EP0574093A1 - Assemblage de soupape - Google Patents

Assemblage de soupape Download PDF

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Publication number
EP0574093A1
EP0574093A1 EP93202270A EP93202270A EP0574093A1 EP 0574093 A1 EP0574093 A1 EP 0574093A1 EP 93202270 A EP93202270 A EP 93202270A EP 93202270 A EP93202270 A EP 93202270A EP 0574093 A1 EP0574093 A1 EP 0574093A1
Authority
EP
European Patent Office
Prior art keywords
shaft
valve
inner race
valve bore
race
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.)
Withdrawn
Application number
EP93202270A
Other languages
German (de)
English (en)
Inventor
Paul Ludwig Gluchowski
David George Savini
Karl Jacob Haltiner
Roger Michael Brisbane
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.)
Motors Liquidation Co
Original Assignee
Motors Liquidation Co
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 Motors Liquidation Co filed Critical Motors Liquidation Co
Publication of EP0574093A1 publication Critical patent/EP0574093A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F02D9/1065—Mechanical control linkage between an actuator and the flap, e.g. including levers, gears, springs, clutches, limit stops of the like
    • 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
    • F02D9/1005—Details of the flap
    • F02D9/101—Special flap shapes, ribs, bores or the like
    • F02D9/1015—Details of the edge of the flap, e.g. for lowering flow noise or improving flow sealing in closed flap position
    • 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
    • F02D9/1035—Details of the valve housing
    • F02D9/106—Sealing of the valve shaft in the housing, e.g. details of the bearings

Definitions

  • This invention relates to a valve assembly for regulating the air flow to an internal combustion engine. More particularly, the invention relates to a valve assembly for an electronic throttle control system for an internal combustion engine.
  • Electronic throttle control systems for internal combustion engines frequently utilize a rotatable valve member disposed in an engine air induction passage to regulate the air flow through the passage.
  • the valve member can be a throttle valve which is positioned by an operator by way of a motor and shaft to control air flow to the internal combustion engine. Air flow to the internal combustion engine varies as a function of the air flow area around the valve member.
  • the air flow valve area around the valve member is geometrically related to the angular position of the valve member.
  • the change in air flow area around the valve member is substantial when the valve member is near its minimum air flow position. This can decrease control of the air flow to the internal combustion engine during low load conditions.
  • the air flow around the valve member when the motor is not actuated can be sufficiently restricted to prevent the internal combustion engine from producing enough power to idle or drive the vehicle.
  • an axial load on the shaft can cause the throttle valve to scrape on its bore.
  • the wear which can result tends to admit more air flow though the valve body than was originally calibrated. This can allow increased air flow around the valve member, which can be relatively substantial when the valve member is near its minimum air flow position. This can further decrease control of the air flow to the internal combustion engine during low load conditions.
  • Mechanisms to control endplay of the shafts are known, but many are difficult to assemble to the valve body. Examples of the prior art can be found in US Patent Nos. 4462358, 4474150 and 4860706.
  • a valve assembly in accordance with the present invention is characterised by the features specified in claim 1.
  • the present invention provides a valve assembly for regulating air flow to an internal combustion engine comprising a valve body having a valve bore forming an induction passage, and a shaft extending across the valve bore.
  • a valve member is secured to the shaft for rotation between a non-actuating position and a maximum actuating position.
  • a return mechanism urges the valve member toward the non-actuating position when the valve member is rotated away from the non-actuating position.
  • the shaft extends through a ball bearing disposed in a shaft socket.
  • a spring washer is disposed between the ball bearing and the shaft socket to resist displacement of the outer race of the ball bearing toward the valve bore; and a thrust collar is secured to the end of the shaft to resist displacement of the inner race of the ball bearing away from the valve bore.
  • Rotation of the valve member in excess of 90 degrees enables a relatively low change in air flow around the valve member when the valve member is rotated between the positions at which the minimum air flow is produced, thereby facilitating control of the air flow at low engine loads.
  • the chamfered peripheral edge reduces sharp changes in the air flow as the valve member approaches and moves away from the wall of the valve bore during decreases and increases in the air flow, respectively.
  • the engagement of the ball bearing with the shaft and the valve body limits axial float or displacement of the shaft with respect to the bore.
  • valve assembly 10 generally indicates a valve assembly of the present invention for regulating air flow to an internal combustion engine.
  • the valve assembly 10 comprises a valve body 12 having a valve bore 14 forming an induction passage for air flow to an internal combustion engine (not shown) with the valve bore having a generally circular cross section of substantially uniform diameter.
  • a shaft 16 has opposite ends which are journalled for rotation in the valve body 12. The shaft 16 extends across the valve bore 14.
  • a (flat butterfly) valve member 18 is secured to the shaft 16 for rotation between a non-actuating position, indicated in phantom by numeral 20, and a maximum actuating position, indicated in phantom by numeral 22.
  • the valve member 18 allows the maximum air flow when in the maximum actuating position 22.
  • the valve member 18 is typically parallel to the axis of the valve bore 14 when in the maximum actuating position 22.
  • the valve member 18 is rotated approximately 95 degrees between the maximum actuating position 22 and the non-actuating position 20. The rotation of the valve member 18 between the maximum actuating position 22 and the non-actuating position 20 enables control of the air flow through the valve bore 14.
  • the non-actuating position 20 can be defined by engagement of a shaft boss 17 with a non-actuating stop 21 fixed to the valve body 12.
  • the shaft boss 17 is fixed to a pulley which is fixed to the shaft 16.
  • the maximum actuating position 22 can be defined by engagement of the shaft boss 17 with an actuating stop 23 fixed to the valve body 12.
  • An actuator includes a toothed timing belt 28 which wraps around a correspondingly toothed pulley which is connected to the shaft 16 to produce rotation of the valve member 18.
  • the actuator includes a motor 29 having a toothed pulley which the timing belt 28 also wraps around. The motor 29 rotates its pulley to cause displacement of the timing belt 28 to rotate the valve member 18.
  • An adjustable tensioner can enable adjustment in the distance between the shaft 16 and motor shaft to adjust the tension in the timing belt 28.
  • the valve member 18, shown in Figure 3 has a peripheral edge 24 which is chamfered, wherein, when the valve member is rotated away from the maximum actuating position 22, the upstream side of the valve member is inclined toward the peripheral edge. The thickness of the valve member 18 thereby decreases in the radial direction toward the peripheral edge 24.
  • Figure 5 is a graph showing the flow area of the valve assembly 10 for various angles of the valve member 18 and for various thicknesses of the peripheral edge 24.
  • the graph is based on theoretical calculations.
  • the flow area is the area of the space between the valve member 18 and the valve bore 14 perpendicular to the axis of the valve bore. Flow area is generally proportional to air flow.
  • the variations in thickness of the peripheral edge 24 are produced by varying degrees of thickness reduction produced by the chamfer in the peripheral edge 24.
  • the 0 degree position corresponds to the valve member 18 being in a plane perpendicular to the axis of the valve bore 14.
  • Figure 5 illustrates the value of the (chamfered) peripheral edge 24 since it results in a gradual change in flow area produced by oscillation of the valve member 18 in the region wherein the flow area is minimum. This improves control of the internal combustion engine at low loads since small oscillations of the valve member 18, when it is in the positions wherein the flow area is minimum, do not substantially affect engine output.
  • the (chamfered) peripheral edge 24 enables these control improvements while also allowing the valve member 18 to be sufficiently thick for strength requirements.
  • the valve member 18 is preferably 2 mm thick, with the chamfer producing a peripheral edge having a thickness of 0.5 mm.
  • Figure 5 also illustrates the capability of the valve assembly 10 to allow engine operation if the motor 29 does not actuate the valve member 18 since under such conditions, the valve member will be urged by the return means 26 to rotate the valve member to the non-actuating position 20.
  • the valve member 18 When the valve member 18 is in the non-actuating position 20 (that is, rotated approximately 5 degrees beyond the 0 degree position away from the maximum actuating position 22), the flow area is sufficient to allow sufficient air to flow to the internal combustion engine to allow it to produce sufficient output to idle or drive the vehicle.
  • valve assembly 10 Another advantage of the valve assembly 10 is that the shaft boss 17 is away from the non-actuating stop 21 when the valve member 18 is in the position wherein the flow area is minimum which is typically the position of the valve member when the internal combustion engine is idling. This reduces the likelihood of the shaft boss 17 contacting the non-actuating stop 21 when the internal combustion engine is idling.
  • the valve assembly 10 also includes a shaft socket 30 connected to the valve body 12 externally thereof.
  • the shaft socket 30 has an axis which intersects the centre of the valve bore 14 and which is perpendicular to the valve bore.
  • the shaft socket 30 has a socket opening 32 enabling one end of the shaft 16 to extend into the shaft socket.
  • a ball bearing having outer race 36 and an inner race 38 is disposed in the shaft socket 30 so that the one end of the shaft 16 extends through the inner race 38.
  • the inner race 38 has an inner diameter which is sized to establish a clearance between the inner race 38 and shaft 16.
  • the outer race 36 has an outer diameter which is sized to establish a clearance between the outer race and shaft socket 30.
  • a thrust collar 40 is secured to the shaft 16, by a press fit, to prevent displacement of the inner race 38 along the axis of the shaft away from the valve bore 14.
  • a resilient washer 42 is disposed between the outer race 36 and shaft socket 30 to resist displacement of the outer race toward the valve bore 14 along the axis of the shaft 16.
  • a bearing means 44 is provided between the valve body 12 and the other end of the shaft 16.
  • the bearing means 44 is adapted to urge the other end of the shaft 16 away from the valve bore 14 along the axis of the shaft to limit axial end float of the shaft.
  • the bearing means 44 comprises a ball bearing having an outer race 46 and an inner race 48 with the other end of the shaft 16 extending through the inner race 48.
  • the inner race 48 has an inner diameter which is sized to establish a clearance between the inner race 48 and shaft 16.
  • the bearing means 44 further comprises a bearing seat 50 connected to the valve body 12 externally thereof.
  • the bearing seat 50 has a seat opening 52 through which the other end of the shaft 16 extends.
  • the outer race 46 is disposed on the bearing seat 50 so that axial displacement of the outer race 46 along the shaft toward the valve bore 14 is obstructed.
  • the bearing means 44 also includes a thrust retainer 54 engaging the inner race 48 to urge the inner race 48 toward the valve bore 14 along the axis of the shaft 16.
  • Axial float of the shaft 16 with respect to the valve bore 14 is limited by the thrust collar 40 and bearing means 44 which limit displacement of the shaft 16 inward toward the valve bore 14 along the axis of the shaft, with the resilient washer 42 maintaining a selected clearance between the valve member 18 and valve bore 14.
  • the urging of the shaft 16 by the resilient washer 42 and bearing means 44 also reduces axial play between the outer and inner races 36, 38, and between the outer and inner races 46, 48.
  • the resilient washer 42 can also deflect to maintain the selected clearance if temperature changes produce different thermal expansions of the shaft 16 and valve body 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
EP93202270A 1990-07-12 1991-06-18 Assemblage de soupape Withdrawn EP0574093A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US55031390A 1990-07-12 1990-07-12
US550313 1990-07-12

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP91201535.1 Division 1991-06-18

Publications (1)

Publication Number Publication Date
EP0574093A1 true EP0574093A1 (fr) 1993-12-15

Family

ID=24196644

Family Applications (2)

Application Number Title Priority Date Filing Date
EP93202270A Withdrawn EP0574093A1 (fr) 1990-07-12 1991-06-18 Assemblage de soupape
EP91201535A Withdrawn EP0466227A1 (fr) 1990-07-12 1991-06-18 Assemblage de soupape

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP91201535A Withdrawn EP0466227A1 (fr) 1990-07-12 1991-06-18 Assemblage de soupape

Country Status (3)

Country Link
EP (2) EP0574093A1 (fr)
JP (1) JPH04249678A (fr)
CA (1) CA2044213A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2732073A1 (fr) * 1995-03-23 1996-09-27 Bosch Gmbh Robert Dispositif d'etranglement pour moteur a combustion interne et procede de realisation
GB2304861A (en) * 1995-09-07 1997-03-26 Ford Motor Co Throttle shaft seal for a throttle body
US6070852A (en) * 1999-01-29 2000-06-06 Ford Motor Company Electronic throttle control system
US6095488A (en) * 1999-01-29 2000-08-01 Ford Global Technologies, Inc. Electronic throttle control with adjustable default mechanism
US6155533A (en) * 1999-01-29 2000-12-05 Ford Global Technologies, Inc. Default mechanism for electronic throttle control system
US6173939B1 (en) 1999-11-10 2001-01-16 Ford Global Technologies, Inc. Electronic throttle control system with two-spring failsafe mechanism
US6244565B1 (en) 1999-01-29 2001-06-12 Ford Global Technologies, Inc. Throttle body shaft axial play control
US6253732B1 (en) 1999-11-11 2001-07-03 Ford Global Technologies, Inc. Electronic throttle return mechanism with a two-spring and two-lever default mechanism
US6267352B1 (en) 1999-11-11 2001-07-31 Ford Global Technologies, Inc. Electronic throttle return mechanism with default and gear backlash control
US6286481B1 (en) 1999-11-11 2001-09-11 Ford Global Technologies, Inc. Electronic throttle return mechanism with a two-spring and one lever default mechanism
US6299545B1 (en) 1999-05-03 2001-10-09 Visteon Global Tech., Inc. Rotating shaft assembly
CN108603446A (zh) * 2016-03-03 2018-09-28 马勒国际有限公司 用于机动车辆的内燃机的新鲜空气供应装置

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5282448A (en) * 1993-03-01 1994-02-01 General Motors Corporation Fuel control of a two-stroke engine with over-center throttle body
JPH07198045A (ja) * 1994-01-10 1995-08-01 Ngk Insulators Ltd 排気管用バタフライ弁及びこれを用いた排気管構造
IT1286795B1 (it) * 1996-12-02 1998-07-17 Magneti Marelli Spa Corpo farfallato motorizzato
US5979871A (en) * 1998-03-30 1999-11-09 Ford Motor Company Clamshell throttle valve assembly
US6129071A (en) * 1998-07-20 2000-10-10 Ford Global Technologies, Inc. Throttle valve system
EP1375871B1 (fr) * 1999-11-01 2004-12-29 Denso Corporation Procédé de montage d'une vanne à papillon pour l'aspiration d'un moteur à combustion interne
JP4285267B2 (ja) 2004-02-19 2009-06-24 株式会社デンソー 排気ガス再循環装置
US9915352B2 (en) * 2016-08-03 2018-03-13 Scc, Inc. Butterfly valve utilizing spring for consistent disk placement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE837785C (de) * 1943-05-15 1952-05-02 Bayerische Motoren Werke Ag Kugellagerdichtung fuer die Drosselklappenwellen von Vergasern
GB2067719A (en) * 1979-12-29 1981-07-30 Nissan Motor A throttle mechanism
US4860706A (en) * 1987-09-14 1989-08-29 Aisan Kogyo Kabushiki Kaisha Throttle body
US4938452A (en) * 1988-12-10 1990-07-03 Aisan Kogyo Kabushiki Kaisha Air control device for internal combustion engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4318386A (en) * 1979-09-20 1982-03-09 Automotive Engine Associates Vortex fuel air mixer
EP0076612A1 (fr) * 1981-09-29 1983-04-13 Merle Robert Showalter Obturateur d'étranglement
DE3205160C2 (de) * 1982-02-13 1984-05-30 Audi Nsu Auto Union Ag, 7107 Neckarsulm Drosselklappe für eine im Querschnitt kreisförmige Ansaugleitung einer Brennkraftmaschine
US4474150A (en) * 1982-11-22 1984-10-02 General Motors Corporation Valve assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE837785C (de) * 1943-05-15 1952-05-02 Bayerische Motoren Werke Ag Kugellagerdichtung fuer die Drosselklappenwellen von Vergasern
GB2067719A (en) * 1979-12-29 1981-07-30 Nissan Motor A throttle mechanism
US4860706A (en) * 1987-09-14 1989-08-29 Aisan Kogyo Kabushiki Kaisha Throttle body
US4938452A (en) * 1988-12-10 1990-07-03 Aisan Kogyo Kabushiki Kaisha Air control device for internal combustion engine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 11, no. 348 (M-642)14 November 1987 & JP-A-62 129 538 ( TOYOTA MOTOR CORP. ) 11 June 1987 *
PATENT ABSTRACTS OF JAPAN vol. 13, no. 299 (M-847)11 July 1989 & JP-A-01 087 838 ( HITACHI LTD ) 31 March 1989 *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2732073A1 (fr) * 1995-03-23 1996-09-27 Bosch Gmbh Robert Dispositif d'etranglement pour moteur a combustion interne et procede de realisation
GB2304861A (en) * 1995-09-07 1997-03-26 Ford Motor Co Throttle shaft seal for a throttle body
GB2304861B (en) * 1995-09-07 1999-09-01 Ford Motor Co Throttle shaft seal for a throttle body
US6070852A (en) * 1999-01-29 2000-06-06 Ford Motor Company Electronic throttle control system
US6095488A (en) * 1999-01-29 2000-08-01 Ford Global Technologies, Inc. Electronic throttle control with adjustable default mechanism
US6155533A (en) * 1999-01-29 2000-12-05 Ford Global Technologies, Inc. Default mechanism for electronic throttle control system
US6244565B1 (en) 1999-01-29 2001-06-12 Ford Global Technologies, Inc. Throttle body shaft axial play control
US6299545B1 (en) 1999-05-03 2001-10-09 Visteon Global Tech., Inc. Rotating shaft assembly
US6173939B1 (en) 1999-11-10 2001-01-16 Ford Global Technologies, Inc. Electronic throttle control system with two-spring failsafe mechanism
US6267352B1 (en) 1999-11-11 2001-07-31 Ford Global Technologies, Inc. Electronic throttle return mechanism with default and gear backlash control
US6286481B1 (en) 1999-11-11 2001-09-11 Ford Global Technologies, Inc. Electronic throttle return mechanism with a two-spring and one lever default mechanism
US6253732B1 (en) 1999-11-11 2001-07-03 Ford Global Technologies, Inc. Electronic throttle return mechanism with a two-spring and two-lever default mechanism
CN108603446A (zh) * 2016-03-03 2018-09-28 马勒国际有限公司 用于机动车辆的内燃机的新鲜空气供应装置
CN108603446B (zh) * 2016-03-03 2019-09-20 马勒国际有限公司 用于机动车辆的内燃机的新鲜空气供应装置

Also Published As

Publication number Publication date
JPH04249678A (ja) 1992-09-04
EP0466227A1 (fr) 1992-01-15
CA2044213A1 (fr) 1992-01-13

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