DE102015205415A1 - Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle - Google Patents

Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle

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Publication number
DE102015205415A1
DE102015205415A1 DE102015205415.2A DE102015205415A DE102015205415A1 DE 102015205415 A1 DE102015205415 A1 DE 102015205415A1 DE 102015205415 A DE102015205415 A DE 102015205415A DE 102015205415 A1 DE102015205415 A1 DE 102015205415A1
Authority
DE
Germany
Prior art keywords
radiator fan
frame
air
8th
passage area
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.)
Pending
Application number
DE102015205415.2A
Other languages
German (de)
Inventor
Helmut Hoyer
Bernd Brinkmann
Johann Hendrik Wegers
Christian Jolk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ford Global Technologies LLC
Original Assignee
Ford Global Technologies LLC
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 Ford Global Technologies LLC filed Critical Ford Global Technologies LLC
Priority to DE102015205415.2A priority Critical patent/DE102015205415A1/en
Priority claimed from DE202015101896.7U external-priority patent/DE202015101896U1/en
Publication of DE102015205415A1 publication Critical patent/DE102015205415A1/en
Application status is Pending legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/10Guiding or ducting cooling-air, to, or from, liquid-to-air heat exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08Fluid driving means, e.g. pumps, fans

Abstract

The invention relates to a radiator fan assembly (1) for a cooling system of a liquid-cooled vehicle engine. The radiator fan assembly (1) comprises a housing (2) having a passage area (3) for cooling air and a working machine (14) for accelerating cooling air in a flow direction (x) through the housing (2). The housing (2), viewed in the flow direction of the cooling air, can be arranged in front of or behind a surface region of a cooler of the cooling system. According to the invention, the working machine (14) lies outside the passage area (3). In this case, the housing (2) has a through-region (3) peripherally bounding quadrangular frame (7) and at least one the passage region (3) in individual cells (4, 5, 6) dividing gutter (12, 13). Furthermore, in the frame (7) and the at least one intermediate web (12, 13, 18) with the working machine (14) medium, so air-conductively connected air duct is formed, which has a the passage region (3) facing the air outlet opening.

Description

  • The present invention relates to a radiator fan assembly for a cooling system of a liquid-cooled vehicle engine according to the preamble of claim 1.
  • Vehicle engines in the sense of internal combustion engines should be limited in their operating temperature at the top. To comply with this particular upward, appropriate cooling measures are required. For this purpose, air-cooled vehicle engines have areas with a mostly rib-like outer structure, in order to deliver a portion of the operating heat to the ambient air via the thus enlarged surface. In contrast, liquid-cooled vehicle engines are connected to a cooling system in which a coolant flowing around the engine block and the cylinder head of the vehicle engine absorbs a large part of the resulting waste heat. For this purpose, usually arranged in the housing wall of the vehicle engine channels are provided, which together with the coolant passing through these form a so-called coolant jacket.
  • To prevent overheating of the coolant, this is then passed through a self-contained cooling circuit of the cooling system through a suitable radiator. In this case, at least part of the heat absorbed by the coolant is released via the radiator, which is usually designed as an air-coolant heat exchanger, into the ambient air. Such coolers have a structure which can be flushed by the ambient air in the form of cooling air and at the same time can be flowed through by the coolant. In this way, a continuous delivery of the absorbed by the coolant heat of the operating vehicle engine to the ambient air can be realized. The effectiveness of the cooler depends essentially on the size of its passing with the cooling air in contact effective surface. Another influencing factor is the flow velocity of the cooling air, the increase of which also increases the volume of ambient air coming into contact with the surface of the cooler.
  • Depending on the temperature condition of ambient air and coolant, the flow velocity of the cooling air at low speeds and in particular when standing can no longer be sufficient. For this reason, cooling systems for liquid-cooled vehicle engines have a radiator fan assembly which can either be continuously operated or can only be engaged as needed. Said radiator fan assemblies have a working machine, for example in the form of impellers, with which a part of the ambient air can be sucked in and accelerated. The thus accelerated by the movement of the vehicle independently ambient air thus provides the necessary flow rate to ensure sufficient cooling of the vehicle engine. For this purpose, the radiator fan assembly is disposed either in front of or behind the radiator, so that the cooling air is either blown or sucked through the structure of the radiator.
  • Known radiator fan assemblies therefore have a propeller equipped with mostly radially arranged blades, which is usually driven by an electrically driven motor. Due to the inclination of the wings they are correspondingly obliquely flowed by the ambient air, so that when the propeller rotating a directed movement of the cooling air takes place. In order to extend the limited on one surface region of the radiator circle of action of the propeller on the entire surface, the radiator fan assembly comprises a suitable housing. The housing has a passage area, in the center of which the propeller is arranged. Due to the adapted to the dimensions of the surface of the radiator design of the housing, the over the rotating propeller through the passage area sucked in and accelerated cooling air is distributed accordingly.
  • From the US 2011/223015 A1 . US 2012/318393 A1 . US 2013/045084 A1 and the EP 2 191 142 B1 . GB 2466058 B and GB 2468323 A as well as the JP 56167897 A wingless domestic fans are known. By dispensing with an open-plan propeller, these have a with little noise associated operation. Their basic principle provides a round or oval frame, which circumscribes a passage area circumferentially. Within the frame, a circumferential air outlet opening is formed, from which out through the frame flowing air can escape. The air flowing through the frame is sucked in from outside through an air compressor arranged outside the passage area and accelerated accordingly so that within the frame an air pressure which is higher than the ambient pressure is established. A sufficient air flow through the passage area is achieved by a configuration of the frame in the region of the air outlet opening as Coanda surface. The air flowing out of the air outlet opening flows around the Coanda surface, whose inclined orientation widens the cross-section in the flow direction of the air. Due to the thereby decreasing air pressure ambient air is entrained, so that sets a sufficient continuous air flow.
  • Further developments of this principle for wingless living room fans go out of the CN 201982331 U and the CN 202165291 U show, which provide an automatic pivoting of the frame relative to a base housing in which the air compressor is arranged.
  • In particular, with respect to automobiles, the housing of the radiator fan assembly covers a majority of the surface of the radiator; regardless of the location of the radiator fan assembly in front of or behind the radiator. As a result, the cooler can be supplied only partially with flowing cooling air (wind), in particular in a moving vehicle, whereby its efficiency is reduced. Furthermore, the surface region of the radiator lying in the passage region of the housing is additionally concealed by the electric motor arranged in the center thereof together with the stationary propeller, which leads to a further reduction in the performance of the radiator. Due to the arrangement of the housing, the propeller also runs against a resulting dynamic pressure, which increases its energy consumption.
  • Since the space conditions in the engine compartment are very limited, the possible dimensions of a radiator fan arrangement are subject to corresponding specifications, which are to be supplemented by requirements in connection with the crash behavior and the thermal protection against the vehicle engine. Particularly in the case of vehicle engines with an exhaust system arranged in their front region, the passage region of the housing of the radiator fan arrangement together with the electric motor and propeller sometimes has to be offset far from the center of the radiator.
  • This is the only way to ensure a sufficient distance to the catalytic converter with its extremely high surface temperature, while simultaneously reducing the cooling capacity.
  • It thus becomes clear that a radiator fan arrangement driven by an electric motor with a propeller arranged in the passage region of its housing basically represents a compromise, since its effective area covers less than 50% of the actual surface of the radiator. In this respect, such radiator fan assemblies therefore certainly still provide room for improvement.
  • Against this background, the invention has the object, further develop a radiator fan assembly for a cooling system of a liquid-cooled vehicle engine to the effect that the effective surface of a combinable cooler of the cooling system is largely uncovered and the radiator fan assembly has a total of compact dimensions.
  • This object is achieved by a radiator fan assembly having the features of claim 1. Further, particularly advantageous embodiments of the invention disclose the respective subclaims.
  • It should be noted that the features listed individually in the following description can be combined with one another in any technically meaningful manner and show further embodiments of the invention. The description additionally characterizes and specifies the invention, in particular in connection with the figures.
  • A radiator fan arrangement is shown below, which is advantageously suitable for use in or on a vehicle, in particular a motor vehicle.
  • The radiator fan assembly according to the invention comprises a housing having a passage area for cooling air. In principle, the housing can be formed, for example, at least partially of metal and / or a plastic, whereby in addition to production-related requirements, the prevailing influences on the site such as temperature and contact with any media may be considered as possible material selection criteria.
  • In order first to suck in cooling air from the ambient air, the radiator fan arrangement has a working machine. By their operation, the sucked ambient air can then be accelerated in the form of cooling air in a flow direction through the housing. In order to direct the thus flowing cooling air to the surface of a radiator, it is provided that the housing of the radiator fan arrangement can be arranged either in front of or behind a surface region of the radiator of the cooling system. Depending on the arrangement and working direction, the cooling air can consequently be sucked or blown through the cooler.
  • According to the invention, a position of the working machine is provided outside the passage area of the housing. Furthermore, the housing has a passage area circumferentially bounding frame. The frame can be adapted in an advantageous manner to the outer dimensions of the auszustattenden cooler. Due to the usually square or rectangular configuration of typical radiator, the frame of the housing may also have a quadrangular or rectangular configuration in a particularly preferred manner. In this way, the effective surface area of the radiator may be almost entirely within the passage area of the radiator fan assembly housing.
  • Furthermore, at least one intermediate web which divides the passage region into individual cells can be provided. In other words, the passage area can be divided into two cells, for example by a single gutter. In the arrangement of, for example, two intermediate webs, the passage area can thus be divided into, for example, three cells. In the arrangement of more than one gutter, these can preferably be arranged parallel to each other.
  • Independently of this, a continuous air channel is formed in the frame and the at least one intermediate web. In this way, the quasi-hollow housing of the radiator fan assembly with ambient air or cooling air can be flowed through. In order to generate a corresponding current within the air duct, the air duct is connected according to the medium-conducting with the working machine. The exit of the cooling air from the housing via an air outlet opening. The air outlet opening may extend in a preferred manner circumferentially along the frame and / or the at least one gutter.
  • The resulting advantage lies in a relatively large passage area of the housing of the radiator fan assembly. In combination with a cooler, it is therefore possible that its effective surface is almost completely uncovered with cooling air can flow. This is independent of whether the cooling air is actively accelerated by the working machine or passively by the ambient air flowing in any case for other reasons (for example, wind). As a result, in particular when the vehicle is in motion with such a radiator fan arrangement, the surface of the radiator which can be flowed on solely by the airstream is raised to a maximum compared to conventional designs.
  • Because of the working machine arranged outside the passage area, the housing of the radiator fan arrangement can be designed to be excessively narrow, so that it is also possible to accommodate it within an engine compartment with only a small clearance. At the same time, the work machine provided for sucking and accelerating the cooling air may be disposed away from any components inside the engine room having a high surface temperature, so that possible thermal problems can be easily prevented.
  • According to an advantageous further development of the above-described basic concept of the invention, the part of the air duct located inside the frame may be delimited by a wall of the frame. Said wall may then comprise an inner wall and an outer wall, wherein the inner wall facing the passage area of the housing, while the outer wall is located on a side facing away from the passage area of the wall. Inner wall and outer wall are arranged in such a way to each other that they include an angle between them with respect to the cross section of the frame.
  • Opposite this angle, the inner wall has an end portion which is curved or bent into the air duct.
  • Furthermore, the outer wall has at its end opposite the angle a curved end side, which is curved towards the passage region of the housing. The bent end portion of the inner wall and the curved end face of the outer wall are arranged in such a way to each other that the bent end portion of the curved end face is at least partially encompassed. In this case, the end face and the end section are spaced apart to form the air outlet opening.
  • Due to this configuration, the necessary air outlet opening is realized with little effort, since this requires no additional components. Due to the bent into the air duct end portion of the inner wall of the air duct is narrowed toward the air outlet opening, resulting in an increased flow velocity of the cooling air out of the frame out. In this way, a dynamic pressure can first build up within the air duct, which allows a continuous outflow of cooling air from the air outlet opening out.
  • The invention provides that the housing can have an embodiment such that the cross section of the central passage area increases in the flow direction of the cooling air therethrough. In this way, the initial air pressure of the exiting from the air outlet opening cooling air decreases in the flow direction, so that due to the pressure difference in the flow direction located in front of the housing ambient air is virtually entrained. As a result, the air flow through the passage area is increased.
  • Structurally, this can be achieved by the inner wall of the frame is configured in a corresponding manner circumferentially inclined with respect to the flow direction.
  • According to a particularly preferred embodiment of the radiator fan assembly according to the invention, the frame of the housing so be formed so that its air outlet opening is inclined relative to the flow direction. Inclined here means that the direction of the effluent from the air outlet opening cooling air and the flow direction form an angle between 0 ° and 90 ° between them. Preferably, said angle can be from 20 ° to 70 °. Advantageously, this angle can be from 40 ° to 50 °. Due to the thus inclined air outlet opening, the cooling air is first passed further into the center of the passage area, so that there is a better distribution of the cooling air within the passage area. In order to achieve such an inclination of the air outlet opening, the end portion of the inner wall and the end face of the outer wall can advantageously be correspondingly inclined and aligned with each other.
  • With regard to the configuration of the frame of the housing, the latter can have two longitudinal limbs opposite one another and two transverse limbs which are likewise opposite one another. Longitudinal limbs and transverse limbs are aligned with each other in such a way that the longitudinal limbs are connected together at their respective same ends by a respective one of the transverse limbs. After this, the transverse limbs between the longitudinal limbs and the longitudinal limbs can extend correspondingly between the transverse limbs. It is envisaged that the transverse legs are made shorter compared to the longitudinal legs. The longitudinal limbs may preferably extend parallel to one another in the horizontal direction, while the transverse limbs run parallel to one another in the vertical direction. Basically, longitudinal limbs and transverse limbs are connected to one another in a medium-conducting manner, so that they form the air duct circumferentially.
  • Against this background, it is considered advantageous that the at least one intermediate web can extend between the two transverse webs, while it is connected medium-conducting with these. In this respect, the at least one intermediate web can extend parallel to the longitudinal legs.
  • Alternatively or in addition thereto, it is further provided that the at least one intermediate web or another intermediate web can extend between the longitudinal legs. Again, the intermediate web in question is then connected medium-conducting with the two longitudinal legs. Accordingly, the at least one intermediate web - or another intermediate web - may extend parallel to the transverse webs.
  • With regard to the at least one intermediate web, it is envisaged that this may likewise comprise an air outlet opening. Particularly preferably, this may also have two air outlet openings, which are then arranged such that each individual cell of the divided by the at least one gutter passage area has a circumferential air outlet opening. As a result, each individual cell of the passage area can be sufficiently supplied with cooling air. Advantageously, it is thus possible to make adjustments to the dimensions of the respective radiator in order to apply cooling air as effectively as possible to its effective surface area.
  • According to a further advantageous development of the invention, the transitions between the longitudinal limbs and the transverse limbs of the frame can each have an inner radius between them. Between the at least one intermediate web and the longitudinal limbs and / or the transverse limbs, in each case alternatively or in addition to this, an inner radius can be formed. Due to the smoothed by the inner radius transition any irregularities in the exit of the flowing cooling air from the air outlet opening are largely avoided, so that no undesirable and the cooling performance can be reduced turbulence. Also, this undesirable back pressures in the respective corners of the frame can be effectively avoided within the air duct.
  • Alternatively or in addition thereto, the outer transitions between the longitudinal limbs and the transverse limbs may have an outer radius. Due to the thus bent corner regions of the frame, a continuous flow of the cooling air through the air duct can be achieved. Abrupt transitions, as they can occur without such rounding, are thus not present, so that a uniform outlet of the cooling air is made possible out of the frame.
  • As already stated above, the invention provides an arrangement outside the passage area for the working machine. In this connection, a connection piece can be provided which can be suitably connected to the frame. The goal here is that said connector has a medium-conducting connection with the air duct and the working machine. For this purpose, the free end of the connecting piece may be connected to the working machine, which may be formed in a particularly preferred manner as an air compressor.
  • With regard to the drive of the working machine, at least two variants are advantageous. For example, the working machine can be driven by a motor, in particular an electric motor. Alternatively, the work machine and torque transmitting with the Vehicle engine be connected so that their operation takes place in dependence on the operation of the vehicle engine. Of course, a combination of these two variants is conceivable. This would have the advantage, for example, that the cooler could also be operated by the electric motor when the vehicle engine is at a standstill when the vehicle engine is switched off, while its torque is used when the vehicle engine is switched on.
  • In an advantageous manner, the working machine can be connected with the periphery of the vehicle engine torque transmitting. The connection can be made for example by a belt or a chain or a shaft. Also, a type of clutch and / or transmission between the machine and the vehicle engine is conceivable to make the performance of the machine independently of the speed of the vehicle engine.
  • According to a further advantageous development, a condenser for an air conditioning system can be provided, wherein the condenser can then be arranged within the passage region of the radiator fan arrangement. In this way, a very compact design can be achieved by the heat exchanger in the form of cooler and condenser can be arranged in a small space to each other and are supplied via the radiator fan assembly with cooling air.
  • Thanks to the invention presented here radiator fan assembly, it is now possible to leave the effective surface of a combinable cooler of a vehicle cooling system largely uncovered. The reason for this is the complete omission of the conventional working machine and the propeller within the passage area. Due to the displacement of the work machine and the advantageous use of the cooling air providing frame, the radiator fan assembly also have a total of much more compact dimensions.
  • Further advantageous details and effects of the invention are explained in more detail below with reference to different, schematically illustrated in the figures embodiments. Show it:
  • 1 a radiator fan assembly according to the invention in a view
  • 2 the radiator fan assembly according to the invention 1 in a side view,
  • 3 the radiator fan assembly according to the invention from the 1 and 2 in a supervision,
  • 4 a part of the radiator fan assembly according to the invention 1 in a perspective representation,
  • 5 an alternative embodiment of the part of the radiator fan assembly 4 in self-representation as well
  • 6 a section through a part of the radiator fan assembly of the 1 to 5 ,
  • 1 is a schematic view of a radiator fan assembly according to the invention 1 refer to. This is used for combination with a cooler, not shown, of a cooling system for a liquid-cooled vehicle engine.
  • The radiator fan assembly 1 includes a housing 2 , which can be arranged in front of or behind the surface of the cooler not shown in detail. In the center of the housing 2 is a transit area 3 formed, which in this case in three separate cells 4 . 5 . 6 is divided. Through the passage area 3 or the cells 4 . 5 . 6 Through the radiator can be acted upon with not further apparent cooling air.
  • In order to obtain the most accurate cover or full-surface coverage of the effective surface of the non-visible cooler, the housing has 2 initially a substantially square or rectangular frame 7 on, which can be adapted to the outer dimensions of the radiator in an advantageous manner. Said frame 7 has two horizontal longitudinal legs 8th . 9 and two vertical transverse legs 10 . 11 , The longitudinal legs 8th . 9 and the transverse legs 10 . 11 limit the dimensions of the frame 7 to the outside, while at the same time the passage area 3 or the cells 4 . 5 . 6 at least partially limit to the inside. The long legs are visible 8th . 9 and the transverse legs 10 . 11 each spaced parallel to each other, wherein the transverse legs 10 . 11 opposite the longitudinal thighs 8th . 9 are shorter. Furthermore, the longitudinal legs 8th . 9 and the transverse legs 10 . 11 not further recognizable to each other medium-conducting, so air-conductively connected in the context of the invention.
  • The subdivision of the passage area 3 into the individual cells 4 . 5 . 6 takes place here by two intermediate webs 12 . 13 , which is perpendicular between the two longitudinal legs 8th . 9 parallel to the transverse webs 10 . 11 extend. Also the intermediate bridges 12 . 13 are not recognizable way with the two longitudinal legs 8th . 9 air-conducting connected or connect the two longitudinal legs 8th . 9 conducting air together.
  • Outside the passage area 3 is a working machine 14 arranged, which is adapted to suck in and not more clearly identified ambient air. This is the working machine 14 exemplified as an air compressor and a connector 15 with the frame 7 air-conductively connected. Specifically, this connection exists in the present case via one of the two transverse legs 11 of the frame 7 ; more about the with respect to the representation of 1 right transverse leg 11 , In this way, the sucked ambient air on the machine 14 in the frame 7 of the housing 2 pass through which it then flows at elevated pressure. The connection piece 15 can also be made much longer than indicated in the figures, the working machine 14 at any suitable location also far away from the housing 2 can be arranged. Any airflow resistance within the fitting 15 is negligible or optionally compensated by a stronger machine. In terms of the operation of the working machine 14 this can be mechanically driven by an electric motor, not shown further, and / or by the likewise not apparent vehicle engine, for example via a belt.
  • The required exit of the cooling air from the frame 7 will be in later 6 clarified in more detail.
  • With a view of the frame 7 of the housing 2 this is designed such that in the corners of the frame 7 located inner transitions between the longitudinal legs 8th . 9 and the transverse legs 10 . 11 as well as to the intermediate bridges 12 . 13 each have an inner radius 16 are rounded. In addition, those are in the corners of the frame 7 located outer transitions between the longitudinal legs 8th . 9 and the transverse legs 10 . 11 also rounded, by each having a corresponding outer radius 17 have.
  • 2 is a side view of the radiator fan assembly according to the invention 1 out 1 refer to; closer to the in 1 right transverse leg shown on the right 7 of the frame 7 , As you can see, the frame points 7 laterally a constant depth a, which extends over the entire height b of the housing 2 or its frame 7 extends. From this side view is the cross-sectional shape of the machine 14 clearly visible, which is recognizable substantially round, in particular circular. It should also be noted that the working machine 14 opposite the housing 2 returns. In other words, there is a center c of the work machine 14 outside the depth a of the frame 7 ,
  • 3 illustrates the radiator fan assembly according to the invention 1 from the 1 and 2 again in a supervision on their in 1 top longitudinal leg 8th of the frame 7 ,
  • 4 shows the frame 7 of the housing 2 from the previous ones 1 to 3 in a perspective view. For reasons of clarity, this (as well as in the following 5 ) on the representation of the working machine 14 together with connecting piece 15 waived.
  • Compared to the previous illustrations, this is modified in the present case, that the corners of the frame 7 no outer radius here 17 own, but are designed vertically in contrast. Furthermore, have the transitions between the longitudinal legs 8th . 9 and the transverse legs 10 . 11 as well as to the intermediate bridges 12 . 13 in each case an inner radius 16 so that they continue to be rounded.
  • 5 illustrates a possible variant of the design of the frame 7 from the previous ones 1 to 4 , Obviously, this now points instead of the two intermediate webs 12 . 13 only a single gutter 18 on which the passage area 3 correspondingly in only two cells 19 . 20 divided.
  • Said gutter 18 is also not vertical, but horizontally oriented, so that this parallel to and between the two longitudinal legs 8th . 9 runs. This extends the gutter 18 between the two crossbars 10 . 11 , passing these through the gutter 18 are interconnected in a manner not further apparent air-conducting. Analogous to the previous version, the transitions between the longitudinal legs are also here 8th . 9 and the transverse legs 10 . 11 as well as to the individual gutter 18 each with an inner radius 16 rounded designed.
  • 6 only illustrates a representative section through the housing 2 which in particular for its framework 7 applies; closer to the longitudinal legs 8th . 9 and the transverse legs 10 . 11 , Of course, this embodiment also for the intermediate webs 12 . 13 . 18 Find application, wherein the cross section shown here can then be preferably performed mirrored along a mirror plane D substantially.
  • Clear is the frame 7 hollow, so that this one air duct 21 has. As mentioned earlier, said air duct 21 mutatis mutandis, in the intermediate webs not shown here 12 . 13 . 18 executed. Basically, said air duct 21 with the work machine 14 Medium, so air-conductively connected. The air duct 21 is present through the wall of the frame 7 limited. The wall comprises a passage area 3 facing inner wall 22 and an opposite, the passageway area 3 corresponding outer wall facing away 23 , Visible run inside wall 22 and outer wall 23 not parallel to each other. Rather, the inner wall 22 opposite the outer wall 23 inclined, leaving the inner wall 22 and outer wall 23 enclose an angle e between them.
  • Furthermore, the inner wall has 22 an opposite end of the angle e 24 which is in the air duct 21 bent into curved. The end section describes 24 a curve, leaving a rounded transition between the inner wall 22 and the end section 24 until its free end results. In contrast, the outer wall 23 a front side opposite the angle e 25 on, which is also curved. The curvature of the front side 25 is in such a way that this in the passage area 3 is bent into it and the end portion 24 the inner wall 22 at least partially encompasses. Visible are front side 25 and end section 24 under formation of an air outlet opening 26 spaced from each other, which the passage area 3 is facing. The through the front page 25 and the end section 24 formed air outlet 26 runs in such a way that from the air duct 21 outflowing cooling air is inclined with respect to its outlet direction F with respect to a flow direction x. As the flow direction is perpendicular to the height b of the housing 2 extending direction to understand in which, for example, wind through the passage area 3 flows through it.
  • Looking at the cross section shown here it becomes clear that the inner wall 22 of the frame 7 is formed circumferentially inclined relative to the flow direction x. In this way, the cross section of the passage area increases 3 in the flow direction x. Due to the resulting pressure differences within the passage area 3 in the direction of the flow direction x ambient air can flow in a manner not shown in the direction of flow x, whereby the flow of cooling air from the frame 7 is supplemented by a part of the entrained ambient air.
  • LIST OF REFERENCE NUMBERS
  • 1
     Radiator fan arrangement
    2
    Housing of 1
    3
    Passage area of 2
    4
    Cell of 3
    5
    Cell of 3
    6
    Cell of 3
    7
    Frame of 2
    8th
    Longitudinal leg of 7
    9
    Longitudinal leg of 7
    10
    Transverse leg of 7
    11
    Transverse leg of 7
    12
    Gutter between 8th and 9
    13
    Gutter between 8th and 9
    14
    Working machine of 1
    15
    Fitting between 14 and 7
    16
     inner radius
    17
     outer radius
    18
    Gutter between 10 and 11
    19
    Cell of 3
    20
    Cell of 3
    21
    Air duct in 2
    22
    Inside wall of 2
    23
    Outer wall of 2
    24
    End section of 22
    25
    Front side of 23
    26
    Air outlet of 2
    a
    Depth of 2 respectively. 7
    b
    Height of 2 respectively. 7
    c
    Center of 14
    D
     mirror plane
    e
    Angle between 22 and 23
    F
     Outlet direction for cooling air
    x
     flow direction
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • US 2011/223015 A1 [0006]
    • US 2012/318393 A1 [0006]
    • US 2013/045084 A1 [0006]
    • EP 2191142 B1 [0006]
    • GB 2466058 B [0006]
    • GB 2468323 A [0006]
    • JP 56167897 A [0006]
    • CN 201982331 U [0007]
    • CN 202165291 U [0007]

Claims (10)

  1. Radiator fan assembly for a cooling system of a liquid cooled vehicle engine, comprising a housing ( 2 ), which has a passage area ( 3 ) for cooling air and a working machine ( 14 ) for accelerating cooling air in a flow direction (x) through the housing ( 2 ), characterized in that the working machine ( 14 ) outside the passage area ( 3 ), wherein the housing ( 2 ) one the transit area ( 3 ) circumferentially bounding quadrangular frames ( 7 ) as well as at least one passage area ( 3 ) into individual cells ( 4 . 5 . 6 . 19 . 20 ) dividing gutter ( 12 . 13 . 18 ), and wherein in the frame ( 7 ) and the at least one gutter ( 12 . 13 . 18 ) with the working machine ( 14 ) medium-conducting connected air duct ( 21 ) with a passageway ( 3 ) facing the air outlet opening ( 26 ) is trained.
  2. Radiator fan assembly according to claim 1, characterized by a the air duct ( 21 ) bounding wall of the frame ( 7 ), which one the passage area ( 3 ) facing inner wall ( 22 ) as well as the transit area ( 3 ) facing away from outer wall ( 23 ) which forms an angle (e) between itself and the inner wall ( 22 ), wherein the inner wall ( 22 ) one opposite the angle (e), in the air duct ( 21 ) in bent end portion ( 24 ), which under formation of the air outlet opening ( 26 ) from an angle (e) opposite, to the passage area ( 3 ) curved end face ( 25 ) of the outer wall ( 23 ) is at least partially encompassed.
  3. Radiator fan arrangement according to claim 1 or 2, characterized by a circumferential inclination of the inner wall ( 22 ) of the frame ( 7 ) such that the cross-section of the passage area ( 3 ) in the flow direction (x) is increased.
  4. Radiator fan arrangement according to one of the preceding claims, characterized by an arrangement and configuration of the end section (FIG. 24 ) of the inner wall ( 22 ) and the curved end face ( 25 ) of the outer wall ( 23 ) such that an outlet direction (F) for out of the air outlet opening ( 26 ) flowing cooling air relative to the flow direction (x) is inclined.
  5. Radiator fan arrangement according to one of the preceding claims, characterized in that the frame ( 7 ) two opposite longitudinal legs ( 8th . 9 ), which ends in each case one between the longitudinal legs ( 8th . 9 ) and opposite the longitudinal legs ( 8th . 9 ) shorter transverse legs ( 10 . 11 ) are conductively connected to each other medium, wherein the at least one gutter ( 12 . 13 ) between the transverse legs ( 10 . 11 ) is arranged and the two longitudinal legs ( 8th . 9 ) connects to each other medium-conducting.
  6. Radiator fan arrangement according to one of the preceding claims, characterized in that the frame ( 7 ) two opposite longitudinal legs ( 8th . 9 ), which ends in each case one between the longitudinal legs ( 8th . 9 ) and opposite the longitudinal legs ( 8th . 9 ) shorter transverse legs ( 10 . 11 ) are conductively connected to each other medium, wherein the at least one gutter ( 18 ) between the longitudinal legs ( 8th . 9 ) is arranged and the two transverse legs ( 10 . 11 ) connects to each other medium-conducting.
  7. Radiator fan arrangement according to one of the preceding claims, characterized in that the transitions between the longitudinal limbs ( 8th . 9 ) and the transverse legs ( 10 . 11 ) of the frame ( 7 ) and / or between the frame ( 7 ) and the at least one gutter ( 12 . 13 . 18 ) an inner radius ( 16 ) exhibit.
  8. Radiator fan arrangement according to one of the preceding claims, characterized in that the transitions between the longitudinal limbs ( 8th . 9 ) and the transverse legs ( 10 . 11 ) of the frame ( 7 ) an outer radius ( 17 ) exhibit.
  9. Radiator fan arrangement according to one of the preceding claims, characterized by a frame ( 7 ) medium-connected connection piece ( 15 ) to which the frame ( 7 ) opposite free end the working machine ( 14 ), wherein the working machine ( 14 ) is designed as an air compressor, which is electrically driven by an electric motor or mechanically via the vehicle engine.
  10. Radiator fan assembly according to one of the preceding claims, characterized by a condenser for an air conditioner, wherein the condenser within the passage area ( 3 ) is arranged.
DE102015205415.2A 2015-03-25 2015-03-25 Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle Pending DE102015205415A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102015205415.2A DE102015205415A1 (en) 2015-03-25 2015-03-25 Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015205415.2A DE102015205415A1 (en) 2015-03-25 2015-03-25 Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle
DE202015101896.7U DE202015101896U1 (en) 2015-03-25 2015-04-17 Radiator fan assembly for a cooling system of a liquid-cooled engine of a vehicle

Publications (1)

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DE102015205415A1 true DE102015205415A1 (en) 2016-09-29

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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018167443A1 (en) 2017-03-17 2018-09-20 Valeo Systemes Thermiques Ventilation device intended to generate a flow of air through a motor vehicle heat exchanger
WO2018197818A1 (en) 2017-04-28 2018-11-01 Valeo Systemes Thermiques Ventilation device with tubes provided with air flow guide means for a motor vehicle heat exchange module
WO2018197819A1 (en) 2017-04-28 2018-11-01 Valeo Systemes Thermiques Ventilation device with optimised-pitch tubes for a motor vehicle heat exchange module
FR3065675A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Remote heat exchange module optimized between aerodynamic conduits and heat pipes
FR3065676A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Heat exchange module with aerodynamic tubes and caloporators coming from material
FR3065753A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Optimized coanda effect coffee tube ventilation device for automotive vehicle heat exchange module
FR3065748A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Coanda effect tube ventilation device for automotive vehicle heat exchange module
FR3065752A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Double ejector coanda effect tube ventilation device for automotive vehicle heat exchange module
FR3065988A1 (en) * 2017-04-28 2018-11-09 Valeo Systemes Thermiques Optimized dimensioning coanda-effect double ejector tube ventilation device for motor vehicle heat exchange module
FR3065989A1 (en) * 2017-04-28 2018-11-09 Valeo Systemes Thermiques Coanda effect tube ventilation device with optimized ejection slot size for motor vehicle heat exchange module
FR3067401A1 (en) * 2017-06-12 2018-12-14 Valeo Systemes Thermiques Ventilation system for motor vehicle
FR3067294A1 (en) * 2017-06-12 2018-12-14 Valeo Systemes Thermiques Calender for motor vehicle
FR3069618A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Ventilation device for motor vehicle
FR3069617A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Ventilation device for motor vehicle
FR3069623A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Method for manufacturing a ventilation device for a motor vehicle
WO2019063946A1 (en) 2017-09-29 2019-04-04 Valeo Systemes Thermiques Ventilation device for a motor vehicle heat exchange module with air guides for guiding the air flow passing through the air manifolds
FR3071876A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Ventilation device for a heat exchange module of a motor vehicle
FR3071875A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Tube ventilation device for automotive vehicle heat exchange module with air flow deflectors in air collectors
FR3071873A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Tube ventilation device for a motor vehicle heat exchange module with air flow distribution partitions in air collectors
FR3073563A1 (en) * 2017-09-29 2019-05-17 Valeo Systemes Thermiques Ventilation device for motor vehicle
WO2018197816A3 (en) * 2017-04-28 2019-06-20 Valeo Systemes Thermiques Heat exchange module comprising aerodynamic and heat-transfer tubes
WO2019122767A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device intended to generate a flow of air through a motor vehicle heat exchanger with oriented ducts
WO2019122769A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device with tubes provided with oriented air flow guide means for a motor vehicle heat exchange module
WO2019122766A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device having two rows of movable tubes for a motor vehicle heat exchange module

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JPS56167897A (en) 1980-05-28 1981-12-23 Toshiba Corp Fan
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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018167443A1 (en) 2017-03-17 2018-09-20 Valeo Systemes Thermiques Ventilation device intended to generate a flow of air through a motor vehicle heat exchanger
WO2018197816A3 (en) * 2017-04-28 2019-06-20 Valeo Systemes Thermiques Heat exchange module comprising aerodynamic and heat-transfer tubes
WO2018197819A1 (en) 2017-04-28 2018-11-01 Valeo Systemes Thermiques Ventilation device with optimised-pitch tubes for a motor vehicle heat exchange module
FR3065675A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Remote heat exchange module optimized between aerodynamic conduits and heat pipes
FR3065676A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Heat exchange module with aerodynamic tubes and caloporators coming from material
FR3065753A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Optimized coanda effect coffee tube ventilation device for automotive vehicle heat exchange module
FR3065748A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Coanda effect tube ventilation device for automotive vehicle heat exchange module
FR3065752A1 (en) * 2017-04-28 2018-11-02 Valeo Systemes Thermiques Double ejector coanda effect tube ventilation device for automotive vehicle heat exchange module
FR3065988A1 (en) * 2017-04-28 2018-11-09 Valeo Systemes Thermiques Optimized dimensioning coanda-effect double ejector tube ventilation device for motor vehicle heat exchange module
FR3065989A1 (en) * 2017-04-28 2018-11-09 Valeo Systemes Thermiques Coanda effect tube ventilation device with optimized ejection slot size for motor vehicle heat exchange module
WO2018197818A1 (en) 2017-04-28 2018-11-01 Valeo Systemes Thermiques Ventilation device with tubes provided with air flow guide means for a motor vehicle heat exchange module
FR3067294A1 (en) * 2017-06-12 2018-12-14 Valeo Systemes Thermiques Calender for motor vehicle
FR3067401A1 (en) * 2017-06-12 2018-12-14 Valeo Systemes Thermiques Ventilation system for motor vehicle
FR3069617A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Ventilation device for motor vehicle
FR3069623A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Method for manufacturing a ventilation device for a motor vehicle
FR3069618A1 (en) * 2017-07-31 2019-02-01 Valeo Systemes Thermiques Ventilation device for motor vehicle
FR3071876A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Ventilation device for a heat exchange module of a motor vehicle
FR3071875A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Tube ventilation device for automotive vehicle heat exchange module with air flow deflectors in air collectors
FR3071873A1 (en) * 2017-09-29 2019-04-05 Valeo Systemes Thermiques Tube ventilation device for a motor vehicle heat exchange module with air flow distribution partitions in air collectors
FR3073563A1 (en) * 2017-09-29 2019-05-17 Valeo Systemes Thermiques Ventilation device for motor vehicle
WO2019063946A1 (en) 2017-09-29 2019-04-04 Valeo Systemes Thermiques Ventilation device for a motor vehicle heat exchange module with air guides for guiding the air flow passing through the air manifolds
WO2019122767A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device intended to generate a flow of air through a motor vehicle heat exchanger with oriented ducts
WO2019122769A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device with tubes provided with oriented air flow guide means for a motor vehicle heat exchange module
WO2019122766A1 (en) 2017-12-20 2019-06-27 Valeo Systemes Thermiques Ventilation device having two rows of movable tubes for a motor vehicle heat exchange module

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