EP0797726A1 - Ventiltrieb einer brennkraftmaschine - Google Patents
Ventiltrieb einer brennkraftmaschineInfo
- Publication number
- EP0797726A1 EP0797726A1 EP95940953A EP95940953A EP0797726A1 EP 0797726 A1 EP0797726 A1 EP 0797726A1 EP 95940953 A EP95940953 A EP 95940953A EP 95940953 A EP95940953 A EP 95940953A EP 0797726 A1 EP0797726 A1 EP 0797726A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- intermediate member
- rotating body
- valve train
- bore
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 11
- 230000007246 mechanism Effects 0.000 title abstract description 10
- 230000005540 biological transmission Effects 0.000 claims abstract description 18
- 230000033001 locomotion Effects 0.000 claims abstract description 10
- 239000004575 stone Substances 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 210000002435 tendon Anatomy 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2101—Cams
- Y10T74/2102—Adjustable
Definitions
- the invention relates to a valve train of an internal combustion engine and, in particular, to a valve train of an internal combustion engine, in which a rotating body, preferably a cam, on a shaft, preferably the camshaft, can be rotated cyclically during the rotation of the shaft, in order thereby to provide variable valve control.
- a rotating body preferably a cam
- a shaft preferably the camshaft
- FIG. 23 An adjustment mechanism disclosed in this patent application is shown in FIG. 23 and comprises a camshaft 100 with an axis of rotation 500 on which a cam 200 is mounted. Also mounted on the camshaft 100 is an inner eccentric 300, on the outer surface 320 of which is eccentric to the axis of rotation 500, an outer eccentric 400 is mounted. The inner eccentric 300 and the outer eccentric 400 can be rotated via an inner eccentric ring gear 340 and an outer eccentric ring gear 440, as a result of which an intermediate member 490 mounted on an eccentric outer surface of the outer eccentric 400 can be displaced in a plane perpendicular to the axis of rotation 500 relative to the camshaft 100.
- Intermediate member 490 is drivingly coupled to cam 200 and camshaft 100.
- an axial pin 800 which is rotatably mounted in the camshaft 100 as the first transmission element 800, engages with a sliding block flag 810, which is made of the same material as the axial pin 800, into a first groove 600, which is designed as a sliding guide and is formed in the intermediate member 490.
- One of the first groove 600 diametrically Opposing second groove 700 of the intermediate member 490 is in engagement with a sliding block lug 910, which is made of the same material with a second axial pin 900, which is rotatably mounted in a bore 110 of the cam 200.
- the rotation of the camshaft 1 is transmitted via the first axial pin 100 through its flag 110 and the first groove 600 to the intermediate member 490 and from there via the second groove 700 and the flag 910 of the second axial pin 900 to cam 200.
- the intermediate member 490 is located in a concentric position to the camshaft 100, the cam 200 rotates synchronously with the camshaft 100.
- the object of the invention is to further develop the prior art described above in such a way that the friction between the components moving towards one another and thus the wear of these components is reduced with a minimal overall volume.
- a valve train of an internal combustion engine has an adjusting mechanism with a shaft having an axis of rotation, via which the rotary movement for the valve train is introduced therein, with a rotating body which is rotatably mounted with respect to the shaft, and with an intermediate member which surrounds the shaft and which in the axial direction is adjacent to the rotatable rotating body is arranged and rotatable relative to the shaft and is drivingly connected to the shaft via a first sliding guide and a first transmission element and to the rotating body via a second sliding guide and a second transmission element.
- At least one of the transmission elements comprises a radial pin, which is arranged essentially perpendicular to the axis of rotation of the shaft.
- the use of a radial pin as a transmission element has the advantage that the Tilting moment can be reduced, whereby the total occurring tipping moment is reduced.
- the first transmission element is preferably a radial pin.
- Intermediate link may be possible. This can be achieved, for example, in that the radial pin has a kind of spherical head at the end with which it is in engagement with the intermediate member, which ball head fits into the
- the radial pin is slidably received in a recess in a sliding block, which is pivotably mounted in a bearing seat of the intermediate member.
- the pivoting movement takes place between the sliding block and the bearing seat of the intermediate member, while the longitudinal displacement takes place between the radial pin and the sliding block. This allows the radial pin to be fixed firmly in the shaft.
- the radial pin can have a cylindrical section and a substantially rectangular section, the cylindrical section being inserted into a radial bore of the shaft and the substantially rectangular section being in sliding engagement with the recess in the sliding block.
- a shoulder can be provided, which with one on the shaft element to be pushed on forms a form-fitting safeguard against migration of the radial pin out of the radial bore.
- the diameter of the cylindrical section is preferably smaller than the larger of the two cross-sectional edges of the substantially rectangular section.
- the sliding block preferably has the outer contour of a cylinder segment flattened on two sides, the two rounded side surfaces being jacket segments of a cylinder which are connected to one another by an end face.
- the recess is preferably open to the side of the sliding block opposite the end face.
- the sliding block has two sliding surfaces for sliding contact with two opposing surfaces of the rectangular section of the radial pin and two shoulders for contacting a third surface of the rectangular section of the radial pin. A recess can be formed between the shoulders to facilitate the assembly of the radial pin.
- the cylindrical section of the radial pin can be inserted through the recess into the radial bore of the shaft.
- the bearing seat is preferably open on the side of the intermediate member facing the rotating body and has two concave side walls, the radius of curvature of which corresponds to that of the side faces of the sliding block, and an end face for bearing against the end face of the radial pin. This allows the sliding block to be inserted laterally into the bearing seat.
- the rotary body and the intermediate link can be axially fixed on the shaft using the radial pin.
- the second transmission element can comprise an axial pin mounted parallel to the axis of rotation in a bore in the rotating body.
- the washer can have an interruption which ensures free access to the axial pin, the washer on the opposite side of the interruption having a flattened portion which rests on the sliding block and acts as an anti-rotation device for the washer.
- the side faces of the slide flag can extend to one or both sides of the axial pin beyond the circumference of its cylindrical shaft, so that the axial pin has an L-shape or T-shape together with the slide flag. This results in an enlarged contact surface of the sliding stone flag and thus a reduction in the surface pressure towards the groove of the intermediate member and, in the case of a T-shape, a symmetrical introduction of force.
- the bore of the rotating body in which the axial pin is mounted can be closed on the side facing away from the intermediate member and the shaft can have a longitudinal bore and one or more shaft oil bores extending from the longitudinal bore to the outer surface of the shaft.
- a rotary body oil hole can be arranged so that oil from the longitudinal bore of the shaft via the shaft oil bore and the rotary body oil bore into the bore for mounting the axial pin between them and the closed end of this bore, whereby the axial pin through the oil pressure is firmly pressed against the end wall in the groove of the intermediate link. This improves the sliding behavior of the sliding stone flag in the groove.
- a third sliding guide is provided between the rotating body and the intermediate member, which represents a support between the rotating body and the intermediate member and at the same time enables a relative movement between the rotating body and the intermediate member in a direction perpendicular to the axis of rotation.
- This third sliding guide serves to absorb the tilting moment generated by the transmission of the rotary motion on the intermediate member.
- the support provided thereby relieves the load on the tendon bearing between the intermediate member and the external eccentric. Instead, the support against this tilting moment takes place between the rotating body and the intermediate member, which have only a low relative speed to one another.
- the free tilting moment is supported in the valve train according to the invention via the large-area bearing between the rotating body and the shaft, at which only low relative speeds also occur and which is therefore only slightly loaded. This significantly reduces the overall friction loss in the system. In addition, the holding torque of the external eccentric is significantly reduced.
- the third sliding guide can be designed such that a groove is provided in the rotating body, into which a web formed on the intermediate member engages.
- the groove runs in the circumferential direction of the rotating body, wherein it is interrupted by an opening through which the intermediate member with the web can be inserted in the radial direction.
- an intermediate disk can be accommodated in the groove in addition to the web. As a result, the intermediate member also abuts in the area in which the groove is interrupted.
- the rotating body can be widened in the area of the bearing surface in the direction of the axis of rotation and can have dimensions that are wider than at least a portion of the outer contour of the rotating body.
- the shaft is preferably a camshaft and the rotating body is a cam for actuating one
- the intermediate member can be designed so that its outer contour does not project beyond the outer contour of the cam in any operating position. This enables the
- FIG. 1 shows an axial section through a first embodiment of the arrangement according to the invention
- Fig. 1A is an exploded perspective
- FIG. 1B is an exploded perspective view corresponding to FIG. 1A from a different perspective
- Fig. 2 is a radial section along the line E-E in Fig. 1,
- FIG. 3 is a front view of a rotating body designed as a cam
- FIG. 4 is a side view of the cam of FIG. 3,
- Fig. 5 is a sectional view of the cam along the line C-C in Fig. 3,
- FIG. 6 is a perspective view of the cam of FIG. 3,
- FIG. 7 is a front view of an embodiment of an intermediate member
- Fig. 8 is a side view of the intermediate member according to
- Fig. 9 is a sectional view of the link along line H-H in Fig. 7,
- Fig. 10 is a sectional view of the intermediate link along the line II in Fig. 8, 11 is a perspective view of the link shown in FIG. 7,
- FIG. 12 is a first side view of an embodiment of a radial pin
- FIG. 14 is a top view of the radial pin of FIG. 12;
- 15 is a first side view of an embodiment of a sliding block
- FIG. 16 is a perspective view of the slide block of FIG. 15;
- FIG. 17 is a plan view of the sliding block according to FIG. 15 in the direction of the arrow X in FIG. 15,
- Fig. 18 is an axial section through a second
- Fig. 22 is a radial section along the line LL in Fig. 21 and 23 shows an axial section through an adjustment mechanism according to a prior art, which has not been published beforehand.
- a first embodiment of a valve train with an adjusting mechanism for providing variable valve control for internal combustion engines is explained below with reference to FIGS. 1-17.
- a rotary body 10 designed as a cam is rotatably mounted on a shaft 1 designed as a camshaft, which is rotated at half the crankshaft speed during operation of the internal combustion engine, preferably by the crankshaft of the internal combustion engine (not shown).
- an inner eccentric 91 is provided, which is rotatably fixed by a bearing block 92 to a cylinder head 93, which is only indicated.
- An outer eccentric 90 is rotatably mounted on an outer surface of the inner eccentric 91 that is eccentric to the axis of rotation D.
- the inner eccentric 91 is rotatable via an inner eccentric ring gear 91A, while the outer eccentric 90 is rotatable by means of an outer eccentric ring gear 90A which is mounted coaxially with the axis of rotation D and which engages with a lug 90B in a groove 90C of the outer eccentric.
- an intermediate member 20 which is rotatably mounted on an eccentric outer surface of the outer eccentric 90.
- the intermediate member 20 assumes a position coaxial with the axis of rotation D or a position in which its axis of rotation is offset with respect to the axis of rotation D of the camshaft 1.
- the intermediate member 20 is drivingly connected to the camshaft 1 and the cam 10, so that rotation of the camshaft 1 via the intermediate member 20 onto the cam 10 is transmitted. If, depending on the position of the outer eccentric 90 and the inner eccentric 91, the rotation of the intermediate member 20 is concentric with the rotation of the camshaft 1, the cam 10 rotates synchronously with the camshaft 1. If the intermediate member 20 is displaced radially from its concentric position to the camshaft 1 by a corresponding displacement of the outer eccentric 90 and / or the inner eccentric 91, a cyclical increase in speed or a decrease in the speed of rotation of the cam 10 relative to that of the camshaft 1 takes place with each revolution .
- the drive connection of the camshaft 1 to the intermediate member 20 takes place via a radial pin 40, which is inserted into a corresponding radial bore 4 of the camshaft 1.
- the camshaft 1 has a longitudinal bore 2 and the radial bore 4 has a depth that is greater than the sum of the camshaft radius and the radius of the longitudinal bore 2.
- the radial pin 40 has a cylindrical section 42 which is fully inserted into the camshaft 1 and a substantially rectangular section 43 which projects from the camshaft 1.
- a shoulder 41 is formed between the cylindrical section 42 and the rectangular section 43.
- the shoulder 41 is designed with a radius corresponding to the curvature of the surface of the camshaft 1 (see Fig. 12). This ensures surface contact and enables the formation of a lubricating film.
- the rectangular section 43 is slidably surrounded by a recess 51 of a sliding block 50.
- the sliding block 50 has the shape of a cylinder segment flattened on two sides, the two rounded side surfaces 52, 53 being shell segments of a cylinder which are connected to one another by an end surface 54.
- the recess 51 is open on the side opposite the end face 54 and has two sliding surfaces 55, 56 for sliding contact with two opposing surfaces of the rectangular section 43 of the radial pin 40 and two shoulders 57, 58 for contacting a third surface of the rectangular section 43 of the radial pin 40.
- a recess 59 is formed between the shoulders 57, 58 in order to facilitate the assembly of the radial pin 40. If, in fact, the diameter of the cylindrical section 42 of the radial pin 40 is smaller than at least the larger of the two cross-sectional edges 44, 45 of its essentially rectangular section 43, the radial pin 40 due to the recess 59 can pass through the recess 51 in register with the radial bore 4 in the shaft 1 are inserted.
- the rectangular section 43 of the radial pin 40 and the recess 51 of the sliding block 50 are in terms of their Dimensions matched so that the sliding block 50 can slide over the rectangular section 43.
- the intermediate member 20 has a bearing seat 22 which is open on the side facing the cam 10.
- the concave side walls 25, 26 of the bearing seat 22 adjoining the open side are designed corresponding to the radius of the side surfaces 52, 53 of the sliding block 50, so that the sliding block 50 which can be inserted into the bearing seat 22 through the open side of the bearing seat 22 pivots with respect to the intermediate member 20 can be.
- An end face 27 of the bearing seat 22 serves to abut the sliding block 50.
- a recess 27A provided in the end face 27 enables the radial pin 40 to be inserted during assembly.
- a groove 23 is formed, into which a sliding block lug 71 engages, which is made of the same material with an axial pin 70.
- the axial pin 70 is rotatably mounted in a bore 13 in the cam 10 which is closed at one end and extends parallel to the axis of rotation D.
- a rotary body oil bore 19 provided in the cam 10 is at least temporarily in overlap with a shaft oil bore 3 of the camshaft 1 and opens with its opposite end in the bore 13 in a region between the end of the axial pin 70 facing away from the sliding stone flag 71 and the closed end of the bore 13.
- the rotary body oil bore 19 extends over the entire rotary range of the cam 10 relative to the camshaft 1 in connection with the Shaft oil hole 3 is located.
- an oil pressure prevailing in the longitudinal bore 2 of the camshaft 1 is applied to the end face of the axial pin 70 and the Slide stone flag 71 presses against the end wall 24 of the groove 23 of the intermediate member 20 in order to dampen the play between the slide stone flag 71 and the groove 23 when the system is changed.
- the diameter of the pin of the axial pin 70 is preferably smaller than the width of the sliding block lug 21 or of the groove 23.
- the length of the pin of the axial pin 70 is preferably larger than half the width of the cam 1.
- the intermediate member 20 has on the end face which has the open side of the groove 23 and the open side of the bearing seat 22, a web 21 which extends substantially in the circumferential direction and is interrupted by the groove 23 and the open side of the bearing seat 22.
- the web 21 can be inserted by radial insertion into a groove 11 which is formed on the side of the cam 10 facing the intermediate member 20.
- the groove 11 runs essentially in the circumferential direction and is interrupted by an opening 12, which enables the web 21 to be inserted radially.
- the depth of the groove 11 and the thickness of the web 21 are coordinated so that a tilting moment of the intermediate member 20 can be absorbed and at the same time a radial displacement and a rotation of the intermediate member 20 relative to the cam 10 is possible.
- the groove 11 of the cam 10 is delimited on its side facing the intermediate member 20 by an essentially circumferential web 17 which is also interrupted by the opening 12.
- this web 17 deviates from the circumferential direction in a central region 18 in the region of the line DD in FIG. 3.
- the web 17 is raised with respect to the bottom of the groove 11, for example by the fact that in the central area 18 the upper edges of the web 17 on both Sides of the bore for the camshaft 1 run parallel to each other.
- the bottom of the groove 28 formed on the intermediate member 20 by the web 21 is lowered in a corresponding central region 29 with respect to the upper edge of the web 21, for example in that in this central region 29 the bottom portions of the groove 28 have a changed radius of curvature.
- the axial pin 70 is inserted with its cylindrical shaft into the bore 13 of the cam 10.
- the sliding block 50 is inserted into the bearing seat 22 from the open side thereof.
- the intermediate member 20 is inserted with its web 21 into the groove 11 from the side of the cam 10 opposite the bore 13 and thus the cam tip.
- the sliding stone flag 71 enters the groove 23.
- the intermediate member 20 and the cam 10 are axially fixed to each other.
- the unit thus produced from intermediate link and cam is pushed onto the camshaft and the recess in the sliding block 50 is brought into overlap with the radial bore 4 in the camshaft 1.
- the radial pin 40 is inserted through the recess 51 into the radial bore 4.
- the intermediate disk 60 is essentially ring-shaped and has a flattened portion 62 toward the cam tip, which provides a free passage for the axial pin 70 and acts as an anti-rotation device.
- an interruption 61 is provided which provides free passage for the sliding block 50.
- FIG. 21 shows a third embodiment, in which a common inner eccentric 91 is provided for two cams 10A, 10B.
- an adjustment unit is provided on both sides of the camshaft bearing, so that a subsequent insertion of the eccentric is not possible.
- local recesses are provided on the eccentrics in order to insert the radial pin in the case of a complete preassembly unit comprising cams 10A, 10B, the two intermediate members 20 and the eccentrics through the recesses 51 in the respective sliding blocks 50 into the corresponding radial bores 4 of the camshaft 1 to be able to introduce.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
Claims
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4444289 | 1994-12-13 | ||
DE4444289 | 1994-12-13 | ||
DE19529346 | 1995-08-09 | ||
DE19529346 | 1995-08-09 | ||
PCT/DE1995/001783 WO1996018807A1 (de) | 1994-12-13 | 1995-12-12 | Ventiltrieb einer brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0797726A1 true EP0797726A1 (de) | 1997-10-01 |
EP0797726B1 EP0797726B1 (de) | 1998-05-27 |
Family
ID=25942799
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95940953A Expired - Lifetime EP0797726B1 (de) | 1994-12-13 | 1995-12-12 | Ventiltrieb einer brennkraftmaschine |
Country Status (7)
Country | Link |
---|---|
US (1) | US5884592A (de) |
EP (1) | EP0797726B1 (de) |
AT (1) | ATE166698T1 (de) |
AU (1) | AU4252496A (de) |
DE (2) | DE59502370D1 (de) |
ES (1) | ES2119503T3 (de) |
WO (1) | WO1996018807A1 (de) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19546366C2 (de) * | 1995-12-12 | 2002-01-17 | Erwin Korostenski | Ventiltrieb einer Brennkraftmaschine |
US6343582B1 (en) * | 1999-02-08 | 2002-02-05 | Industrial Technology Research Institute | Decompression device for four-stroke engine |
GB2365508A (en) * | 2000-08-08 | 2002-02-20 | Mechadyne Internat Plc | Variable valve timing mechanism |
US8186319B2 (en) * | 2007-07-02 | 2012-05-29 | Borgwarner Inc. | Concentric cam with check valves in the spool for a phaser |
JP5645896B2 (ja) * | 2012-09-20 | 2014-12-24 | リンナイ株式会社 | ガス流量制御装置 |
KR101786708B1 (ko) * | 2016-03-31 | 2017-10-18 | 현대자동차 주식회사 | 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진 |
KR101734235B1 (ko) * | 2016-03-31 | 2017-05-11 | 현대자동차 주식회사 | 연속 가변 밸브 타이밍 장치 및 이를 포함하는 엔진 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2305589A1 (fr) * | 1975-03-27 | 1976-10-22 | Baguena Michel | Distribution variable pour moteur a quatre temps |
GB8711366D0 (en) * | 1987-05-14 | 1987-06-17 | Mitchell S W | Driving connections between two rotatable bodies |
JP2644408B2 (ja) * | 1991-03-29 | 1997-08-25 | アーウィン コロステンスキー | 内燃機関の連続可変バルブタイミング機構 |
JP3177532B2 (ja) * | 1992-01-27 | 2001-06-18 | 株式会社ユニシアジェックス | 内燃機関の吸排気弁駆動制御装置 |
GB2275096B (en) * | 1993-02-15 | 1996-05-22 | Unisia Jecs Corp | Valve control device for internal combustion device |
-
1995
- 1995-12-12 AU AU42524/96A patent/AU4252496A/en not_active Abandoned
- 1995-12-12 DE DE59502370T patent/DE59502370D1/de not_active Expired - Fee Related
- 1995-12-12 EP EP95940953A patent/EP0797726B1/de not_active Expired - Lifetime
- 1995-12-12 WO PCT/DE1995/001783 patent/WO1996018807A1/de active IP Right Grant
- 1995-12-12 US US08/849,846 patent/US5884592A/en not_active Expired - Fee Related
- 1995-12-12 ES ES95940953T patent/ES2119503T3/es not_active Expired - Lifetime
- 1995-12-12 DE DE19581405T patent/DE19581405D2/de not_active Expired - Lifetime
- 1995-12-12 AT AT95940953T patent/ATE166698T1/de not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO9618807A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP0797726B1 (de) | 1998-05-27 |
AU4252496A (en) | 1996-07-03 |
US5884592A (en) | 1999-03-23 |
DE59502370D1 (de) | 1998-07-02 |
DE19581405D2 (de) | 1998-02-05 |
WO1996018807A1 (de) | 1996-06-20 |
ES2119503T3 (es) | 1998-10-01 |
ATE166698T1 (de) | 1998-06-15 |
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