Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
  • F02M35/10—Air intakes; Induction systems
  • F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
  • F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
  • F02B27/0226—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means characterised by the means generating the charging effect
  • F02B27/0268—Valves
  • F02B27/0273—Flap valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
  • F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
  • F02B31/06—Movable means, e.g. butterfly valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
  • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
  • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
  • F02D9/107—Manufacturing or mounting details
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
  • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
  • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
  • F02D9/109—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps having two or more flaps
  • F02D9/1095—Rotating on a common axis, e.g. having a common shaft
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
  • F02M35/10—Air intakes; Induction systems
  • F02M35/10314—Materials for intake systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
  • F02M35/10—Air intakes; Induction systems
  • F02M35/1034—Manufacturing and assembling intake systems
  • F02M35/10354—Joining multiple sections together
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the present invention relates to a suction module of a fresh air system for an internal combustion engine, in particular in a motor vehicle.
• Such a suction module usually has a housing which is equipped with an inlet opening for fresh air and with a flange portion for attaching or connecting the housing to the internal combustion engine.
• a flange section In the flange section a plurality of outlet openings for the fresh air are provided.
• a distributor space is usually formed, from which, during operation of the internal combustion engine, the fresh air supplied via the inlet opening is distributed to the outlet openings. At least one such outlet opening is provided per combustion chamber of the internal combustion engine.
• Such a suction module can be used both in a supercharged internal combustion engine and in a non-supercharged internal combustion engine.
• each combustion chamber is assigned at least one such controllable outlet opening.
• each combustion chamber of the internal combustion engine are assigned two outlet openings, one of which is controlled in each case, that is variable with respect to its flow-through cross-section, while the other is uncontrolled, so is permanently fully open.
• the fresh air supply can be optimized depending on the current operating state of the internal combustion engine.
• Such a control device can be equipped with a control shaft which has at least one control flap arranged on the control shaft for the respective outlet opening.
• the respective control flap can thus be the respective outlet opening in terms control of their flow-through cross-section.
• the respective outlet opening can be opened or closed with the aid of the associated control flap.
• any intermediate positions are conceivable. Depending on the function of the control flap, this can also be referred to as tumble flap or swirl flap.
• the present invention is not limited to suction modules having controllable discharge ports but relates to all suction modules having or containing controllable orifices. This also affects suction modules which have bypass openings in their interior, which can be opened and closed to switch intake manifold lengths. For this purpose, such a control device for controlling the flow-through cross sections of these bypass openings are used.
• a suction module for a fresh air system of an internal combustion engine which is equipped with a housing having an inlet opening for fresh air and a flange portion with a plurality of outlet openings for fresh air.
• the known suction module has switchable suction tube lengths whose effective length is switched by opening and closing of bypass openings.
• the suction module is also equipped with a control device for controlling a flow-through cross section of these bypass openings.
• the control device has a control shaft and a plurality of non-rotatably mounted on the control shaft control flaps for the bypass openings.
• the control shaft is rotatably mounted on the housing about a rotation axis by means of at least one bearing bracket.
• the housing has at least one bearing receptacle for receiving the respective bearing bracket, which has an insertion opening.
• the respective bearing bracket is inserted in a direction perpendicular to the axis of rotation insertion direction through the respective insertion opening into the associated bearing receptacle.
• the respective bearing bracket has two bearing parts, namely a first bearing part and a second bearing part.
• the two bearing parts each have an inner surface, which face each other with respect to a direction perpendicular to the axis of rotation and perpendicular to the insertion direction transverse direction, which extend perpendicular to the transverse direction and which lie flat against each other.
• the bearing parts each have a storage area.
• the two bearing areas are designed such that in each case a linear and radially biased contact with the control shaft results at a plurality of points distributed in the circumferential direction.
• the present invention is concerned with the problem of providing for a suction module of the aforementioned type an improved embodiment which characterized in particular by a reduced production cost. Furthermore, improved storage of the control shaft and / or increased reliability of the control device are desired.
• the present invention relates to two basic aspects which are independent of each other, that is, can be used alternatively, but which can preferably also be combined with one another.
• the one aspect including its embodiments, can be combined with the other aspect and its embodiments as desired.
• the present invention is based on the general idea to provide for storage of the control shaft at least one bearing bracket, which represents a separate component with respect to the housing and with respect to the control shaft and in which the control shaft is rotatably mounted about an axis of rotation concentric with the control shaft.
• the housing has a bearing receptacle for receiving the bearing bracket for the respective bearing bracket.
• the bearing receptacle is open at the connection side of the flange portion, so that the bearing bracket can be inserted into the respective bearing receptacle by means of an insertion opening provided on the connection side.
• the respective bearing bracket is inserted in an insertion direction through the respective insertion opening into the associated bearing receptacle, wherein this insertion direction is oriented substantially perpendicular to the axis of rotation.
• the control shaft may comprise a continuous, one-piece shaft body, which may be e.g. is formed by a metallic rod to which the control flaps can be molded from plastic. It is also conceivable to provide a multi-part shaft body for the control shaft, which is assembled from several rod-shaped sections. The individual shaft body sections may e.g. be attached by molded control flaps together.
• the respective bearing bracket is equipped with at least two position blocks, which cooperate with complementary, formed in the associated bearing seat guide contours for aligning the bearing bracket when the bearing bracket in the bearing receptacle is used.
• This makes it possible to realize an optimal alignment of the bearing on the control shaft.
• a particularly low-friction bearing for the control shaft and thus a relatively high reliability for the control shaft can be realized.
• the respective bearing bracket on its outer side with two outer surfaces facing away from each other with respect to a transverse direction which is substantially perpendicular to the axis of rotation and substantially perpendicular to the insertion direction and the respective at least one position block projecting therefrom exhibit.
• the respective bearing receiver then has on its inner side for the respective position block a complementary guide contour for aligning the Bearing bracket in a direction parallel to the axis of rotation extending longitudinal direction and in the transverse direction.
• the respective position block is expediently formed integrally on the bearing bracket, that is to say made of the same material.
• the respective position block may have two longitudinal longitudinal positioning surfaces facing away from each other with respect to the longitudinal direction, which extend parallel to one another and perpendicular to the longitudinal direction.
• the associated bearing receptacle expediently has on its inside for the respective position block two longitudinal longitudinal guide surfaces facing each other with respect to the longitudinal direction, which extend parallel to each other and perpendicular to the longitudinal direction and on each of which one of the longitudinal positioning surfaces of the respective position block bears flatly.
• the respective position block may have a flat Querpositionier Structure extending perpendicular to the transverse direction.
• the associated bearing receptacle can then expediently have on its inside for the respective position block a planar transverse guide surface which extends perpendicular to the transverse direction and against which the transverse positioning surface of the respective position block lies flat.
• This measure results in an optimized alignment of the respective bearing bracket with respect to the transverse direction.
• the axis of rotation defined by the respective bearing bracket is centered by the transverse positioning surfaces which cooperate with the transverse guide surfaces.
• the respective bearing bracket may have on each of its two outer surfaces at least two such position blocks, which are spaced apart in the insertion direction. This results in a particularly efficient alignment of the bearing bracket within the respective bearing receptacle.
• a further improvement results according to a development in which at least two such position blocks are arranged in alignment with one another in the insertion direction on the respective outer surface. This simplifies the design of the associated guide contour within the bearing receptacle.
• the position block preceding in the insertion direction is smaller than the position block following in the insertion direction.
• the position blocks interact separately with the associated guide contours, which improves a reliable orientation of the bearing bracket.
• a distance of the longitudinal positioning surfaces measured parallel to the longitudinal direction is smaller than in the following, larger-dimensioned position block.
• a distance, measured parallel to the transverse direction, of the transverse positioning surface from the respective outer side of the bearing console in the case of the preceding, smaller-dimensioned position block is smaller than in the following, larger-dimensioned position block.
• the one position block in the insertion direction between the control shaft and the other positives be arranged onsblock.
• the control shaft can be inserted comparatively deep into the flange section with the aid of the respective bearing bracket.
• larger control flaps can be used in particular.
• control shaft with respect to the insertion direction between the two position blocks, whereby a particularly secure alignment of the control shaft is possible.
• the respective bearing console may each have at least two position blocks spaced apart from each other in the longitudinal direction on both outer surfaces. While the bearing bracket can be constructed comparatively small or compact overall in only one position block in the longitudinal direction, the provision of at least two position blocks spaced in the longitudinal direction enables a comparatively wide or large bearing bracket with respect to the longitudinal direction. The larger the bearing bracket builds in the longitudinal direction, the more efficient the alignment of the bearing shaft. Furthermore, larger bearing forces can be supported in a wide bearing bracket. Suitably, the two position blocks may be arranged in alignment with one another on the respective outer surface in the longitudinal direction.
• At least one such position block may have on each outer surface a preceding in the insertion flat stop surface, which extends perpendicular to the insertion and the flat abuts a flat counter-abutment surface which is formed on the inner contour of the respective bearing mount.
• the underlying problem can also be solved by dividing at least one such bearing bracket into at least two bearing parts.
• the respective bearing bracket thus has a first bearing part and a second bearing part.
• the bearing bracket only two bearing parts, so that it is designed in two parts.
• the at least two bearing parts of the split bearing bracket can thereby form separate components.
• they can also be movably connected to each other, for example via a film hinge.
• the bearing parts of the split bearing bracket can be made in one piece in a common injection molding tool, that is, connected in the same material. It is important that the first bearing part is relatively movable relative to the second bearing part at least for the assembly of the bearing bracket.
• the invention is based on the general idea of supporting the two bearing parts flat on planar positioning surfaces, whereby a predetermined alignment of the two bearing parts relative to each other can be realized comparatively accurately.
• the control shaft can be stored reliably rotatable within the bearing bracket.
• an impermissibly high radial compression of the control shaft in the bearing bracket can be avoided, which can easily be the case for non-optimally oriented bearing parts.
• the second aspect leads to a simplified structure and in particular to an improved shaft bearing with increased reliability.
• the second aspect proposes to equip the first bearing part with a first bearing section defining a first peripheral section the control shaft lies flat against it, while the second bearing part has a second bearing section opposite the first bearing section, which defines a second circumferential section opposite the first peripheral section, against which the control shaft bears flatly.
• the two bearing parts each have an inner surface which, with respect to the transverse direction already mentioned above on the first aspect, which is substantially perpendicular to the axis of rotation and substantially perpendicular to the insertion direction, face each other and which each have at least one planar positioning surface, which in the Extend substantially perpendicular to the transverse direction.
• at least one such positioning surface of the first bearing part lies flat against at least one such positioning surface of the second bearing part.
• the respective positioning surface of the respective inner surface may be raised, so be spaced apart in the transverse direction. In this way, it can be achieved that the two bearing parts in the area of the mutually facing inner surfaces touch exclusively on the positioning surfaces. This does not exclude that the two bearing parts are connected to each other, for example via a film hinge and / or in principle can also abut each other in the region of the bearing sections.
• an embodiment in which the two bearing parts outside the bearing sections are in contact with each other in the region of the inner surfaces exclusively via the positioning surfaces in the transverse direction is particularly advantageous.
• a gap is formed in the transverse direction between the inner surfaces outside the positioning surfaces.
• a gap is formed in the insertion direction on both sides of the adjoining positioning in the transverse direction between the inner surfaces.
• the respective gap completely penetrates the respective bearing bracket in a longitudinal direction running parallel to the axis of rotation.
• disturbing interactions in the transverse direction are excluded by touching the bearing parts outside of the positioning.
• the two bearing parts do not touch one another on a side of the control shaft facing away from the positioning surfaces.
• a disturbing interaction is excluded in this area.
• the two bearing parts each have a separating edge, in particular a tear-off edge, on the side of the control shaft facing away from the positioning surfaces.
• These separation edges can be formed by the residues of a compound, in particular a film hinge.
• This connection may be provided in the production of the mating bearing parts. This connection can be separated before assembly of the two bearing parts to the bearing bracket, for example by cutting or tearing. Likewise, this compound can be separated when assembling the two bearing parts to the bearing bracket.
• the film hinge tears by itself when the bearing parts are closed around the control shaft to the bearing bracket. Therefore, an embodiment is expedient in which the two bearing parts are separate components, at least when the bearing bracket is inserted into the bearing receiver. Separate bearing parts can position themselves unhindered by the positional surfaces.
• At least two such positioning surfaces are formed on the respective inner surface on the two bearing parts, which improves an optimal alignment of the two bearing parts to one another.
• the two positioning surfaces of the respective bearing part can expediently be spaced apart from one another in the insertion direction. It is also conceivable to provide the two positioning surfaces on the respective inner surface in the longitudinal direction spaced from each other. It is also conceivable that more than two, for example three or four or more such positioning surfaces are provided on the respective inner surface, wherein it can be provided in particular that at least two such positioning in the insertion direction and two such positioning in the longitudinal direction are spaced apart. Spacing in the longitudinal direction is provided when the respective bearing bracket is to be relatively large or wide in the longitudinal direction.
• the first bearing part may have on its inner surface at least one projecting in the transverse direction guide pin, while the second bearing part has on its inner surface at least one oriented in the transverse direction, complementary to the associated guide pin guide opening into which the associated guide pin inserted in the transverse direction is.
• a predetermined orientation of the two bearing parts is also achieved relative to each other.
• guide pin and guide hole with appropriate fit which is preferably a press fit, a sufficient fixation of the two bearing parts are achieved together.
• Such a guide pin may preferably be integrally formed on the respective bearing part, so be made of the same material.
• the respective guide pin can be bordered by the respective positioning, so that the respective guide pin projects within the positioning of the respective bearing part.
• the respective guide opening can be enclosed by the respective positioning surface. In this case, the guide opening is introduced within the positioning surface in the respective bearing part. This results in a particularly compact design for the bearing bracket.
• the first bearing part may comprise at least two such guide pins, which are spaced apart in the insertion direction and / or in the longitudinal direction.
• the second bearing part then has complementary to the guide pins on at least two such guide openings, which are also spaced apart in the insertion direction and / or in the longitudinal direction. This measure also leads to an improvement in the alignment of the two bearing parts to each other. Likewise, this can also realize a bearing bracket large in the longitudinal direction.
• the second bearing part has at least one guide pin which is inserted into a guide opening formed on the first bearing part.
• the guide pins are preferably formed exclusively on the first bearing part, while the guide openings are formed exclusively on the second bearing part.
• the first peripheral portion or the second peripheral portion may be greater than 180 °, so that the bearing shaft inserted into the associated bearing portion is clamped therein.
• the first bearing part formed on the first bearing portion is shaped so that the first peripheral portion is greater than 180 °.
• the larger peripheral portion extends for example over a maximum of 240 ° and may be for example about 200 °.
• a further embodiment results when a gap is provided in each case in the circumferential direction between the first bearing section and the second bearing section. As a result, alignment of the two bearing sections relative to each other can be achieved by contacting the positioning surfaces to each other.
• bearing parts do not touch in the region of the bearing sections.
• an optimal alignment of the bearing sections relative to one another is possible by the interaction of the adjoining positioning surfaces.
• This also achieves a functional separation within the bearing console, since the positioning surface align the bearing sections relative to one another, while the bearing sections cause the bearing of the control shaft.
• the bearing part with the larger bearing portion has laterally on its inner surface on a bearing portion in the circumferential direction enlarging projection.
• the bearing part with the smaller bearing section has, laterally on its inner surface, a rear section which reduces the bearing section in the circumferential direction. jump, in which the projection engages. This results in a particularly compact design.
• the two bearing parts do not touch in the region of the projection and the return. This measure also simplifies alignment of the two bearing sections relative to one another when the positioning surfaces come into contact with each other.
• the positioning abut each other in a positional plane, in which also lies the axis of rotation.
• the axis of rotation can be centered.
• the flange portion is provided on its connection side with at least one sealing groove for receiving a seal, wherein the seal in the connected to the internal combustion engine state of the housing sealingly abuts the internal combustion engine.
• at least one such bearing mount in a section of the seal groove, such that the seal groove has a groove interruption in the region of this bearing mount.
• at least one such bearing bracket in the region of the sealing groove has a groove portion which seals the sealing groove in the Completed area of the aforementioned groove interruption. In this way, the groove section formed on the respective bearing bracket can supplement the adjoining sealing groove virtually without interruption and preferably flush, so that in the mounted state the seal inserted therein can be guided without interruption.
• This measure has the advantage that, in particular, a distance in the longitudinal direction can be selected to be particularly small between adjacent outlet openings.
• the control shaft can also be used in the area of the seal by means of such a bearing receptacle.
• Another advantage of this embodiment is seen in the fact that the bearing bracket used in the bearing mount with the aid of the seal on
• the intake module can be prepared largely completely as an assembly, which simplifies their installation on the internal combustion engine.
• the compression of the seal creates a biasing force which drives the bearing bracket in the direction of insertion into the bearing seat, which also assists in secure positioning of the bearing bracket relative to the housing.
• At least one such position block may have a holding surface facing away from the control shaft, which is flush with a groove bottom of the groove portion.
• the respective position block with its holding surface forms a portion of the groove bottom of the sealing groove, which also allows a simplified assembly and improved positioning of the bearing bracket in the flange.
• the bearing bracket is designed as a plastic injection molded part.
• the usual Entformungsschrägen, for removal of the finished plastic part from the injection mold, are arranged on the not intended for positioning outer surfaces as is common practice.
• the proportion of the positioning surfaces is less than 20%, in particular less than 10% of the total component surface. Due to the small proportion of the total surface still a problem-free removal of the sprayed bearing brackets from the tool is possible.
• the housing has at least one inlet opening for fresh air and a flange section which has the controllable openings which form outlet openings for fresh air there.
• the bearing receptacles are formed on a connection side of the flange section provided for connecting the housing to the internal combustion engine.
• Fig. 1 is a greatly simplified schematic diagram of a schematic
• Fig. 2 is a bottom view of the suction module
• 3 to 5 are each an isometric view of a bearing bracket in an unfolded state, in various embodiments,
• FIGS. 6 and 7 are each an isometric view of the bearing bracket in a folded state, in the embodiments shown in Figs. 4 and 5,
• Fig. 8 shows a cross section of the suction module in the region of a bearing bracket, wherein a housing of the suction module is shown in section, while the bearing bracket is shown in a side view.
• an internal combustion engine 1 comprises an engine block 2, which has a plurality of cylinders 3, in each of which a combustion chamber 4 of the internal combustion engine 1 is contained.
• a piston not shown here, is arranged in a stroke-adjustable manner in each cylinder 3.
• About a fresh air system 5 is the combustion chambers. 4 Fresh air supplied.
• a corresponding fresh air flow 6 is indicated by arrows.
• the fresh air system 5 is connected via a suction module 7 to the internal combustion engine 1 or to the engine block 2 or attached thereto.
• an exhaust system 8 is provided, can be removed via the combustion exhaust gases from the combustion chambers 4.
• a corresponding exhaust stream 9 is indicated by arrows.
• the internal combustion engine 1 is a supercharged internal combustion engine 1, since it is equipped with a charging device 10, which in the example is an exhaust gas turbocharger, which can also be referred to below as 10.
• the exhaust gas turbocharger 10 has in a conventional manner a compressor 1 1, which is installed in the fresh air system 5, and a turbine 12, which is installed in the exhaust system 8.
• Compressor 1 1 and turbine 12 are drivingly connected to each other, for example, by a common drive shaft 13.
• the internal combustion engine 1 can also be designed as a non-supercharged internal combustion engine 1, ie as a naturally aspirated engine.
• the suction module 7 has a housing 14 which encloses a distributor space 15.
• the housing 2 has an inlet opening 16 and a plurality of outlet openings 17. Through the inlet opening 16, the fresh air stream 6 can enter the distributor chamber 15. Through the outlet openings 17, the fresh air stream 6 can emerge from the distributor chamber 15 and flow into the respective combustion chamber 4 via corresponding fresh air channels 18 formed in the engine block 2. Gas exchange valves for controlling gas exchange processes are not shown here.
• the housing 14 has a flange portion 19 with which the housing 14 or the suction module 7 is fastened to the engine block 2 or to the internal combustion engine. ne 1 can be connected.
• the flange portion 19 is integrally formed on the housing 14, so made of the same material therewith.
• the suction module 7 is also equipped with a control device 20, by means of which at least one of the outlet openings 17 of the flow-through cross-section can be controlled. It is clear that in another embodiment, the flow-through cross section of any other opening can be controlled by means of the control device 20, so that the following description is also readable on a suction module 7 with other controllable openings.
• each cylinder 3 or each combustion chamber 4 is assigned two outlet openings 17, wherein only one of these two outlet openings 17 can be controlled with the aid of the control device 20, while the respective other outlet opening 17 is uncontrolled, ie permanently open ,
• the uncontrolled Auslasso réelleen 17 are also designated in Fig. 2 with 17a.
• the outlet openings 17 that can be controlled or controlled with the aid of the control device 20 are also designated 17 b in FIG. 2.
• the control device 20 has at least one control shaft 21 which carries a control flap 22 for at least one controlled outlet opening 17b, which is non-rotatably arranged on the control shaft 21. To rotate the control shaft 21, a corresponding actuator 68 is provided.
• FIG. 1 To rotate the control shaft 21, a corresponding actuator 68 is provided.
• a single, common control shaft 21 is provided for all controllable outlet openings 17b, each of which carries a control flap 22 for all controllable outlet openings 17b.
• the control shaft 21 is suitably made of a metal
• the control flaps 22 are preferably made of a plastic, wherein the control flaps 22 may be directly molded onto the control shaft 21.
• the control shaft 21 is rotatably supported by means of a plurality of bearing brackets 23 on the housing 14 about a rotation axis 24.
• the control shaft 21 is expediently rectilinear, so that the axis of rotation 24 extends concentrically with the control shaft 21.
• FIG. 8 shows a simplified cross-section of the suction module 7 through the housing 14 in the region of the flange portion 19 perpendicular to the axis of rotation 24, in the area of such a bearing bracket 23, wherein the bearing bracket 23 itself is not shown cut, but in a side view, whose viewing direction is parallel to the axis of rotation 24.
• the housing 14 in the region of the flange portion 19 for each bearing bracket 23 an associated bearing mount 25.
• the respective bearing mount 25 has an insertion opening 27 on a connection side 26 of the flange section 19, so that the respective bearing mount 25 is open on the connection side 26.
• connection side 26 serves to connect the housing 14 to the internal combustion engine 1 or to the engine block 2 thereof, wherein the connection side 26 faces the engine block 2 or is arranged on a side of the connection flange 19 facing away from the housing 14.
• the respective bearing bracket 23 is inserted through the insertion opening 27 into the bearing receptacle 25 in an insertion direction 28 indicated by an arrow.
• the insertion direction 28 is oriented perpendicular to the axis of rotation 24.
• the respective bearing bracket 23 has on its outer side two outer surfaces 29 which are remote from one another with respect to a transverse direction 30 indicated in FIGS. 6 to 8 by a double arrow.
• the transverse direction 30 is perpendicular to the axis of rotation 24 and perpendicular to the insertion direction 28.
• the bearing bracket 23 each have at least one of the respective outer surface 29 protruding position block 31.
• the bearing assembly 25 would have on its inner side 32 a guide contour 33 for aligning the bearing bracket 23 with respect to the transverse direction 30 and with respect to a longitudinal direction 34, which is indicated in FIGS. 6 and 7 by a double arrow and which extends parallel to the axis of rotation 24.
• the respective position block 31 has two with respect to the longitudinal direction 34 facing away from each other planar Lekspositionier lake 35, which extend parallel to each other and perpendicular to the longitudinal direction 34.
• Leksositionier vom 35 are indicated in Fig. 7 with broken reference lines.
• the bearing receptacle 25 or the respective guide contour 33 has on the inner side 32 for the respective position block 31 two planar longitudinal guide surfaces 36, which can be seen only in FIG.
• the longitudinal guide surfaces 36 are facing each other with respect to the longitudinal direction 34 and extend parallel to one another and perpendicular to the longitudinal direction 34.
• the longitudinal positioning surfaces 35 of the respective position block 31 lie flat against the respective longitudinal guide surface 36.
• the respective position block 31 here is equipped with a plane Querpositionier Chemistry 37 which extends perpendicular to the transverse direction 30 and is remote with respect to the transverse direction 30 of the rest of the bearing bracket 23.
• a plane Querpositionier Chemistry 37 which extends perpendicular to the transverse direction 30 and is remote with respect to the transverse direction 30 of the rest of the bearing bracket 23.
• the bearing seat 25 on its inner side 32 and on its guide contour 33 for the respective position block 31 on a flat transverse guide surface 38 which extends perpendicular to the transverse direction 30 and at which the respective Querpositionier Chemistry 37 of the respective position block 31 is applied flat
• the aforementioned longitudinal positioning surfaces 35 with the longitudinal guide surfaces 36 effect an alignment of the bearing bracket 23 with respect to the longitudinal direction 34
• the transverse positioning surfaces 37 in conjunction with the transverse guide surfaces 38 indicate an orientation of the bearing bracket 23 with respect to the transverse direction 30.
• the respective bearing bracket 23 has on each of its two outer surfaces 29 at least two such position blocks 31, which are spaced apart in the insertion direction 28. Accordingly, in order to distinguish between the two position blocks 31, the position block 31 preceding the bearing receptacle 25 during insertion of the bearing bracket 23 can be referred to below as the preceding or preceding position block 31a, while the position block 31 following the insertion is also referred to below as the subsequent position block 31b can.
• the smaller preceding position block 31 a is dimensioned smaller both in the longitudinal direction 34 and in the transverse direction 30 than the larger, subsequent position block 31 b.
• a longitudinal distance 39 which the two longitudinal positioning surfaces 35 of the respective position block 31 have from one another, is smaller in the preceding position block 31 a than in the subsequent position block 31 b.
• a transverse distance 40 measured parallel to the transverse direction 30, of the respective transverse positioning surface 37 from the associated outer surface 29, from which the respective position block 31 projects, is smaller in the preceding position block 31 a than in the subsequent position block 31 b.
• the preceding position block 31 a is arranged with respect to the insertion direction 28 between the control shaft 21 and the subsequent position block 31 b, whereby the control shaft 21 can reach a particularly large distance from the connection side 26, which corresponds to a large penetration depth. This is advantageous for the realization of relatively large control flaps 22.
• While the embodiment of the bearing bracket 23 shown in FIG. 6 has only two position blocks 31 on each outer side 29, four such position blocks 31 are provided on each outer side 29 in the embodiment shown in FIG. Thus, at least two such position blocks 31 in the longitudinal direction 34 are spaced from each other on the respective outer surface 29. Specifically, two spaced apart in the longitudinal direction 34 preceding smaller position blocks 31 a and two subsequent larger position blocks 31 b are provided.
• the bearing brackets 23 presented here that at least one of the position blocks 31, namely in each case the preceding position block 31 a, a preceding in the insertion 28 flat stop surface 41 is formed, which extends perpendicular to the insertion direction 28.
• the bearing mount 25 has on its inner side 32 for the respective position block 31, here for the respective preceding position block 31 a, a flat counter-abutment surface 42 on which the abutment surface 41 rests flat as soon as the bearing bracket 23 reaches a predetermined insertion depth in the bearing seat 25 Has.
• the respective bearing bracket 23 has two bearing parts, namely a first bearing part 43 and a second bearing part 44.
• the first bearing part 43 has a first bearing section 45 on which the control shaft 27 abuts with a first peripheral section 46.
• the second bearing part 44 has a second bearing section 47, which is opposite to the first bearing section 45 and against which the control shaft 21 abuts with a second peripheral section 48, which in turn adjoins the first peripheral section 48.
• section 46 is opposite.
• Both bearing parts 43, 44 each have laterally on the respective bearing portion 45, 47 then an inner surface 49, which face each other with respect to the transverse direction 30.
• At least one planar positioning surface 50 which extends in each case perpendicular to the transverse direction 30, is formed on the respective inner surface 49.
• the respective positioning surface 50 of the first bearing part 43 abuts flat against at least one positioning surface 50 of the second bearing part 44.
• the two bearing parts 43, 44 with respect to the transverse direction 30 are optimally aligned with each other.
• the positioning surfaces 50 of the two bearing parts 43, 44 abut one another in a positional plane 58.
• the positioning surfaces 50 are expediently arranged on the bearing parts 43, 44 such that the axis of rotation 24 defined by the bearing bracket 43 lies in the position plane 58.
• the positioning surfaces 50 are located with respect to the control shaft 21 only on one side of the bearing parts 43, 44. This page is located in Fig. 8 below the Control shaft 21. It can also be seen that the two bearing parts 43, 44 do not touch each other on a side of the control shaft 21 facing away from the positioning surfaces 50, that is to say in FIG. 8 above the control shaft 21. Thus, the radial gap 54 described above continues until the end of the bearing bracket 23 preceding the insertion direction 28. There, at this preceding end is also recognizable that the two bearing parts 43, 44 on the side facing away from the positioning surfaces 50 side of the control shaft 21 each have a separation or tear-off edge 70. Accordingly, at least when inserted into the bearing holder 25 bearing bracket 23, the two bearing parts 43, 44 separate components.
• the first bearing part 43 has on its inner surface 49 at least one guide pin 51 projecting in the transverse direction 30. These guide pins 51 are not visible in the folded state of Fig. 6 to 8.
• the respective second bearing part 43 has, according to FIGS. 3 to 5, on its inner surface 49 at least one guide opening 52 oriented in the transverse direction 30, which is shaped complementarily to the associated guide pin 51. In the folded state of FIGS. 6 to 8, the respective guide pin 51 is inserted into the associated guide opening 52 in the transverse direction 30. The guide openings 52 are not visible in Figs. 6 to 8.
• the positioning of the guide pins 51 on the respective inner surface 49 expediently takes place deliberately in such a way that the respective guide pin 51 is bordered by the respective positioning surface 50 and in particular centered thereon. Accordingly, the positioning openings 52 are bordered on the second bearing part 44 of the respective positioning surface 50 and in particular centered on it.
• the respective positioning surface 50 is raised from the associated inner surface 49, that is to say it is spaced apart in the transverse direction 30.
• at least two such positioning surfaces 50 are formed on both bearing parts 43, 44 on the respective inner surface 49, which can be arranged spaced apart in the insertion direction 28 and / or in the longitudinal direction 34.
• FIG. 3 shows an embodiment in which the respective bearing part 43, 44 has exactly two positioning surfaces 50, which are spaced apart in the longitudinal direction 34 and are also aligned with respect to the longitudinal direction 34.
• only two positioning surfaces 50 are likewise provided on the two bearing parts 43, 44, but in this case they are spaced apart in the insertion direction 28 and are also aligned with one another in the insertion direction 28.
• Fig. 5 shows an example in which the respective bearing part 43, 44 each having four positioning surfaces 50, wherein each two in the insertion direction 28 and two each in the longitudinal direction 34 spaced from each other and are aligned.
• exactly two guide pins 51 and exactly two guide openings 52 are respectively provided.
• the bearing pedestal 23 in each case is the first peripheral section 46 defined by the first bearing section 45 of the first bearing part 43 greater than 180 ° and in the example is approximately 225 °.
• the second peripheral section 48 defined by the second bearing section 47 of the second bearing part 44 is smaller than 180 ° and, in the example shown, is approximately 120 °.
• the control shaft 21 can be clipped on the first bearing section 45, while the second bearing section 47 secures the control shaft 21 in the first bearing section 45 in the folded state of the bearing bracket 23.
• the sum of the first peripheral portion 46 and the second peripheral portion 48 is smaller than 360 °.
• a projection 55 is formed in the region of the first bearing portion 45, which enlarges the first bearing portion 45 in the circumferential direction 53, so that the projection 55 covers or defines a part of the first peripheral portion 46.
• the second bearing part 44 has in the region of the second bearing portion 47 a recess 56, that is, a recess or recess.
• the recess 56 leads to a reduction of the second peripheral portion 48. Further, the projection 55 engages in this recess 56 a.
• the positioning of the projection 55 in the recess 56 is designed so that the two bearing parts 43, 44 also in the region of the projection 55 and the recess 56 do not touch. Rather, a gap 57 between projection 55 and recess 56 is also formed there.
• the flange portion 19 is provided on its side facing the viewer side 26 with a seal 59, with the help of the
• Flange portion 19 and the housing 14 is sealed in the mounted state relative to the engine block 2 in order to prevent leakage of the combustion chambers 4 supplied fresh air into the environment.
• a complementary groove 59 is formed in the connection side 26 of the flange portion 19, a sealing groove 60 is incorporated, of which also in Fig. 8, a section can be seen.
• at least one such bearing mount 25 is arranged in a section of the seal groove 60, such that the seal groove 60 has a groove interruption 61 in the region of this bearing mount 25.
• the bearing bracket 23 inserted into this bearing receptacle 25 is now designed such that in the region of the sealing groove 60 it has a groove section 62 which seals the sealing groove 60 in the region of the groove bottom. refraction 61 completed.
• the groove section 62 provided on the bearing bracket 23 completes the sealing groove 60 completely in the region of the groove interruption 61, so that the seal 59 can abut seamlessly on a groove base 63 of the sealing groove 60.
• the two subsequent position blocks 31 b each have a remote from the control shaft 21 retaining surface 64, which connect flush to the groove bottom 53 of the groove portion 60 and thereby form a portion of the groove bottom 63 of the sealing groove 60 itself , As a result, it is basically possible to produce a continuous contact with the seal 59 in the region of the groove interruption 61 as well.
• the seal 59 has, according to FIG. 2, a circulation 65, which is led around all outlet openings 17 and around all bearing receptacles 25, thus enclosing or enclosing them.
• the seal 59 on a plurality of webs 66 which are each passed through a groove interruption 61, that is, through a bearing receptacle 25 and there are in contact with the associated bearing bracket 23.
• These webs 66 are used in the pre-assembly of the suction module 7 to secure the bearing brackets used in the bearing receptacles 23 23 on the flange 19.
• the webs 66 cause a bias of the bearing brackets 23 in the insertion direction 28, whereby the bearing brackets 23, in particular with their stop surfaces 41 biased come to the counter-stop surfaces 42 to the plant.
• the two bearing parts 43, 44 can preferably be produced in a common injection molding tool.
• the two bearing parts 43, 44 can also be made in one piece, but movably connected to each other.
• a film hinge 67 may be formed at the transition between the two bearing parts 43, 44 for this purpose.
• the film hinge 67 may be configured to allow pivotal movement of the two bearing members 43, 44 relative to one another about a pivot axis parallel to the axis of rotation 24 defined by the film hinge 67 to form the respective bearing bracket 23 Condition of the bearing bracket 23 to produce.
• the required bearing brackets 23 can thus be clipped onto the control shaft 21 in the unfolded state shown in FIGS. 3 to 5 with their first bearing parts 43 at the corresponding positions.
• the bearing brackets 23 can be transferred into the folded state shown in FIGS. 6 to 8, in which the respective second bearing part 44 is pivoted about the film hinge 67 or about its pivot axis until the position surfaces 50 come into contact with each other.
• the guide pins 51 are inserted into the guide openings 52. It can be provided to dimension the film hinge 67 so that it is destroyed during assembly of the two bearing parts 43, 44 to the bearing bracket 23 (folded state), so that the two bearing parts 43, 44 after assembly or after folding the bearing bracket 23 are no longer connected to each other via the film hinge 67.
• 6 to 8 show such embodiments in which after folding the bearing bracket 23, the film hinge 67 is destroyed or no longer exists.
• the film hinge 67 ruptures when the bearing members 43, 44 for assembling the bearing bracket 23 are directly positioned against each other on the control shaft 21. In this case, then the above-mentioned and visible in Figs. 6 to 8 separating or Abrisskanten 70 arise.
• the film hinge 67 can also be dimensioned so that it is not destroyed by the folding of the bearing bracket 23, but creates a resilient connection between the two bearing parts 43, 44, so that the bearing portions 45, 47 when folding the bearing parts 43, 44 are adjustable relative to each other and by the film hinge 67, an alignment of the two bearing portions 45, 47 relative to each other is not hindered.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Manufacturing & Machinery (AREA)
• Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
• Mounting Of Bearings Or Others (AREA)

Applications Claiming Priority (2)

Publications (1)

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• 2015
  • 2015-03-13 DE DE102015204605.2A patent/DE102015204605B4/de active Active
• 2016
  • 2016-03-07 JP JP2017542091A patent/JP6317530B2/ja not_active Expired - Fee Related
  • 2016-03-07 US US15/557,799 patent/US10107238B2/en active Active
  • 2016-03-07 KR KR1020177025596A patent/KR101880009B1/ko active IP Right Grant
  • 2016-03-07 WO PCT/EP2016/054782 patent/WO2016146417A1/de active Application Filing
  • 2016-03-07 EP EP16709324.4A patent/EP3268591A1/de not_active Withdrawn
  • 2016-03-07 CN CN201680014594.9A patent/CN107407189B/zh active Active

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