WO2022048705A1 - Dispositif de soupape d'une portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement et portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement - Google Patents

Dispositif de soupape d'une portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement et portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement Download PDF

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Publication number
WO2022048705A1
WO2022048705A1 PCT/DE2021/100699 DE2021100699W WO2022048705A1 WO 2022048705 A1 WO2022048705 A1 WO 2022048705A1 DE 2021100699 W DE2021100699 W DE 2021100699W WO 2022048705 A1 WO2022048705 A1 WO 2022048705A1
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WO
WIPO (PCT)
Prior art keywords
valve
exhaust gas
arm
lever arm
valve body
Prior art date
Application number
PCT/DE2021/100699
Other languages
German (de)
English (en)
Inventor
Dietmar FILSINGER
Carsten Weinhold
Stephan WENIGER
Viktor Dick
Original Assignee
Ihi Charging Systems International Gmbh
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
Priority claimed from DE102020123178.4A external-priority patent/DE102020123178A1/de
Priority claimed from DE102020123177.6A external-priority patent/DE102020123177A1/de
Priority claimed from DE102020123179.2A external-priority patent/DE102020123179A1/de
Application filed by Ihi Charging Systems International Gmbh filed Critical Ihi Charging Systems International Gmbh
Publication of WO2022048705A1 publication Critical patent/WO2022048705A1/fr

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Classifications

    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
    • F16K1/2007—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member specially adapted operating means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
    • F16K1/2014—Shaping of the valve member
    • 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 invention relates to a valve device of an exhaust gas routing section of an exhaust gas turbocharger of the type indicated in the preamble of patent claim 1.
  • the invention also relates to an exhaust gas routing section of an exhaust gas turbocharger according to the preamble of patent claim 16.
  • Valve devices for exhaust gas routing sections are known.
  • exhaust gas guide sections have a bypass channel for the controllable inflow of a turbine wheel rotatably accommodated in the exhaust gas guide section, which bypass channel is opened or closed with the aid of a valve device.
  • the valve devices serve to open and close a flow opening formed between the two flows.
  • the valve device can be designed to open and close the flow opening and to open and close the bypass channel. In other words, this means that a single valve device, comprising a single valve body, is designed to regulate the inflow onto the turbine wheel.
  • Patent specification DE 10 2012 015 536 B4 discloses a valve device for an exhaust gas routing section of an exhaust gas turbocharger, the exhaust gas routing section having a single-flow design and having a bypass channel to bypass a turbine wheel rotatably accommodated in the exhaust gas routing section.
  • a valve disk of the valve device In a closed position, in which a valve opening formed in the bypass channel is closed with the aid of the valve disk, a valve disk of the valve device has a longitudinal center axis of the valve disk at a distance from a longitudinal center axis of the valve opening.
  • the published application WO 2017/108160 A1 discloses a valve device of an exhaust gas routing section of an exhaust gas turbocharger, the exhaust gas routing section having two flows and a bypass channel.
  • the valve device is used to open and close the bypass duct and to open and close a flow connection cross section formed in the exhaust gas routing section.
  • the object of the present invention is to provide an improved valve device of an exhaust gas routing section of an exhaust gas turbocharger.
  • the further object is to specify an improved exhaust-gas routing section of an exhaust-gas turbocharger.
  • this object is achieved with a valve device of an exhaust gas routing section of an exhaust gas turbocharger with the features of claim 1 .
  • the further object is achieved according to the invention with an exhaust gas routing section of an exhaust gas turbocharger with the features of claim 16.
  • a valve device of an exhaust gas routing section of an exhaust gas turbocharger has a valve system comprising a valve body and a valve arm.
  • the valve body is arranged on a valve lever arm of the valve device with the aid of the valve arm fastened to the valve body, the valve lever arm being movable with the aid of a movement device of the valve device.
  • the valve body has a projection facing away from the valve lever arm. At least one movement gap is formed between the valve system and the valve lever arm.
  • the valve body has a valve longitudinal axis and the valve arm has an arm longitudinal axis.
  • the valve system and/or the valve lever arm are designed for complete or at least partial compensation of exhaust gas forces acting on the valve system and/or on the valve lever arm.
  • valve device can be implemented in a simple manner by offsetting the valve arm.
  • this means that the valve arm is not accommodated centrally on the valve body, viewed in a section along the longitudinal axis of the valve, but rather the valve arm is arranged at a radial distance from the longitudinal axis of the valve.
  • An asymmetrical shape is also achieved by arranging indentations or protuberances on the valve body or on the valve arm or on the valve lever arm.
  • FIG. 1 is a perspective view of a section through a valve device of an exhaust gas routing section of an exhaust gas turbocharger according to the prior art in a first position
  • FIG. 2 shows a further valve device according to the prior art in a section in a second position with exemplary isotherms during operation of the exhaust gas turbocharger
  • FIG. 3 shows a perspective view of a valve device according to the invention in a first exemplary embodiment
  • FIG. 4 shows a perspective view of the valve device according to the invention in a second embodiment
  • FIG. 5 shows a perspective view of the valve device according to the invention in a third exemplary embodiment
  • FIG. 6 shows a perspective view of the valve device according to the invention in a fourth exemplary embodiment
  • FIG. 7 shows a perspective view of the valve device according to the invention in a fifth exemplary embodiment
  • FIG. 8 shows a perspective view of the valve device according to the invention in a sixth embodiment
  • FIG. 9 shows a sectional view of the valve device according to the invention in a seventh exemplary embodiment
  • 10 shows a sectional view of the valve device according to the invention in an eighth exemplary embodiment
  • FIG. 11 shows a sectional view of the valve device according to the invention in a ninth embodiment
  • FIG. 12 shows a sectional view of the valve device according to the invention in a tenth exemplary embodiment
  • FIG. 13 shows a sectional view of the valve device according to the invention in an eleventh exemplary embodiment
  • valve device 14 shows the valve device according to the invention in a top view in a twelfth embodiment
  • FIG. 15 shows the valve device according to the invention in a sectional illustration along a section line XV-XV. Fig. 14, and
  • FIG. 16 shows the valve device according to the invention in a sectional illustration along a section line XVI-XVI. 14
  • An exhaust gas guide section 1 of an exhaust gas turbocharger 2 that can be flowed through according to FIG. 1 according to the prior art comprises an inlet channel 3 for the entry of a fluid flow into the exhaust gas guide section 1, generally exhaust gas from an internal combustion engine 7, a first spiral channel 4 and a second spiral channel 5 downstream of the inlet channel 3 for conditioning the flow, and an outlet channel, not shown in detail, downstream of the spiral channels 4, 5, through which the exhaust gas can escape from the exhaust gas guide section 1 in a targeted manner.
  • a wheel chamber not shown in detail, is formed, in which a turbine wheel, not shown in detail, is rotatably accommodated.
  • the spiral channels 4, 5 are using a Partition T can be flown through separately from one another.
  • a through-flow opening 10 is formed in the partition T so that exhaust gas can flow from the first spiral channel 4 into the second spiral channel 5 and vice versa.
  • the exhaust gas routing section 1 is connected to an exhaust manifold 6 of the internal combustion engine 7, so that the exhaust gas of the internal combustion engine 7 can enter the spiral ducts 4, 5 via the inlet duct 3 in order to act on the turbine wheel.
  • a valve device 8 for separating and connecting the first spiral channel 4 and the second spiral channel 5 is arranged in the exhaust gas guide section 1.
  • a valve body 9 of the valve device 8 is arranged in a throughflow opening 10, with the aid of which the two spiral channels 4, 5 are designed so that a flow can flow through them.
  • the valve device 8 comprises a valve system 11 which has the valve body 9 and a valve arm 13 connecting the valve body 9 to a valve lever arm 12 of the valve device 8 .
  • a bypass channel 14 formed in the exhaust gas guide section 1, which is designed to bypass a rotatably accommodated turbine wheel of the exhaust gas turbocharger 2 (not shown in detail) in the exhaust gas guide section 1, can be opened and closed with the aid of the valve body 9.
  • the through-flow opening 10 is open and exhaust gas can flow out of the first spiral channel 4 into the second spiral channel 5 and vice versa. That is, exhaust gas from the one spiral channel 4; 5 into the other spiral channel 5; 4 can overflow via the flow opening 10.
  • a valve opening 15 of the bypass channel 14 is open.
  • a flow rate of the exhaust gas or its mass flow, which is routed via the bypass duct 14, depends on an opening position of the valve body 9 a small amount of flow can flow via the bypass channel 14 . If the valve body 9 is in a maximum opening position, the flow opening 10 and the valve opening 15 are fully open.
  • the valve body 9 is to be arranged in further positions between the first position and the maximum opening position, so that the exhaust gas flowing through the flow opening 10 and/or the valve opening 15 can be adapted to achieve the best possible efficiency of the exhaust gas turbocharger 2 in accordance with the exhaust gas quantity flowing through
  • the valve body 9 has a projection 16 which faces away from the valve lever arm 12 .
  • the valve lever arm 12 is connected to a moving device 18 for moving the valve device 8 . It is designed for pivoting about a pivot axis 20 at its end 19 of the lever arm facing away from the valve system 11 .
  • the valve body 9 of the valve device 8 like. Fig. 1 is solid, the valve body 9 of the valve device 8 like. 2 is hollow, in particular in the form of a pot.
  • the valve arm 13 extends from a base 22 formed in an interior space 21 of the valve body 9 along the longitudinal valve axis 23 of the valve body 9 in the form of a cylinder, with its longitudinal extension projecting beyond a body ring 24 of the valve body 9.
  • a longitudinal arm axis 31 of the valve arm 13 is configured coaxially with the longitudinal valve axis 23 , which forms an axis of symmetry of the valve body 9 at least in one plane of the valve body 9 .
  • the body ring 24 surrounds the valve body 9 and projects beyond it in the radial direction and has a contact surface 25 for sealing rising contact in a valve seat 26 in the exhaust gas guide section 1, which is associated with the valve opening 15.
  • the valve lever arm 12 is designed to receive the valve arm 13 in a receiving opening 27 at its end designed to face the valve arm 13 .
  • the valve lever arm 12 is designed to extend into the interior space 21 and is supported with its bottom 22 opposite end at the bottom 22 from.
  • the receiving opening 27 has a longitudinal opening axis 28 which is coaxial with the longitudinal valve axis 23 in the first position of the valve body 9 .
  • the valve arm 13 has a securing element 29 for secure mounting on the valve lever arm 12 , the valve lever arm 12 being arranged between the valve body 9 and the securing element 29 .
  • valve device 8 in particular the valve body 9 and a section of the valve lever arm 12 facing the valve body 9, are permanently directly exposed to the exhaust gas flow and acted upon by it.
  • the temperature and mass of the exhaust gas flow fluctuates depending on the operation of the internal combustion engine 7.
  • a spatial expansion of the valve system 11 and the valve lever arm 12 is, however, dependent on the temperature of the exhaust gas flow and thus also fluctuates or changes with the operation of the internal combustion engine 7.
  • the movement gap 30 therefore also changes, depending on the operation of the internal combustion engine 7. In the first position of the valve device 8, this is irrelevant with regard to undesirable noise emissions, but forces of the exhaust gas flow act almost completely on the valve body 9, especially at the maximum opening position, which, for example, result in rattling due to movement of the valve system 11 relative to the valve lever arm 12.
  • An example is a temperature distribution on and in the valve system 11 and the valve lever arm 12 with the aid of isotherms 11, I2, I3, I4, I5, I6, I7, I8, I9, a first isotherm 11, a second isotherm I2, a third isotherm I3, a fourth isotherm I4, a fifth isotherm I5, a sixth isotherm I6, a seventh isotherm I7, an eighth isotherm I8 and a ninth isotherm I9 shown in Fig. 2, the first isotherm 11 being a highest temperature of the temperature distribution and the ninth isotherm I9 have a lowest temperature of the temperature distribution and the isotherms I2 to I8 in between have a descending temperature of the temperature distribution in the order of their ascending digits.
  • valve system 11 and/or the valve lever arm 12 of the valve device 8 is designed for complete or at least partial compensation of exhaust gas forces acting on the valve body 9 .
  • an asymmetrical configuration of the valve system 11 and/or the valve lever arm 12 is provided.
  • this means that the valve system 11 is positionally stable with regard to the position of the valve system 11 relative to the valve lever arm 12, in particular in the open position, in particular in the maximum open position.
  • exhaust gas forces of the exhaust gas flow which flows around the valve system 11 and act on it, are at least partially compensated, so that the movement caused by the attack of the exhaust gas forces is eliminated or at least reduced between the valve lever arm 12 and the valve system 11.
  • the valve system 11 and/or the valve lever arm 12 are designed in such a way that a particularly abrupt change in direction of the applied exhaust gas force 55 is avoided.
  • valve longitudinal axis 23 is formed at a distance from the arm longitudinal axis 31 .
  • the two longitudinal axes 23, 31 are not coaxial, but have a radial spacing 32 in the present exemplary embodiment.
  • the valve arm 13 is preferably designed in the form of a cylinder, which enables simple production with, for example, a one-piece design of the valve system 11, the distance 32 in this exemplary embodiment is in the form of a radial distance.
  • the distance 32 has a value which is greater than a maximum value of the movement gap 30.
  • a support element 33 is formed on the valve arm 13 to support the valve lever arm 12 and is produced in one piece with the valve arm 13 .
  • the valve arm 13 is completely ring-shaped.
  • the support element 33 which is provided to support the valve lever arm 12 in the direction of the longitudinal axis 31 of the arm, can have a relatively short extension in the direction of the longitudinal axis 31 of the arm in order to reduce weight.
  • the valve lever arm 12 can have an annular or segment-shaped bead (not shown in detail) opposite the support element 33 for improved mobility of the valve system 11 to avoid jamming during operation of the exhaust gas turbocharger.
  • valve device 8 is shown in a second embodiment.
  • the valve body 9 is pot-shaped and is designed to partially accommodate the valve lever arm 12 in its interior space 21 .
  • the contour 17 of the valve body 9 has an indentation 34 , the indentation 34 being formed in the area of a lateral surface 35 of the valve body 9 .
  • the valve lever arm 12 is held between two pins 36, the two pins 36 on the body ring 24 extending from the body ring 24 in a direction away from the projection 16.
  • the valve lever arm 12 is arranged between the securing element 29 and the base 22 in order to securely accommodate it.
  • the indentation 34 is designed to avoid stalls in the exhaust gas flow when the exhaust gas hits it, as a result of which the exhaust gas forces acting on the valve body 9 can be reduced. This leads to a reduction in the relative movement of the valve body 9 in relation to the valve lever arm 12. An abrupt change in the direction of the applied exhaust gas force 55 is thus avoided.
  • the indentation 34 has a fin 37 .
  • the indentation 34 has a first step 38 relative to the lateral surface 35 .
  • the valve body 9 is designed in such a way that the pressure distribution on the valve surface resulting from the inflow leads to a resultant exhaust gas force, which remains as stable as possible in its direction of force over an engine cycle and thus prevents movement on the valve body.
  • a valve device 8 according to the invention designed according to FIG. 6 has a force application point on the valve body 9 which is designed at a distance from the longitudinal valve axis 23 in the radial direction.
  • a bulge (not shown) is formed that protrudes into the interior space 21, which in a simple manner leads to a displacement of a center of gravity SK of the valve body 9 of the valve body 9, which is otherwise designed according to its contour 17 symmetrically to its longitudinal valve axis 23, in the radial direction at a distance from the longitudinal valve axis 23 .
  • a shift in the point of application of force which leads to a reduction in the movement of the valve system 11 in the open position of the valve device 8, relates to the valve arm 13 in an exemplary embodiment that is not shown in detail. This has a center of gravity which is formed at a distance from its arm longitudinal axis 31 in the radial direction.
  • the realization of the asymmetry of the valve body 9 and/or the valve arm 13 and/or their mutual arrangement in the direction of the valve longitudinal axis 23 of the valve body 9 and/or in the radial direction can be designed in many ways.
  • the indentation can be arranged closer to the valve lever arm 12 in the axial direction of the valve longitudinal axis 23 . It could also be designed to be deeper, or it could be designed to extend further over a circumference of the lateral surface 35 .
  • a further implementation of the asymmetry can be achieved with the aid of a nose 39 formed on the valve lever arm 12 .
  • the lug 39 can be designed to be more or less inclined in relation to an arm surface 40 of the valve lever arm 12. It can be rounded on its side surfaces 41 in order to avoid a flow separation of the exhaust gas flow, or it can be designed with relatively sharp edges in order to bring about turbulence.
  • the asymmetry can be formed with respect to all spatial valve axes. Influencing the pressure distribution from the exhaust gas flow on the valve surface is decisive for the execution of the asymmetry. The resulting force at the point of force application should prevent movement on the valve as far as possible.
  • FIGS. 7 and 8 variants with respect to the indentation 34 and the nose 39 are shown in a fifth or sixth exemplary embodiment of the valve device according to the invention.
  • a defined form of the valve system 11 and the valve lever arm 12 can be determined in a simulation program which is used for flow simulation or flow calculation.
  • a spring element is formed between the valve body 9 and the valve lever arm 12 and/or between the securing element 29 and the valve lever arm 12 to encompass the valve arm 13 for damping purposes.
  • the valve device 8 is, with the aid of its contour 17 and/or the spaced arrangement of the valve longitudinal axis 23 and the arm longitudinal axis 31 or the opening longitudinal axis 28 and/or the shape of the valve lever arm 12 with the formation of the lug 39 at its end facing away from the valve system 11 Avoiding points of attack of the exhaust gas flow designed to avoid moments in at least more than two quadrants, see Fig. 9, lead.
  • the valve device 8 is preferably designed in such a way that torques occur exclusively in one quadrant during operation.
  • a zero point of the associated axis system is defined by the point of application of force, which corresponds to the center of gravity SK or the center of gravity of the valve arm 13 .
  • a perfectly stable position of the valve system 11 is achieved by a torque effect, which is described by a position in the coordinate system that is fixed over the time of an engine cycle.
  • designs are also advantageous which have the smallest possible orbit in a quadrant over the time of an engine cycle or avoid zero crossings, i.e. quadrant changes of the momentarily acting torques.
  • valve system 11 of the valve device 8 is designed for complete or at least partial compensation of exhaust gas forces acting on the valve body 9 also formed in the seventh embodiment of FIG.
  • the valve lever arm 12 has a convexly curved lever arm surface 43 in an end region 42 accommodated in the interior space 21 of the valve body 9 .
  • the end area 42 is characterized by a sudden increase in a diameter D of the valve lever arm 12 for contacting the valve body 9 , with a second step 48 being formed between the end area 42 and the rest of the valve lever arm 12 .
  • Quasi-complementary in this context means that the two surfaces 43, 44 are mostly but not completely complementary.
  • a gap 46 is formed between the two surfaces 43, 44, which is formed to permit relative movement between the valve body 9 and the valve lever arm 12.
  • the gap 46 is larger than in the central region 47 of the end region 42.
  • the gap 46 is also over a small area 49 running from the second paragraph 48 towards the end 45 increases. The enlargement of the gap 46 in the end 45 and in the small area 49 allows the relative movement between the valve body 9 and the valve lever arm 12.
  • the two curved surfaces 43, 44 have a center of rotation M which, starting from a first body surface contacting the partition T in the position of the valve device 8 in which the flow opening 10 is completely closed 50 in the direction of the valve lever arm 12 at a further distance IM, characterized by the second shoulder 48 is formed.
  • a spring element 51 is provided, which is used as a damping element. It is arranged between the securing element 29 and the valve lever arm 12 .
  • valve body 9 Depending on an embodiment of the valve system 11 and depending on the position of the center of rotation M as a function of the further distance IM, there are large or small deflections of the valve body 9.
  • Figures 10 to 13 each show a sectional view of the valve device 8 according to the invention in an eighth embodiment, in a ninth embodiment, in a tenth embodiment and in an eleventh embodiment, with the center of rotation M in the direction of the valve longitudinal axis 23 between the first body surface 50 and a second body surface 52 , which is designed to face away from the first body surface 50 , is arranged approximately centrally.
  • the two body surfaces 50, 52 form the maximum extent of the valve body 9 in the direction of the valve longitudinal axis 23, and thus its axial extent lv.
  • the eighth exemplary embodiment of the valve device 8 according to the invention is designed to be lighter, with the valve lever arm 12 comprising the valve arm 13 having, on its end region 42 designed to face the base 22, the lever arm surface 43 designed for sliding on the inner surface 44, with the end region 42 being designed in the shape of a shell and the valve lever arm 12 rises from a shell interior 54 of end portion 42.
  • valve device 8 is designed in a ninth embodiment, as shown in FIG.
  • the valve arm 13 is designed to slide off the valve lever arm 12 .
  • the valve arm 13 is spherical at its end facing the base 22, wherein it has a valve arm surface 56 which is convex relative to the base 22 and which is used to slide the valve lever arm 12, which has its lever arm surface 43 complementary to the valve arm surface 56.
  • the lever arm surface 43 and the valve arm surface 56 have a radius of curvature 59 which is related to the center of rotation M. In other words, this means that the radius of curvature 59 changes depending on the further distance IM, and thus depending on the positioning of the center of rotation M, a greater or lesser degree of curvature is formed.
  • the movement gap 30 is of conical design, with a first gap radius 57 of the movement gap 30 having a value which differs from an axially spaced second gap radius 58 of the movement gap 30. In other words, this means that either the valve arm 13 or the receiving opening 27 or both are conical. Likewise, the movement gap 30 can be double-conical, thus having a waist.
  • the valve device 8 has the spring element 51 arranged obliquely in the direction of the longitudinal valve axis 23 in order to achieve improved damping.
  • a surface of the valve lever arm 12 opposite the securing element 29 is conically formed in the direction of the valve longitudinal axis 23, the securing element 29 being designed complementary to the surface of the valve lever arm 12 on its surface opposite.
  • the spring element 51 is arranged between the two surfaces.
  • the paragraph 48 of the valve lever arm 12 relevant for marking the center of rotation M is also formed in this exemplary embodiment and represents a represents the deepest point of the cone forming the conical surfaces, which point faces the bottom 22.
  • valve device 8 according to the invention is shown in a twelfth embodiment, in Fig. 14 in a plan view, in Fig. 15 in a sectional view along a section line XV-XV and in Fig. 16 in a sectional view along the Section line XVI-XVI is illustrated.
  • the spring element 51 is designed to be supported in the axial direction along its spring axis 53 on the valve arm 13 and on the valve lever arm 12 , as a result of which the valve body 9 is braced relative to the valve lever arm 12 . So that a controlled movement is possible with the help of the spring element 51, the spring element 51 is designed to support itself on the second shoulder 48 at its first spring end 60 facing the floor 22, with the spring element being able to slide off with the help of its curvature in the region of the first spring end 60 60 on the valve lever arm 12 is possible.
  • the spring element 51 extends radially outwards in the area of the body ring 24 and is convexly curved, whereby sliding contact can be produced between the body ring 24 and the spring element 51, with the aid of which the valve body 9 is supported.
  • the spring element 51 has five spring arms 61 which are arranged on a spring ring 63 of the spring element 51 which is arranged on the second spring end 62 which is designed to face away from the first spring end 60 .
  • the spring element 51 could also have a different number of spring arms 61 .
  • the spring ring 63 is designed to surround the valve arm 13 for securely holding the spring element 51, the valve arm 13 having an arm shoulder 64 which is designed to receive the spring ring 63 securely.
  • a support of the spring element 51 can be realized at its second spring end 62 on the valve arm 13 and a support of the spring ring 63 on the valve lever arm 12, whereby a Avoidance of a function-eliminating support of the second spring end 62 on the valve lever arm 12 is achieved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un dispositif de soupape d'une portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement, pourvu d'un système de soupape (11) comprenant un corps de soupape (9) et un bras de soupape (13), le corps de soupape (9) étant disposé sur un bras de levier de soupape (12) du dispositif de soupape (8) avec le bras de soupape (13) fixé au corps de soupape (9), le bras de levier de soupape (12) étant mobile à l'aide d'un dispositif de déplacement (18) du dispositif de soupape (8), et le corps de soupape (9) ayant une saillie (16) opposée au bras de levier de soupape (12). Au moins un espace de déplacement (30) est formé entre le système de soupape (11) et le bras de levier de soupape (12), le corps de soupape (9) ayant un axe longitudinal de soupape (23) et le bras de soupape (13) ayant un axe longitudinal de bras (31). Selon l'invention, afin d'empêcher ou de réduire un déplacement relatif formé au moins entre le système de soupape (11) et le bras de levier de soupape (12), le système de soupape (11) et/ou le bras de levier de soupape (12) est (sont) conçu(s) pour compenser totalement ou au moins partiellement les forces de gaz d'échappement agissant sur le système de soupape (11) et/ou sur le bras de levier de soupape (12), le corps de soupape (9) et/ou le bras de soupape (13) et/ou l'agencement de ceux-ci l'un par rapport à l'autre étant formés de manière asymétrique dans la direction d'un axe longitudinal de soupape (23) du corps de soupape (9) et/ou dans la direction radiale. L'invention concerne en outre une portion de transport de gaz d'échappement (1) d'un turbocompresseur à gaz d'échappement (2).
PCT/DE2021/100699 2020-09-04 2021-08-19 Dispositif de soupape d'une portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement et portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement WO2022048705A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102020123179.2 2020-09-04
DE102020123178.4A DE102020123178A1 (de) 2020-09-04 2020-09-04 Ventilvorrichtung eines Abgasführungsabschnitts eines Abgasturboladers und Abgasführungsabschnitt eines Abgasturboladers
DE102020123178.4 2020-09-04
DE102020123177.6 2020-09-04
DE102020123177.6A DE102020123177A1 (de) 2020-09-04 2020-09-04 Ventilvorrichtung eines Abgasführungsabschnitts eines Abgasturboladers und Abgasführungsabschnitt eines Abgasturboladers
DE102020123179.2A DE102020123179A1 (de) 2020-09-04 2020-09-04 Ventilvorrichtung eines Abgasführungsabschnitts eines Abgasturboladers und Abgasführungsabschnitt eines Abgasturboladers

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PCT/DE2021/100700 WO2022048706A1 (fr) 2020-09-04 2021-08-19 Dispositif de soupape d'une portion d'acheminement des gaz d'échappement d'un turbocompresseur de gaz d'échappement, et portion d'acheminement des gaz d'échappement d'un turbocompresseur de gaz d'échappement
PCT/DE2021/100699 WO2022048705A1 (fr) 2020-09-04 2021-08-19 Dispositif de soupape d'une portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement et portion de transport de gaz d'échappement d'un turbocompresseur à gaz d'échappement

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DE102022103039A1 (de) * 2022-02-09 2023-08-10 Ihi Charging Systems International Gmbh Regelvorrichtung eines Abgasführungsabschnitts eines Abgasturboladers

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WO2017108160A1 (fr) 2015-12-21 2017-06-29 Ihi Charging Systems International Gmbh Segment de guidage de gaz d'échappement pour un turbocompresseur et procédé de fonctionnement d'un turbocompresseur
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DE102007018617A1 (de) * 2006-04-24 2007-10-31 Borgwarner Inc., Auburn Hills Turbolader
DE102012015536B4 (de) 2012-08-06 2019-05-16 Audi Ag Abgasanlage für eine Brennkraftmaschine
US20150285133A1 (en) * 2013-04-15 2015-10-08 Ihi Corporation Variable-flow-rate valve mechanism and turbocharger
WO2017108160A1 (fr) 2015-12-21 2017-06-29 Ihi Charging Systems International Gmbh Segment de guidage de gaz d'échappement pour un turbocompresseur et procédé de fonctionnement d'un turbocompresseur
DE102016112523A1 (de) * 2016-07-07 2018-01-11 Ihi Charging Systems International Gmbh Regelvorrichtung für einen Abgasturbolader
WO2019190662A1 (fr) * 2018-03-27 2019-10-03 Borgwarner Inc. Ensemble de soupape pour turbine à spirales multiples

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* Cited by examiner, † Cited by third party
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US20240060446A1 (en) * 2022-08-16 2024-02-22 Borgwarner Inc. Valve for a dual-volute turbine

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