EP2400121A1 - Phase-variable device for engine - Google Patents
Phase-variable device for engine Download PDFInfo
- Publication number
- EP2400121A1 EP2400121A1 EP09840363A EP09840363A EP2400121A1 EP 2400121 A1 EP2400121 A1 EP 2400121A1 EP 09840363 A EP09840363 A EP 09840363A EP 09840363 A EP09840363 A EP 09840363A EP 2400121 A1 EP2400121 A1 EP 2400121A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotary drum
- clutch case
- clutch
- grooves
- phase
- 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
- 239000003921 oil Substances 0.000 claims description 40
- 239000010705 motor oil Substances 0.000 claims description 11
- 230000033001 locomotion Effects 0.000 claims description 8
- 230000005540 biological transmission Effects 0.000 abstract description 6
- 239000004744 fabric Substances 0.000 description 7
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 235000019589 hardness Nutrition 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
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
-
- 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
- F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and 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
-
- 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
- F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
- F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
-
- 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
- F01L1/352—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 bevel or epicyclic gear
- F01L2001/3522—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 bevel or epicyclic gear with electromagnetic brake
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- This invention relates to a phase-varying apparatus for use with an automobile engine for varying the rotational phase of the camshaft of a valve actuation mechanism relative to its sprocket to thereby change the opening/closing timing of a valve or valves by exerting a braking force of an electromagnetic clutch to the rotary drum operably coupled to the sprocket.
- This type of phase-varying apparatus has been proposed in, for example, Patent Document 1 cited below, in which the camshaft of a valve actuation mechanism is normally rotated in synchronism with a sprocket driven by the crankshaft of the engine via a rotary drum such that when an electromagnetic brake means exerts a braking force to the rotary drum the phase of the camshaft relative to the sprocket is changed.
- In this phase-varying apparatus, engine oil is introduced between the frictional faces of the friction member of a clutch case and of the rotary drum in frictional contact with the friction member. The oil is introduced from an oil passage formed in the camshaft to the frictional faces through an oil sump provided inside the clutch case and through an oil feeding cut-away formed in the inner circumferential edge of the front end of the clutch case. As a consequence, these frictional faces are cooled by the engine oil.
-
- Patent Document 1:
JPA Laid Open No. 2002-371814 Figs. 1 through 4 ) - The phase-varying apparatus disclosed in Patent Document 1 has an electromagnetic clutch constituting a relevant portion of the electromagnetic braking means, which comprises: a generally annular clutch case secured not to rotate about its axis. It has a C-shape transverse cross section and an open end facing the disk face of the rotary drum; an electromagnetic coil accommodated in the clutch case; a plate for holding a friction member (referred to as friction member holding plate) securely fixed to the inside of, and near the open end of, the clutch case; and a flattened frictional member jointed to the friction member holding plate and having a surface slightly projecting from the front end of the inner and outer circumferential walls of the clutch case. The frictional member is made of a fabric that can positively convert the attractive force generated by the electromagnetic clutch into a braking torque that acts on the rotary drum.
- However, such fabric friction member is likely to be clogged after a certain period of time and then its friction coefficient µ is significantly reduced. As a consequence, its frequency of use is limited when it is used as the frictional member of the electromagnetic clutch.
- It is noted that in order to suppress fluctuations in attractive forces of the electromagnetic clutch a gap (called air gap) of a precise magnitude must be given between the face s of the friction member and the rotary drum by preciesly manufacturing the fabric friction member and the rotary drum. However, precision manufacture of an air gap and accurate measurement of the air gap thus formed require special facilities.
- It is, therefore, an object of the present invention to overcome such prior art problems as mentioned above by providing a phase-varying apparatus for use with an automobile engine that can transmit a torque from the clutch case to the rotary drum via an oil film lying between them.
- To achieve the object above, there is provided in accordance with the present invention a phase-varying apparatus for use with an automobile engine, the apparatus including, as defined in claim 1: an outer cylinder subjected to the rotational motion of the crankshaft of the engine; an inner cylinder connected to the camshaft for opening and closing the intake and exhaust valves of the engine and rotatable relative to the outer cylinder; and an intermediate member, disposed between the outer and inner cylinders, for transmitting the rotational motion of the outer cylinder to the inner cylinder, the intermediate member movable in the axial direction thereof to cause a relative rotation of the inner cylinder relative to the outer cylinder to thereby vary the valve timing of the intake and exhaust valves, the phase-varying apparatus characterized in that:
- the phase-varying apparatus comprises:
- an annular rotary drum coaxially disposed round the inner cylinder and connected to the intermediate member, and
- an electromagnetic clutch for controlling the braking force to be exerted to the rotary drum in accord with the driving condition of the engine;
- the electromagnetic clutch has
- an annular clutch case arranged facing the rotary drum, and
- an electromagnetic coil for generating a braking force that acts on the rotary drum when energized so as to move the clutch case towards the rotary drum; and
- a multiplicity of grooves are formed in at least one of the opposing faces of the rotary drum and the clutch case, for establishing engine oil passages to form an oil film in and around the grooves such that the oil film transmits a torque between the rotary drum and the clutch case.
- (Function) When the electromagnetic coil is energized, the clutch case is moved towards the rotary drum, so that the braking force of the electromagnetic coil is exerted to the rotary drum. In this case, because of the oil film staying in and around the grooves formed in at least one of the opposing faces of the rotary drum and the clutch case, a torque is positively transmitted between the clutch case and the rotary drum. As a result, a large friction coefficient µ is obtained without providing any fabric friction member for transmitting a torque between the clutch case and the rotary drum.
- As defined in
claim 2, the phase-varying apparatus defined in claim 1 may be configured in such a way that
the annular clutch case has an outer and an inner circumferential wall together forming a C-shape transverse cross section and a circular groove between the outer and inner circumferential walls, the circular groove adapted to accommodate therein the electromagnetic coil and facing the rotary drum, and the outer circumferential wall provided on one end thereof facing the rotary drum with the grooves,
grooves are formed in the front end of the outer circumferential wall facing the rotary drum;
a gap is formed between the inner circumferential wall of the clutch case and the rotary drum; and
the rotary drum and the clutch case transmits torque to each other via the oil film formed in and around the grooves. - (Function) Transmission of torque can be performed between the clutch case and the rotary drum by means of an oil film formed in and around the grooves while retaining a gap between the inner circumferential wall and the rotary drum. As a result, the air gap between the inner circumferential wall and the rotary drum can be easily adjusted.
- As can be seen from the description given above, a phase-varying apparatus in accord with Claim 1 can provide a large µ without any fabric friction member between the clutch case and the rotary drum.
- In a phase-varying apparatus in accord with
claim 2, the gap between the inner circumferential wall of the clutch case and the rotary drum can be easily adjusted to adjust the attractive force of the electromagnetic clutch. -
-
Fig. 1 shows a longitudinal cross section of a phase-varying apparatus for use with an automobile engine in accordance with a first embodiment of the invention; -
Fig. 2 is a perspective view of the apparatus ofFig. 1 , illustrating the internal structure of the apparatus; -
Fig. 3 is a front view of the apparatus ofFig. 1 ; -
Fig. 4 is a cross section taken along Line A-A ofFig. 3 ; -
Fig. 5 is a cross section of a relevant portion of the clutch case in accordance with the first embodiment of the invention; -
Fig. 6 is an enlarged cross section of the clutch case shown inFig. 5 ; -
Fig. 7 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a second embodiment of the invention; -
Fig. 8 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a third embodiment of the invention; -
Fig. 9 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a fourth embodiment of the invention; -
Fig. 10 is a front view of a relevant portion of the clutch case in accordance with the fourth embodiment of the invention; -
Fig. 11 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a fifth embodiment of the invention; and -
Fig. 12 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a sixth embodiment of the invention. - 10 Outer hollow cylinder; 20 Inner hollow cylinder; 30 Intermediate member; 42 Electromagnetic clutch; 44 Rotary drum; 44a Disk face; 60 Clutch case; 62 Electromagnetic coil; 63 Inner circumferential wall; 63a End face of inner wall; 64 outer circumferential wall; 64a End face of outer circumferential wall; 66 and 67 Grooves formed in the end faces;
- The invention will now be described in detail by way of example with reference to the accompanying drawings, in which:
Fig. 1 shows a longitudinal cross section of a phase-varying apparatus for use with an automobile engine in accordance with a first embodiment of the invention;Fig. 2 is a perspective view of the apparatus ofFig. 1 , illustrating the internal structure of the apparatus;Fig. 3 is a front view of the apparatus ofFig. 1 ;Fig. 4 is a cross section taken along Line A-A ofFig. 3 ;Fig. 5 is a cross section of a relevant portion of the clutch case in accordance with the first embodiment of the invention;Fig. 6 is an enlarged cross section of the clutch case shown inFig. 5; Fig. 7 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a second embodiment of the invention;Fig. 8 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a third embodiment of the invention;Fig. 9 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a fourth embodiment of the invention;Fig. 10 is a front view of a relevant portion of the clutch case in accordance with the fourth embodiment of the invention;Fig. 11 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a fifth embodiment of the invention; andFig. 12 shows cross sections of relevant portions of the clutch case and rotary drum in accordance with a sixth embodiment of the invention. - Referring to
Figs. 1 and2 , there is shown a phase-varying apparatus of the present invention for use with an automobile engine, which is integrally mounted to the engine. The apparatus is used in an engine oil atmosphere. In this apparatus, the rotation of the crankshaft is transmitted to the camshaft of the apparatus so as to vary the valve timing (that is, opening/closing timing of the intake and exhaust valves) in accord with the load and rpm of the engine. - Specifically, the phase-varying apparatus has: an outer
hollow cylinder 10 serving as a sprocket subjected to the driving force of the crankshaft of the engine; an innerhollow cylinder 20 arranged coaxial with, and rotatable relative to, theouter cylinder 10, and constituting a part of thecamshaft 2 of the apparatus, anintermediate member 30 arranged between, and in helical spline engagement with, theouter cylinder 10 andinner cylinder 20, the intermediate member is moveable in the axial direction to vary the phase of theinner cylinder 20 relative to theouter cylinder 10; and an electromagnetic brake means 40 provided on one side of theinner cylinder 20 distant from thecamshaft 2, for moving theintermediate member 30 in the axial direction. The electromagnetic brake means 40 is mounted on the cover (engine case) 8. - The
outer cylinder 10 consists of asprocket 12 having on the inner circumferential periphery thereof acircular recess 13; aninner flange plate 14 in intimate contact with one side of thesprocket 12 to defineflange engagement grooves 13A in collaboration with thecircular recess 13; and aspline case 16 being fixed between thesprocket 12 and theinner flange plate 14 by ascrew 11 and having a spline engagement section that engages theintermediate member 30. - Provided between a diametrically
large recess 13a formed near the open end of therecess 13 and a diametricallysmall recess 13b adjacent thecircular recess 13a is astepped section 13c that opposes the outer circumferential edge of aflange 24 formed on the outer circumferential surface of theinner cylinder 20, as described in detail below. - The rotational motion of the crankshaft is transmitted to the outer cylinder 10 (sprocket 12) by a chain C.
Flange engagement grooves 13A and aspline engaging section 17 of theouter cylinder 10 can be easily formed by integrating together thesprocket 12,inner flange plate 14, andspline case 16 into theouter cylinder 10 by means of coupling screws. - A male and a female
helical splines intermediate member 30. A malehelical spline 23 is provided on the outer circumferential surface of theinner cylinder 20. The female helical spline (or spline engaging section) 17 is provided on the inner circumferential surface of thespline case 16. Since the inner andouter splines intermediate member 30 are formed as opposite helical splines that spiral in the opposite directions, only a small axial movement of theintermediate member 30 can cause a large phase shift of theinner cylinder 20 relative to theouter cylinder 10. Theintermediate member 30 is provided on the outer circumferential surface thereof with a squaremale thread 31. - The electromagnetic brake means 40 has an electromagnetic clutch 42 supported by the cover (engine case) 8, a
rotary drum 44 rotatably mounted on theinner cylinder 20 via abearing 22 and engages the squaremale thread 31 of theintermediate member 30, the rotary drum subjected to the braking force of the electromagnetic clutch 42, and atorsion coil spring 46 disposed between therotary drum 44 and theouter cylinder 10. - The
electromagnetic clutch 42 is mounted on the outer circumferential surface of the boss section 8a of the cover (engine case) 8. Formed in the inner circumferential surface of the 44 is a femalesquare thread 45 such that therotary drum 44 and theintermediate member 30 can undergo relative rotations along the femalesquare thread 45 and squaremale thread 31. In other words, theintermediate member 30 can move in the axial direction while rotationally sliding along thesquare threads - The
rotary drum 44 andouter cylinder 10 are connected to each other with a twistedtorsion coil spring 46 so that when no braking force is exerted to therotary drum 44, all theouter cylinder 10,inner cylinder 20,intermediate member 30, androtary drum 44 rotate together. It is noted that thetorsion coil spring 46 coaxially extends between therotary drum 44 and outer cylinder 10 (or spline case 16), so that it contributes to the axial length of the phase-varying apparatus, but contributes to minimization of the radial dimension of the apparatus. - By controlling the electric current supplied to the electromagnetic clutch 42 or turning ON/OFF the electromagnetic clutch 42, the
intermediate member 30 can be moved in the axial direction as it rotates along thesquare threads inner cylinder 20 relative to theouter cylinder 10, which in turn regulate the opening/closing timing of the valves driven by the cam 2a of thecamshaft 2. - When the
electromagnetic clutch 42 is turned OFF (that is, de-energized), theelectromagnetic clutch 42 is located at the position shown inFig. 1 by a phantom line, where a gap S is formed between therotary drum 44 andelectromagnetic clutch 42. In this instance theouter cylinder 10 andinner cylinder 20 are rotated together in phase. As theelectromagnetic clutch 42 is turned ON, theelectromagnetic clutch 42 is moved to the right to attract therotary drum 44, thereby exerting a braking force to therotary drum 44. - This braking force causes the rotational motion of the
rotary drum 44 to be retarded relative to theouter cylinder 10. That is, theintermediate member 30 is advanced (or moved to the right inFig. 1 ) by thesquare threads outer cylinder 10, thereby changing the phase of thecamshaft 20 relative to the outer cylinder 10 (sprocket 12).. Accordingly, therotary drum 44 is retained at a position where the braking force balances out the spring force of thetorsion coil spring 46, leaving theinner cylinder 20 out of phase by a predetermined angle with respect to theouter cylinder 10. - On the other hand, as the
electromagnetic clutch 42 is turned OFF, no braking force acts on therotary drum 44 any longer, so that theintermediate member 30 is now subjected solely to the spring force of thetorsion coil spring 46, which causes theintermediate member 30 to be retracted (or moved to the left as seen inFig. 1 ) to its home position. Meanwhile the inner cylinder 20 (camshaft 2) is rotated either in the forward or backward direction with respect to the outer cylinder 10 (sprocket 12), thereby annihilating the phase difference between them. - The
circumferential flange 24 is formed on the outer circumferential surface of theinner cylinder 20 journalled in thesprocket 12. On the other hand, theflange engagement groove 13A is formed inside the circumferential inner surface of the outer cylinder 10 (sprocket 12). Theflange 24 engages with thegroove 13A. Frictionaltorque enhancement members flange 24 and the engagement face of thegrooves 13A. Thus, the frictional torque generated by theouter cylinder 10 in frictional contact with theinner cylinder 20 is increased. At the same time, rattling noises generated by theportions intermediate member 30,outer cylinder 10, andinner cylinder 20 in spline engagement with thesquare threads - As shown in
Figs. 3-5 , theelectromagnetic clutch 42 has an annularclutch case 60 having a C-shape transverse cross section with its annular opening facing thedisk face 44a of therotary drum 44, and having anelectromagnetic coil 62 accommodated in theclutch case 60. Theelectromagnetic coil 62 is fixedly resin-molded within ancircular groove 65 formed between the innercircumferential wall 63 and the outercircumferential wall 64 of theclutch case 60. - Provided on, and along the circumference of, the rear face of the
clutch case 60 are a multiplicity of projecting pins 68. Eachpin 68 engages a corresponding hole 8b formed in thecover 8. That is, theclutch case 60 is fixedly secured to the cover (engine case) 8 so as not to be rotated about the axis of thecamshaft 2 but can slide in the axial direction. - In this case, the
end face 63a of the innercircumferential wall 63 and theend face 64a of the outercircumferential wall 64 of theclutch case 60 are formed to face the opposingdisk face 44a of therotary drum 44 such that an oil film of less than 1 µm in thickness is formed between theend face 63a anddisk face 44a as well as between theend face 64a and thedisk face 44a. - That is, a multiplicity (90 for example) of oil supplying
radial grooves end face 63a of theinner wall 63 andend face 64a of the outercircumferential wall 64. In the example shown herein, theseradial grooves - Each of the
grooves Fig. 6 , and is supplied with oil from anoil sump 74 at all times. - Specifically, as shown in
Fig. 1 , anoil sump 74 is defined radially inside theclutch case 60 by thecover 8. Thisoil sump 74 is communicated with anoil passage 70 formed in thecamshaft 2 and with the space formed between theclutch case 60 and therotary drum 44. Pressurized engine oil is pumped by a pump P into theoil passage 70 of thecamshaft 2 via the oil port of the journal bearing 73 of thecamshaft 2 and theside hole 73a of thecamshaft 2. - The engine oil supplied to the
oil passage 70 is introduced into theoil sump 74 via aside hole 73b formed in theinner cylinder 20. When theelectromagnetic clutch 42 is turned off, the engine oil is discharged from theoil sump 74 via a gap between thedisk face 44a of therotary drum 44 and theclutch case 60, and lead to the front face of therotary drum 44 via anoil outlet port 80. - On the other hand, when the
electromagnetic clutch 42 is energized, thedisk face 44a of therotary drum 44 and the 60 come closer to each other. As a consequence, the engine oil is discharged from theoil sump 74 via thegrooves 66 formed in theend face 63a of the innercircumferential wall 63 and thegroove 67 formed in theend face 64a of the outercircumferential wall 64, and led to the front face of therotary drum 44 via theoil outlet port 80. - As a consequence, the
disk face 44a of therotary drum 44 and the end faces 63a and 64a of theclutch case 60 are effectively cooled by the engine oil irrespective of whether theelectromagnetic clutch 42 is energized or not. - It is noted that as the engine oil is supplied from the
oil sump 74 to thegrooves grooves 66 formed in theend face 63a of theinner wall 63 and thedisk face 44a of therotary drum 44, and between thegrooves 67 formed in theend face 64a of the outercircumferential wall 64 and thedisk face 44a of therotary disk 44. - As a result, torque can be transmitted between the
rotary drum 44 and theclutch case 60 via the oil film formed in and around therespective grooves - In the embodiment described above, a large friction coefficient µ arises between the
clutch case 60 androtary drum 44 due to the oil film formed in and around therespective grooves clutch case 60 androtary drum 44. - The present invention can further achieve the following results:
- (1) Reduction of the friction coefficient µ due to clogging of the friction member can be circumvented, since no friction member is mounted in the
radial grooves 65 of theclutch case 60; - (2) The apparatus requires a less number of components, and hence can be manufactured with less cost, since no friction member is needed; and
- (3) Frictional wear of the
clutch case 60 can be reduced even when therotary drum 44 is made of an alloy if theclutch case 60 is made of a soft steel, provided that theclutch case 60 and therotary drum 44 are made to have sufficiently different surface hardnesses. - Referring to
Fig. 7 , there is shown a second embodiment of the invention. In this embodiment, there is provided an space (hereinafter referred to as air gap (AG)) between theend face 63a of theinner wall 63 of theclutch case 60 and thedisk face 44a of therotary disk 44. Rest of the features of this embodiment are the same as those of the first embodiment. - In this embodiment, it is possible to achieve a large friction coefficient µ between the
clutch case 60 androtary drum 44 without mounting a fabric friction member between them owing to the oil film formed in and around thegrooves 67. - This embodiment can achieve the same results as the first embodiment. Furthermore, by decreasing the initial metallic conformity of the
rotary drum 44 with theclutch case 60, the air gap between therotary drum 44 andclutch case 60 can be decreased to enhance the attractive force of the electromagnetic clutch, thereby compensating for the so-called initial reduction in µ. - In this configuration, the rigidity of the
clutch case 60 can be sufficiently increased, which enables regulation and measurement of the air gap under a stable condition. - Next, a third embodiment will be described with reference to
Fig. 8 . In this embodiment theend face 64a of the outercircumferential wall 64 of theclutch case 60 is tapered and is formed with grooves 67 (not shown). The rest of the features of the third embodiment are the same as those of the second embodiment. - The third embodiment can achieve the same results as the second embodiment, since transmission of torque between the
rotary drum 44 andclutch case 60 is performed via the oil film formed in and round therespective grooves 67. - Next, the fourth embodiment of the invention will now be described with reference to
Figs. 9 and 10 . In this embodiment, theend face 64a of the outercircumferential wall 64 of theclutch case 60 is provided withgrooves 69 each formed oblique to the radius perpendicular to the axis of theinner cylinder 20 and passing through the groove. - In this embodiment, since transmission of torque between the
rotary drum 44 andclutch case 60 is performed via the oil film formed in and around therespective grooves 67 as in the second embodiment, the same results can be achieved as in the second embodiment. - Referring to
Fig. 11 , there is shown a fifth embodiment of the invention. In this embodiment, the open end of the outercircumferential wall 64 of theclutch case 60 has a two-step section 76. The end face 76a of the two-step section 76 has grooves 67 (not shown) serving as oil-flow passages. - In this embodiment also transmission of torque between the
rotary drum 44 andclutch case 60 is performed via the oil film formed in and around therespective grooves 67 as in the second embodiment, so that the same results can be achieved as in the second embodiment. - The configuration of the open end of the outer
circumferential wall 64 of theclutch case 60 that it has the two-step section 76 and the end face 76a has grooves 67 (not shown), allows a larger degree of freedom in the design of the two-step section 76 having a larger width in the radial direction, which provides better controllability of the attractive force of the electromagnetic clutch. - Referring to
Fig. 12 , there is shown a sixth embodiment of the invention in which an annulartapered section 77 is formed at the open end of the outercircumferential wall 64 of theclutch case 60 and an opposing annular taperedsection 78 is formed on thedisk face 44a of therotary drum 44, so that oil flow passages are provided in the form of the grooves 67 (not shown) in the surface of the taperedsection 77. The rest of the features of this embodiment are the same as those of the second embodiment. - In this embodiment also, transmission of torque between the
rotary drum 44 andclutch case 60 is performed via the oil film formed in and around therespective grooves 67 as in the second embodiment, so that the same results can be achieved as in the second embodiment. - Moreover, since torque is transmitted between the
rotary drum 44 andclutch case 60 via the oil film formed between the annular taperedsections electromagnetic clutch 42 is enhanced in the axial direction, and so is the torque. - Although the invention has been described and shown in the examples above as having
grooves clutch case 60, a multiplicity of grooves may be formed alternatively in thedisk face 44a of therotary drum 44, thereby forming an oil film in and around the grooves for transmitting torque between therotary drum 44 andclutch case 60.
Claims (2)
- A phase-varying apparatus for use with an automobile engine, including: an outer cylinder subjected to the rotational motion of the crankshaft of the engine; an inner cylinder connected to the camshaft for opening and closing the intake and exhaust valves of the engine and rotatable relative to the outer cylinder; and an intermediate member, disposed between the outer and inner cylinders, for transmitting the rotational motion of the outer cylinder to the inner cylinder, the intermediate member moveable in the axial direction thereof to cause a relative rotation of inner cylinder relative to the outer cylinder to thereby vary the valve timing of the intake and exhaust valves, the phase-varying apparatus characterized in that:the phase-varying apparatus comprises:an annular rotary drum coaxially disposed around the inner cylinder and connected to the intermediate member, andan electromagnetic clutch for controlling the braking force to be exerted to the rotary drum in accord with the driving condition of the engine;the electromagnetic clutch hasan annular clutch case arranged to face the rotary drum, andan electromagnetic coil for generating a braking force that acts on the rotary drum when energized so as to move the clutch case towards the rotary drum; anda multiplicity of grooves are formed in at least one of the opposing faces of the rotary drum and the clutch case, for establishing engine oil passages to form an oil film in and around the grooves in such a way that the oil film transmits a torque between the rotary drum and the clutch case.
- The phase-varying apparatus according to claim 1, wherein:the annular clutch case has an outer and an inner circumferential wall together forming a C-shape transverse cross section and a circular groove between the outer and inner circumferential walls, the circular groove adapted to accommodate therein the electromagnetic coil and facing the rotary drum,the grooves are formed in one end of the outer circumferential wall facing the rotary drum;a gap is formed between the inner circumferential wall of the clutch case and the rotary drum; andthe rotary drum and the clutch case transmits torque to each other via the oil film formed in and around the grooves.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2009/053150 WO2010095257A1 (en) | 2009-02-23 | 2009-02-23 | Phase-variable device for engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2400121A1 true EP2400121A1 (en) | 2011-12-28 |
EP2400121A4 EP2400121A4 (en) | 2012-12-05 |
EP2400121B1 EP2400121B1 (en) | 2014-07-02 |
Family
ID=42633557
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09840363.7A Not-in-force EP2400121B1 (en) | 2009-02-23 | 2009-02-23 | Phase-variable device for engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US20110297114A1 (en) |
EP (1) | EP2400121B1 (en) |
JP (1) | JP5222392B2 (en) |
KR (1) | KR101463129B1 (en) |
CN (1) | CN102325968B (en) |
WO (1) | WO2010095257A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015051789A1 (en) * | 2013-10-08 | 2015-04-16 | Schaeffler Technologies AG & Co. KG | Camshaft adjusting device |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6225750B2 (en) * | 2014-02-27 | 2017-11-08 | アイシン精機株式会社 | Valve timing control device |
DE102014009726A1 (en) * | 2014-06-28 | 2015-12-31 | Daimler Ag | Camshaft adjusting device with an electromechanical brake unit |
KR102322288B1 (en) * | 2017-06-29 | 2021-11-05 | 현대자동차주식회사 | One Way Clutch type Continuously Variable Valve Timing Device and Engine System thereby |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020038639A1 (en) * | 2000-09-25 | 2002-04-04 | Yosuke Mae | Variable valve timing apparatus |
JP2004132246A (en) * | 2002-10-10 | 2004-04-30 | Nittan Valve Co Ltd | Camshaft phase variable device in automobile engine |
WO2008015746A1 (en) * | 2006-07-31 | 2008-02-07 | Nittan Valve Co., Ltd. | Phase variable device for engine |
WO2008041282A1 (en) * | 2006-09-29 | 2008-04-10 | Nittan Valve Co., Ltd. | Engine valve controller |
WO2008072298A1 (en) * | 2006-12-11 | 2008-06-19 | Nittan Valve Co., Ltd. | Phase variable device of engine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN2072169U (en) * | 1990-06-26 | 1991-02-27 | 核工业第二研究设计院 | Centrifugal safety starting clutch |
US5097804A (en) * | 1991-04-18 | 1992-03-24 | Eaton Corporation | Phase change device |
US6530460B2 (en) * | 2001-02-22 | 2003-03-11 | The Timken Company | Front-rear and side to side torque transfer module for all-wheel drive vehicles |
JP4657500B2 (en) * | 2001-06-15 | 2011-03-23 | 日鍛バルブ株式会社 | Electromagnetic brake cooling structure of phase variable device in automotive engine |
EP1832719A4 (en) * | 2004-09-01 | 2010-10-13 | Nittan Valva | Phase varying device of engine |
JP4386823B2 (en) | 2004-11-11 | 2009-12-16 | 日鍛バルブ株式会社 | Phase variable device for automobile engine |
JP2006250098A (en) | 2005-03-14 | 2006-09-21 | Hitachi Ltd | Valve timing control device for internal combustion engine |
JP4562700B2 (en) | 2006-07-14 | 2010-10-13 | 日鍛バルブ株式会社 | Electromagnetic brake mounting structure of phase variable device in engine |
-
2009
- 2009-02-23 CN CN200980157192.4A patent/CN102325968B/en not_active Expired - Fee Related
- 2009-02-23 WO PCT/JP2009/053150 patent/WO2010095257A1/en active Application Filing
- 2009-02-23 US US13/201,794 patent/US20110297114A1/en not_active Abandoned
- 2009-02-23 EP EP09840363.7A patent/EP2400121B1/en not_active Not-in-force
- 2009-02-23 KR KR1020117016763A patent/KR101463129B1/en not_active IP Right Cessation
- 2009-02-23 JP JP2011500426A patent/JP5222392B2/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020038639A1 (en) * | 2000-09-25 | 2002-04-04 | Yosuke Mae | Variable valve timing apparatus |
JP2004132246A (en) * | 2002-10-10 | 2004-04-30 | Nittan Valve Co Ltd | Camshaft phase variable device in automobile engine |
WO2008015746A1 (en) * | 2006-07-31 | 2008-02-07 | Nittan Valve Co., Ltd. | Phase variable device for engine |
WO2008041282A1 (en) * | 2006-09-29 | 2008-04-10 | Nittan Valve Co., Ltd. | Engine valve controller |
WO2008072298A1 (en) * | 2006-12-11 | 2008-06-19 | Nittan Valve Co., Ltd. | Phase variable device of engine |
Non-Patent Citations (1)
Title |
---|
See also references of WO2010095257A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015051789A1 (en) * | 2013-10-08 | 2015-04-16 | Schaeffler Technologies AG & Co. KG | Camshaft adjusting device |
US9840947B2 (en) | 2013-10-08 | 2017-12-12 | Schaeffler Technologies AG & Co. KG | Camshaft adjusting device |
Also Published As
Publication number | Publication date |
---|---|
EP2400121B1 (en) | 2014-07-02 |
JP5222392B2 (en) | 2013-06-26 |
KR101463129B1 (en) | 2014-11-20 |
EP2400121A4 (en) | 2012-12-05 |
WO2010095257A1 (en) | 2010-08-26 |
CN102325968A (en) | 2012-01-18 |
KR20110128801A (en) | 2011-11-30 |
JPWO2010095257A1 (en) | 2012-08-16 |
US20110297114A1 (en) | 2011-12-08 |
CN102325968B (en) | 2015-07-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8418665B2 (en) | Variable phase controller for automotive engine | |
US8322319B2 (en) | Cam shaft phase variable device in engine for automobile | |
EP1403470B1 (en) | Electromagnetic brake cooling structure of phase variable device in car engine | |
US10544709B2 (en) | Sliding cam module with a bearing element and a camshaft with a sliding cam module, as well as a cover module | |
EP2400121B1 (en) | Phase-variable device for engine | |
EP2067944B1 (en) | Engine valve controller | |
EP2628910A1 (en) | Phase variable device of engine | |
EP2559868B1 (en) | Engine valve controller | |
JP4915006B2 (en) | Device for changing the control time of an internal combustion engine | |
WO2016068179A1 (en) | Valve opening/closing-timing control device | |
EP3176411B1 (en) | Valve opening and closing timing control device | |
WO2016068180A1 (en) | Valve open/close period control device | |
US7913657B2 (en) | Variable valve timing mechanism | |
JP4309440B2 (en) | Valve timing control device for internal combustion engine | |
JP5979102B2 (en) | Valve timing control device | |
JP4447564B2 (en) | Valve timing adjustment device | |
JP2009092078A (en) | Valve timing control device for internal combustion engine | |
WO2018168302A1 (en) | Variable valve device for internal combustion engine | |
WO2019171720A1 (en) | Variable valve device for internal combustion engines | |
JP2019052569A (en) | Variable valve gear of internal combustion engine and assembly method of variable valve gear | |
JP2012112349A (en) | Variable valve gear of internal combustion engine | |
JP2007247632A (en) | Valve timing adjusting device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20110824 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
DAX | Request for extension of the european patent (deleted) | ||
A4 | Supplementary search report drawn up and despatched |
Effective date: 20121107 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F01L 1/34 20060101AFI20121031BHEP Ipc: F01L 1/344 20060101ALI20121031BHEP |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F01L 1/344 20060101ALI20131212BHEP Ipc: F01L 1/34 20060101AFI20131212BHEP |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20140123 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 676059 Country of ref document: AT Kind code of ref document: T Effective date: 20140715 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602009025155 Country of ref document: DE Effective date: 20140814 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 676059 Country of ref document: AT Kind code of ref document: T Effective date: 20140702 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20140702 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141103 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141002 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141002 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141003 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141102 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602009025155 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20150407 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150223 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150223 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20160219 Year of fee payment: 8 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20160224 Year of fee payment: 8 Ref country code: GB Payment date: 20160223 Year of fee payment: 8 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20090223 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602009025155 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170223 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20171031 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170901 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170223 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140702 |