases the efficiency of the aerodynamic component. As a result, the output of the vehicle can be significantly increased.
    The output-increasing device may be formed by a preferably formed by a vehicle underbody of the vehicle diffuser in the spot area of the vehicle, wherein at least one outlet opening of the flow outlet of the space flowed through in the region of the diffuser is arranged.
    In particular, it can be provided that at least one outlet opening of the flow outlet in the outlet region of the diffuser, preferably partially formed by a trailing edge of the diffuser, is arranged. The outlet opening can also - viewed in the direction of travel - laterally next to the diffuser - preferably be arranged in a rear wheel of the vehicle facing the region of the diffuser - or over the outlet edge of the diffuser. This can be dispensed with potentially disturbing openings in the diffuser. In particular, in the case of a lateral outlet, it is advantageous if the space at the end of the heat exchanger or at the end of the jacket space is divided into two lateral outlet regions. It is provided in a particularly advantageous embodiment that the outlet opening of the flow outlet in the initial region of the diffuser - preferably in the region of a formed by a bend transition between a substantially parallel to the roadway and - seen counter to the direction-increasing-area of the vehicle underbody is arranged. The outlet opening of the flow outlet for the heated air is preferably arranged such that a lateral pressure equalization between the 4/29
    Environment is obstructed in a lateral area of the diffuser and the space inside the diffuser.
    The air has a temperature of about 30 ° C before flowing into the heat exchanger. In the heat exchanger, the air is heated by the hot exhaust gases of the exhaust system to several hundred ®G. The volume increase leads to high exit velocities from the space flowed through, in particular when the flow outlet of the space is designed as a nozzle. The high velocity hot air exerts a suction effect on the air under the floor of the vehicle. It increases their speed and thus the suction effect on the underbody, which leads to a significant increase in output of the vehicle.
    Calculations and tests have shown that the best results can be achieved if the flow inlet has a smaller flow cross-section than the flow outlet.
    In detail, between the at least one inlet region and the at least one outlet region there is at least one flow cross-section or group of flow cross-sections remote from at least one inlet opening whose cross-sectional area or sum of the cross-sectional areas is greater than the smallest flow cross-section of the inlet opening or the sum of the smallest flow cross sections of all inlet openings, and smaller than the largest flow cross section of the outlet region or the sum of the flow cross sections of all outlet regions.
    It is particularly advantageous if the sum of all flow cross-sections which are the same distance away from the inlet opening-as it progresses in the flow direction-increases between the flow inlets, in particular the inlet openings, and the largest cross-sectional area of the flow cross-section of the at least one flow outlet-preferably continuously.
    The sum of the cross-sectional areas at the beginning of the flow or inlets (s) is advantageously less than the largest cross-sectional area of the flow outlet. 5/29 5
    Large amounts of swirl can be achieved if the space between the flow inlet and the first flow cross section is formed as a first diffuser region, wherein it is particularly advantageous if the space between the beginning region and the end region of the heat exchanger is designed as a second diffuser, wherein preferably the second diffuser Diffuser region has a plurality of successive and / or parallel sections.
    In a particularly suitable for racing vehicles embodiment of the invention, it is provided that the space has at least two lateral branches, each with a flow inlet, preferably wherein the branches upstream of the flow outlet - particularly preferably in the area or downstream of the exhaust manifold (s) - to a Combine collecting space. The inlet openings can thus be arranged on both sides in the region of lateral air or cooling channels.
    Thus, air flows through dynamic pressure through at least one of the direction of flow facing flow inlet in at least one hot surfaces of the exhaust system, preferably exhaust ducts, exhaust manifold, and / or exhaust gas turbine, surrounding space, then flows around the hot surfaces of the exhaust system, taking a - preferably maximum possible - Amount of heat, the air expands. Finally, the hot air flows out of the room through at least one flow outlet in the region of a preferably formed by the vehicle floor of the vehicle diffuser - especially preferably laterally in the beginning of the diffuser - at a higher speed than the vehicle speed so that the pressure inside the diffuser decreases and / or a pressure equalization between the environment and the interior of the diffuser is prevented or reduced by the outflowing air forms an air exchange obstructing air curtain between the environment and the laterally open to the diffuser. Due to the higher negative pressure inside the diffuser, the output of the vehicle can be significantly increased.
    The output-increasing effect sets itself automatically from a certain driving speed by the increasing back pressure and increases with the driving speed. In the arrangement according to the invention no additional means for starting the system is necessary. 6/29 6
    The invention will be explained in more detail below with reference to FIGS. Show it
    1 shows an inventive vehicle in a plan view in a first embodiment,
    2 this vehicle in a side view,
    3 this vehicle in a rear view,
    4 shows a vehicle according to the invention in a plan view in a second embodiment variant,
    5 this vehicle in a side view,
    6 this vehicle in a rear view,
    7 shows a vehicle according to the invention in a plan view in a third embodiment, FIG.
    8 this vehicle in a side view,
    9 this vehicle in a rear view,
    10 shows a vehicle according to the invention in a plan view in a fourth embodiment,
    11 this vehicle in a side view,
    12 this vehicle in a rear view,
    13 shows a vehicle according to the invention in a plan view in a fifth embodiment, FIG.
    14 this vehicle in a side view,
    Fig. 15 this vehicle in a rear view, 7/29 7
    16 is a detail of this vehicle in a section along the line XVI-XVI in Fig. 13 or 14, and
    17 shows the cross-sectional profile of the vehicle according to the invention according to the first, second, third, fifth embodiment variant.
    Functionally identical parts are provided with the same reference numerals.
    FIGS. 1 to 16 each show a vehicle 1, for example a racing vehicle, whose vehicle floor is designated 2. The vehicle floor 2 has a diffuser 2 a, in particular in the region of the tail lb. Reference numeral 3 designates the exhaust system of an internal combustion engine (not shown). The exhaust system 3 has exhaust ports 3a, exhaust manifold 3b and exhaust pipes 3c. With reference numeral 5, the roadway is indicated. In the exhaust system 3, at least one exhaust-gas turbine 17 of an exhaust-gas turbocharger, which is shown by way of example in FIGS. 13 and 14, can also be arranged.
    The arrow P indicates the direction of travel of the vehicle 1.
    The exhaust system 3 forming a heat-emitting assembly is surrounded by the jacket space 6a (sheathing) of a space 6 through which air flows, which space 6 is located between a flow inlet 7 in the middle or front area 1a of the vehicle 1 and a flow outlet 8 upstream of an outlet edge 2b of the diffuser 2a extends in the rear area lb. In this case, an outlet opening 8a is partially formed by the outlet edge 2b of the diffuser 2a. The jacket space 6a and the outlet system 3 are parts of a heat exchanger 9. The inlet opening 7a of the flow inlet 7 is directed forward in the direction of travel P. The exhaust system 3 and this at least partially surrounding space 6 are traversed in the same direction by exhaust A and L air.
    As a result of the dynamic pressure occurring in front of the inlet opening during the travel of the vehicle 1, air L flows, for example, into the space 6 at 30 ° C., flows through the jacket space 6 a of the heat exchanger 9 and is heated to, for example, 250 ° C., whereby the volume of the air L increases. In the region of the flow outlet 8, the hot air L emerges at high speed from the outlet opening 8a near the outlet edge 2b of the diffuser 2a. As a result, the air flowing under the vehicle floor 2 during the drive of the vehicle 1 is greatly accelerated, which substantially increases the output of the vehicle 1.
    The flow inlet 7 is understood here as the region of the space 6 that extends between the inlet opening 7a and the heat exchanger 9. The flow outlet 8 is analogous to the region which extends between the heat exchanger 9 and the outlet opening 8a.
    FIGS. 1 to 3 show an embodiment in which the air from the free environment flows unimpeded into the space 6 through the inlet opening 7a.
    FIGS. 4 to 6 show an embodiment in which a vehicle radiator 11 of a water or oil cooling system of the vehicle 1 is arranged upstream of each inlet opening 7 a. The air thus flows through the designed as air / water or an air / oil heat exchanger vehicle radiator 11 in the inlet region 7 of the room 6 a.
    The embodiment shown in FIGS. 7 to 9 differs from the variant shown in FIGS. 4 to 6 in that at least one vehicle radiator 11 is arranged in the inlet region 7 of the chamber 6 downstream of the inlet opening 7 a, so that the Air L flows through the vehicle radiator 11, which may be an air / water or an air / oil heat exchanger, in the jacket region 6a of the space 6
    FIGS. 10 to 12 show a fourth variant in which the air in the rear wheels 4 flows out of the space 6 adjacent side regions of the diffuser 2 a. The space 6 splits downstream of the jacket space 6a into two lateral outlet regions 8. Optionally, a vehicle radiator 11 may be arranged upstream of the inlet region 7 as shown in FIGS. 4 to 6 or in the inlet region 7 as shown in FIGS. 7 to 9.
    The fifth embodiment variant shown in FIGS. 13 to 16 differs from the fourth variant shown in FIGS. 10 to 12 in that the transition formed by a kink 15, or the starting region, viewed in the direction of travel, of the Diffuser 2a is arranged vertically below the rear axle 4a of the rear wheel 4 wherein the outlet opening 8a of the flow outlet 8 in a lateral region of the kink 15 and the beginning of the 9/29 9
    Diffuser 2a is arranged so that the outflowing heated air L is directed to the rear and forms a lateral air curtain on both sides of the diffuser. The forming air curtain at the side of the diffuser 2a obstructs the pressure compensation Δρ between the interior 16 of the diffuser 2a and the surroundings U of the vehicle 1 (FIG. 16), as shown in FIG. 16, so that the suppression ps forming in the interior 16 of the diffuser 2a preserved.
    By a special shape of the space 6, in particular the cross-sectional profile of the space 6 in the flow direction, particularly high output forces can be generated. Thus, it has proved to be advantageous if the space 6 between the inlet opening 7a and a in the initial region 9a of the heat exchanger 9 bzW. the shell space 6a is formed as the first diffuser region 12, between the initial region 9a and the end region 9b of the heat exchanger 9 or the jacket region 6a as at least a second diffuser region 13, and between the end region 9b of the heat exchanger 9 and the outlet opening 8a as a nozzle 14, such as is shown schematically in Fig. 13 (in Fig. 13, the nozzle is shown rotated by 90 ° in the plane of the drawing). In this case, each second diffuser region 13 may have a plurality of partial regions 13a, 13b, 13c connected in series. Furthermore, in particular in the area of the exhaust ducts 3a, partial areas 13a ', 13a " of the second diffuser region 13 may be connected in parallel to the subregions 13a.
    As can be seen from the figures, the space 6 may be formed substantially branched and - viewed in plan view - in particular a - seen in the direction of travel - left branch LA and a right branch RA, each with an inlet region 7 and portions 13a, 13a ' 13a ", 13b. Downstream of the subregions 13b, the two branches LA, RA of the space 6 unite in the area of the last subarea 13c of the heat exchanger 9 to form a common collecting space SR.
    In FIG. 17, various ones are shown for those previously shown in FIGS. 1 to 3, 4 to 6, 7 to 9, 10 to 12, or 13 to 13. 16 illustrated embodiments valid flow cross-sectional areas drawn. F0 is the smallest flow cross-section of the inlet opening 7a, with Fi the first flow cross-section in the initial region 9a of the heat exchanger 9, F2 the second flow cross-section in the end region 9b of the heat exchanger 9 and F3 10/29 10 denotes the flow cross-section of the outlet opening 8a. Furthermore, intermediate cross sections Fn, F12, and F13, at the end of the exhaust ducts 3a, and at the beginning and end of the exhaust manifold 3b registered. The sum of the cross-sectional areas (ZF, ZFi, ZFn, ZFi2, ZFi3, F2) that are the same distance from the inlet opening 7a increases between the flow inlet 7, in particular the inlet opening 7a, and 7, viewed in the flow direction of the air L flowing through the chamber 6 the flow outlet 8, in particular the end 9 b of the heat exchanger 9 to.
    To increase the output air L flows by dynamic pressure through at least one of the direction of travel P facing flow inlet 7 in at least one hot surfaces of the exhaust system 3, preferably exhaust ducts 3a, exhaust manifold 3b, and / or exhaust gas turbine 10, surrounding space 6 a. The hot surfaces of the exhaust system 3 are flowed through by the air L, with the maximum possible amount of heat being absorbed. The heating of the air L increases the volume of the air L. The heated air L leaves the space 6 again through at least one flow outlet 7 in the region of a diffuser 2a formed by the vehicle floor 2 of the vehicle 1 at a higher speed than the driving speed. The high-velocity hot air L exerts a suction effect on the air under the vehicle floor 2. It increases their speed and thus the suction effect on the underbody, resulting in a significant increase in output of the vehicle 1. It is particularly advantageous if the air L flows laterally of the diffuser 2a so that a pressure equalization Δρ between the environment U and the interior 16 of the diffuser 2a is prevented or reduced. 11/29
    权利要求:
    Claims (25)
    [1]
    1. PATENT CLAIMS (1), in particular a racing vehicle, with a drive unit having an internal combustion engine (4) with at least one heat-emitting component or a heat-dissipating assembly, the component or assembly being attached to at least one of a working gas, in particular air, flowed through space (6) is bordered, in particular at least partially surrounded by the space flowed through (6), wherein the space (6) has a flow inlet (7) and a flow outlet (8) and the flow outlet (7) in the region of an output-increasing device of the Vehicle (1) is arranged, characterized in that the flow-through space (6) between at least one flow inlet (7) and at least one flow outlet (8) has at least one flow section with diffuser-like expanding flow cross-section.
    [2]
    2. Vehicle (1) according to claim 1, characterized in that at least one inlet opening (7a) is directed at least one flow entrance (7) in the direction of travel (P).
    [3]
    3. Vehicle (1) according to claim 1 or 2, characterized in that at least one vehicle radiator (11) in the region of at least one flow inlet (7) is arranged.
    [4]
    4. Vehicle (1) according to claim 3, characterized in that at least one vehicle radiator (11) upstream of the inlet opening (7a) of the flow inlet (7) is arranged.
    [5]
    5. Vehicle (1) according to claim 3, characterized in that at least one vehicle radiator (11) downstream of the inlet opening (7a) of the flow inlet (7) within the space flowed through (6) is arranged.
    [6]
    6. Vehicle (1) according to one of claims 1 to 5, characterized in that the output-increasing device by a preferably by a vehicle underbody (2) of the vehicle (1) formed diffuser (2a) in the rear area (lb) of the vehicle (1) is formed, wherein at least one 12/29 12 outlet opening (8a) of the flow outlet (8) in the region of the diffuser (2a) is arranged.
    [7]
    7. Vehicle (1) according to claim 6, characterized in that at least one outlet opening (8a) of the flow outlet (8) in the end region of the diffuser (2a) of the subfloor (2), preferably adjacent or above a trailing edge (2b) of the diffuser ( 2a), or at least one outlet opening (8a) is partially formed by an outlet edge (2b) of the diffuser (2a).
    [8]
    8. Vehicle (1) according to claim 6, characterized in that at least one outlet opening (8a) of the flow outlet (8) is arranged laterally, preferably in a rear wheel (4) of the vehicle (1) facing the region of the diffuser (2a), preferably in the diffuser (2a) of the subsoil (2) opens.
    [9]
    9. Vehicle (1) according to claim 6 or 8, characterized in that the outlet opening (8a) of the flow outlet (8) in the initial region of the diffuser (2a), preferably in the region of a bend formed by a bend (15) between a substantially parallel to the carriageway and a - seen counter to the direction of travel (P) - rising region of the vehicle floor (2) is arranged.
    [10]
    10. vehicle (1) according to claim 8 or 9, characterized in that the outlet opening (8 a) of the flow outlet (8) for the heated air (L) is arranged so that a lateral pressure compensation (Δρ) between the environment (U) in a lateral region of the diffuser (2a) and the interior (16) of the diffuser (2a) is obstructed.
    [11]
    11. Vehicle (1) according to one of claims 1 to 10, characterized in that the space (6) through which flows at least in sections a jacket space (6a) which at least partially, preferably predominantly surrounds the component or the assembly.
    [12]
    12. Vehicle (1) according to one of claims 1 to 9, characterized in that the heat-emitting component or the heat-dissipating assembly is formed by the exhaust system (3) of the internal combustion engine. 13/29 13
    [13]
    13. Vehicle (1) according to claim 12, characterized in that the exhaust system (3) at least one of at least one flowed through space (6) surrounding the exhaust passage (3a) in the cylinder head of the internal combustion engine (4) and / or at least one of at least one flowed through Room (6) surrounded Abgaskrummer (3b) and / or at least one exhaust gas turbine (10).
    [14]
    14. Vehicle (1) according to claim 13, characterized in that at least one exhaust manifold (3b) is individually sheathed, wherein preferably all the exhaust manifolds (3b) are individually sheathed and the at least one sheathing (6a) is part of the flow-through space (6). is.
    [15]
    15. Vehicle (1) according to claim 13 or 14, characterized in that at least one exhaust gas turbine (10) is jacketed, wherein preferably the vehicle (1) has two exhaust gas turbines (10) or at least one exhaust gas turbine (10) with two exhaust gas flows and both Exhaust gas turbines (10) or exhaust gas flows - preferably individually - are sheathed, and wherein the at least one sheath (6a) is part of the space flowed through (6).
    [16]
    16. Vehicle (1) according to one of claims 12 to 15, characterized in that the outlet system (3) and at least partially surrounding this space (6) are flowed through in the same direction.
    [17]
    17. Vehicle (1) according to one of claims 1 to 16, characterized in that the flowed through space (6) is part of at least one heat exchanger (9).
    [18]
    18. Vehicle (1) according to one of claims 1 to 17, characterized in that between the at least one inlet region (7) and the at least one outlet region (8) at least one of at least one inlet opening (7a) in a defined distance remote flow cross-section ( Ft; Fn; Fi2; F13) or a group of flow cross-sections (F'i; Fn; i2) Fi3) whose cross-sectional area or sum of the cross-sectional areas (IFi; IFn; ZF12; ZFi3) is greater than the smallest flow cross-section (F0) of the inlet opening (7a) or the sum of the smallest flow cross-sections (ZF0) of all inlet openings (7a), and smaller than the largest flow cross-section (F2) of the 14/29 14 outlet region (8) or the sum of the flow cross-sections of all Exit areas (8).
    [19]
    19. Vehicle (1) according to one of claims 1 to 18, characterized in that the sum of all of the inlet opening (7a) equidistant flow cross-sections (F0; Fi; Fn; Fi2; Fi3; F2) - when proceeding in the flow direction (L ) of the space (6) - between the flow inlets (7), in particular the inlet openings (7a), and the largest cross-sectional area of the flow cross-section (F2) of the at least one flow outlet (8) - preferably continuously - increases.
    [20]
    20. Vehicle (1) according to one of claims 1 to 19, characterized in that the sum of the cross-sectional areas at the beginning of the flow or inlets (s) (7) is less than the largest cross-sectional area (F2) of the flow outlet (8).
    [21]
    21. Vehicle (1) according to claim 17 to 20, characterized in that the space (6) between the flow inlet (7) and an initial region of the heat exchanger (9) as the first diffuser region (12) is formed.
    [22]
    22. Vehicle (1) according to any one of claims 17 to 21, characterized in that the space (6) between the initial region (9a) and the end region (9b) of the heat exchanger (9) as a second diffuser region (13) is formed, Preferably, the second diffuser region (13) has a plurality of subregions (13a, 13a ', 13a ", 13b) connected in series and / or in parallel.
    [23]
    23. Vehicle (1) according to one of claims 1 to 22, characterized in that the flow outlet (8) of the space (6) preferably between the second flow cross-section (F2) and the outlet opening (8a) - formed as a nozzle (14) is.
    [24]
    24. Vehicle (1) according to one of claims 1 to 23, characterized in that the space (6) has at least two branches (LA, RA) each having a flow inlet (7), wherein preferably the branches (LA, RA) upstream of the flow outlet - particularly preferably in the region or downstream of the exhaust manifold (s) (13b) - to a collecting space (SR) unite.
    [25]
    25. A method for increasing the output in a vehicle (1) according to one of claims 1 to 24, characterized in that air (L) by dynamic pressure through at least one of the direction of travel (P) facing the flow inlet (7) in at least one hot surfaces of the Outlet system (3), preferably exhaust ducts (3a), exhaust manifold (3b), and / or the exhaust gas turbine (10), surrounding space (6) flows around the hot surfaces of the exhaust system (3) while receiving a - preferably maximum possible - amount of heat and expands, and that the hot air (L) from the space (6) through at least one flow outlet (7) in the region of a, preferably through the vehicle floor (2) of the vehicle (1) formed diffuser (2a) - particularly preferably laterally in Beginning region of the diffuser (2 a) - flows at a higher speed than the vehicle speed so that the pressure in the interior (16) of the diffuser (2 a) decreases and / or a pressure compensation (Δρ) between the Environment (U) and the interior (16) of the diffuser (2a) is prevented or reduced. 2013 03 07 Fu 16/29
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    同族专利:
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    AT510623B1|2010-11-11|2012-09-15|Avl List Gmbh|DRIVE UNIT FOR A VEHICLE|
    DE3410296A1|1984-03-21|1985-09-26|Herwig 4156 Willich Fischer|Device for improving the grip of vehicles|
    DE20016748U1|2000-09-28|2000-11-30|Abbrecher Siegfried|Variable aerodynamic cooling system|
    DE102008039495A1|2008-08-23|2010-02-25|Bayerische Motoren Werke Aktiengesellschaft|Cover elements e.g. laminar underbody covers, for underbody of motor vehicle i.e. car, have elongated recess and/or elevation that runs in direction of air flow, where air flow is self-adjustable in underbody during drive of motor vehicle|
    AT510269B1|2010-11-11|2012-03-15|Avl List Gmbh|METHOD FOR THE DEPOSIT GENERATION OF VEHICLES OPERATED BY INTERNAL COMBUSTION ENGINES|GB2536214B|2015-03-05|2020-05-27|Elogab O|Engine system and method of generating electricity from an internal combustion engine|
    CN110886796A|2018-09-11|2020-03-17|南京林业大学|Truck drum type braking air cooling device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50035/2013A|AT513883B1|2013-01-22|2013-01-22|Vehicle, in particular racing vehicle|
    ATA50154/2013A|AT513886B1|2013-01-22|2013-03-07|Vehicle, in particular racing vehicle|ATA50154/2013A| AT513886B1|2013-01-22|2013-03-07|Vehicle, in particular racing vehicle|
    PCT/EP2014/051076| WO2014114611A1|2013-01-22|2014-01-21|Vehicle, in particular racing vehicle|
    EP14701041.7A| EP2948363B1|2013-01-22|2014-01-21|Vehicle, in particular racing vehicle|
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