CN102325968A - Phase-variable device for engine - Google Patents
Phase-variable device for engine Download PDFInfo
- Publication number
- CN102325968A CN102325968A CN2009801571924A CN200980157192A CN102325968A CN 102325968 A CN102325968 A CN 102325968A CN 2009801571924 A CN2009801571924 A CN 2009801571924A CN 200980157192 A CN200980157192 A CN 200980157192A CN 102325968 A CN102325968 A CN 102325968A
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- rotary drum
- clutch box
- clutch
- inner cylinder
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- 230000005540 biological transmission Effects 0.000 claims abstract description 20
- 239000003921 oil Substances 0.000 claims description 33
- 230000015572 biosynthetic process Effects 0.000 claims description 10
- 239000010705 motor oil Substances 0.000 claims description 9
- 239000002783 friction material Substances 0.000 description 18
- 230000000694 effects Effects 0.000 description 11
- 239000000835 fiber Substances 0.000 description 8
- 230000007246 mechanism Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000003321 amplification Effects 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 230000002153 concerted effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 230000008569 process Effects 0.000 description 1
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- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 230000000979 retarding effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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
Abstract
Provided is a phase-variable device for an engine, which can perform the transmission of a torque between a clutch case and a rotary drum by making use of an oil film. The engine phase-variable device causes relative rotations between an outer cylinder portion (10) and an inner cylinder portion (20) by moving an intermediate member (30) axially, thereby changing the opening/closing timings of an intake valve or an exhaust valve. The engine phase-variable device comprises an annular rotary drum (44) connected to the intermediate member (30), and an electromagnetic clutch (42) for controlling a braking force on the rotary drum (44) in accordance with the running state of the engine. The electromagnetic clutch (42) includes an annular clutch case (60) arranged to face the rotary drum (44), and an electromagnetic coil (62) for generating, when powered, a braking force on the rotary drum (44). Grooves (66 and 67) are formed in the end face (63a) of the inner circumference wall (63) and in the end face (64a) of the outer circumference wall (64) of the clutch case (60), so that the transmission of a torque between the rotary drum (44) and the clutch case (60) is performed through the grooves (66 and 67) and the oil film formed therearound.
Description
Technical field
The present invention relates to braking force acted on the rotary drum, camshaft is changed with respect to the rotatable phase of sprocket wheel and make the phase variable device of the motor that the switching of valve changes opportunity by magnetic clutch.
Background technique
As this phase variable device; For example; Someone has proposed following phase variable device: the sprocket wheel with the driving force of the bent axle that transmits motor constitutes with the mode that the camshaft that constitutes active valve mechanism rotates with becoming one; Sprocket wheel and camshaft rotate synchronously, if but braking force act on the rotary drum by electromagnetic braking mechanism, then on rotary drum, produce rotational latency with respect to sprocket wheel; The related ground of the rotational latency of rotary drum therewith, the phase change with respect to sprocket wheel of camshaft (with reference to patent documentation 1).
In this phase variable device; Because in the friction material of clutch box and the slide relative portion between the rotary drum; The breach that the oil that the oil that adopted oily path in being arranged on camshaft, is arranged on the radially inner side of clutch box accumulates portion and is arranged on the inner circle wall front edge of clutch box imports usefulness imports the structure of engine oil, so can cool off the slide relative face of friction material and rotary drum.
Patent documentation 1: TOHKEMY 2002-371814 communique (with reference to the 4th page to the 6th page, Fig. 1～Fig. 4)
Summary of the invention
Invent problem to be solved
The phase variable device of patent documentation 1 record; Since by the magnetic clutch that will constitute electromagnetic braking mechanism with towards the circular clutch box of the transverse section コ font of the disc face opening of rotary drum in circumferencial direction locking, be housed in electromagnetic coil in the clutch box, be fixed on the inboard friction material retaining plate of the opening portion of clutch box and flat friction material constitutes; This flat friction material is connected with the friction material retaining plate; The internal and external peripheral wall front edge of its surface ratio clutch box is outstanding a little; Used the fiber friction material as friction material, so can be transformed into retarding torque from the attraction force that magnetic clutch produces and pass to rotary drum reliably.
But the fiber friction material if use unceasingly, then causes obstruction, produces significant μ and reduces.Therefore, when on magnetic clutch, having used the fiber friction material, be provided with restriction on the usage frequency in actual vehicle.
In addition, for the deviation of the attraction force that suppresses to produce from magnetic clutch, must precision the surface of processing fiber class friction material and the gap (air gap) of clutch box and rotary drum well.But, process the machining state that air gap is perhaps measured air gap well for precision, have no alternative but use special devices.
The present invention is the invention of making in view of the problem of above-mentioned existing technology, and its purpose is, the phase variable device of the motor of the transmission that can utilize oil film to carry out the torque between clutch box and the rotary drum is provided.
In order to solve the means of problem
In order to achieve the above object, in the phase variable device of the motor of technological scheme 1, possess: the urceolus portion of rotation that transmits the bent axle of motor; Can rotate the inner cylinder portion that the camshaft that opens and closes with the Aspirating valves that makes motor or outlet valve links with this urceolus portion relatively; Be configured between above-mentioned urceolus portion and the above-mentioned inner cylinder portion; The rotating force of above-mentioned urceolus portion is passed to the intermediate member of above-mentioned inner cylinder portion, is moving axially through making this intermediate member, make above-mentioned urceolus portion and above-mentioned inner cylinder portion between produce rotation relatively; The switching of above-mentioned Aspirating valves or outlet valve is changed opportunity; It is characterized in that possessing: be configured in above-mentioned inner cylinder portion around, the rotary drum of the ring-type that links with above-mentioned intermediate member; Correspondingly control the magnetic clutch to the braking force of above-mentioned rotary drum with the operating condition of motor, above-mentioned magnetic clutch possesses: the clutch box of the ring-type that disposes in opposite directions with above-mentioned rotary drum; When energising, make above-mentioned clutch box produce electromagnetic coil to the braking force of above-mentioned rotary drum to above-mentioned rotary drum side shifting; On at least one side's among above-mentioned rotary drum and forward surface above-mentioned clutch box or above-mentioned clutch box and the forward surface above-mentioned rotary drum forward surface; Formed the groove of the path of engine oil, through carry out the transmission of the torque between above-mentioned rotary drum and the above-mentioned clutch box at the oil film of above-mentioned groove and formation on every side thereof.
(effect) if electromagnetic coil is energized, then clutch box produces braking force by electromagnetic coil to rotary drum simultaneously to the rotary drum side shifting.At this moment, because the groove that on rotary drum and forward surface clutch box or clutch box and forward surface rotary drum, forms and formed oil film on every side, so can utilize oil film to carry out the transmission of the torque between clutch box and the rotary drum.Therefore, when between clutch box and rotary drum, carrying out the transmission of torque,, also can access high μ (friction factor) between clutch box and rotary drum even fiber friction material etc. is not installed.
In the phase variable device of the motor of technological scheme 2, make following structure: in the phase variable device of the motor of technological scheme 1 record; The clutch box of above-mentioned ring-type; Its transverse section forms the コ font; In the annular slot that surrounds by inner circle wall and periphery wall, take in above-mentioned electromagnetic coil; On above-mentioned periphery wall and forward surface above-mentioned rotary drum, form above-mentioned groove, between above-mentioned inner circle wall and above-mentioned rotary drum, form the gap, through carry out the transmission of the torque between above-mentioned rotary drum and the above-mentioned clutch box on every side at the above-mentioned groove that forms on the above-mentioned periphery wall and the oil film that forms thereof.
(effect) can be under the state that forms the gap between inner circle wall and the rotary drum when utilizing oil film to carry out the transmission of the torque between clutch box and the rotary drum, is utilized in the groove that forms on the periphery wall and the oil film that forms carries out on every side.Therefore, can easily adjust gap (air gap) between inner circle wall and the rotary drum.
The effect of invention
As from above explanation clear and definite, the phase variable device according to the motor of technological scheme 1 even fiber friction material etc. is not installed, also can access high μ between clutch box and rotary drum.
According to the phase variable device of the motor of technological scheme 2, can easily adjust the gap (air gap) between inner circle wall and the rotary drum.
Description of drawings
Fig. 1 is the longitudinal sectional view of phase variable device of expression the 1st embodiment's of the present invention motor.
Fig. 2 is the stereogram of internal structure of the phase variable device of expression motor of the present invention.
Fig. 3 is the front view of clutch box.
Fig. 4 is the sectional view along the A-A line of Fig. 3.
Fig. 5 is clutch box and the major component sectional view of rotary drum among the 1st embodiment of the present invention.
Fig. 6 is the amplification view of the groove that on clutch box, forms.
Fig. 7 is expression the 2nd embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
Fig. 8 is expression the 3rd embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
Fig. 9 is expression the 4th embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
Figure 10 is the major component front view of expression the 4th embodiment's of the present invention clutch box.
Figure 11 is expression the 5th embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
Figure 12 is expression the 6th embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
Symbol description:
10: circular urceolus portion
20: circular inner cylinder portion
30: intermediate member
42: magnetic clutch
44: rotary drum
44a: disc face
60: clutch box
62: electromagnetic coil
63: inner circle wall
63a: end face
64: periphery wall
64a: end face
66,67: groove
Embodiment
For the optimal way that carries out an invention
Below, based on a description of drawings mode of execution of the present invention.Fig. 1 is the longitudinal sectional view as the phase variable device of the of the present invention the 1st embodiment's motor; Fig. 2 is the stereogram of the internal structure of this device of expression; Fig. 3 is the front view of clutch box; Fig. 4 is the sectional view along the A-A line of Fig. 3, and Fig. 5 is clutch box and the major component sectional view of rotary drum among the 1st embodiment of the present invention, and Fig. 6 is the amplification view of the groove that on clutch box, forms; Fig. 7 is expression the 2nd embodiment's of the present invention clutch box and the major component sectional view of rotary drum; Fig. 8 is expression the 3rd embodiment's of the present invention clutch box and the major component sectional view of rotary drum, and Fig. 9 is expression the 4th embodiment's of the present invention clutch box and the major component sectional view of rotary drum, and Figure 10 is the major component front view of expression the 4th embodiment's of the present invention clutch box; Figure 11 is the 5th embodiment's of expression invention the clutch box and the major component sectional view of rotary drum, and Figure 12 representes the 6th embodiment's of the present invention clutch box and the major component sectional view of rotary drum.
In Fig. 1 and Fig. 2; The phase variable device of the motor in the present embodiment constitutes as device: for example; To be assembled on the engine for automobile and to have been carried out incorporate form and under the engine oil environment, used; The mode that the suction air valve synchronously opens and closes with the rotation with bent axle passes to camshaft with the rotation of bent axle, according to operating conditions such as the load of motor, rotating speeds is changed opportunity of switching of the suction air valve of motor simultaneously.
Specifically, the phase variable device of motor possesses: as the circular urceolus portion 10 of the sprocket wheel of the driving force of the bent axle that transmits motor; Be configured in relatively rotating the circular inner cylinder portion 20 of the slave end of the part of formation camshaft 2 epaxially with urceolus portion 10 with respect to urceolus portion 10; Carry out helical spline with urceolus portion 10 and inner cylinder portion 20 respectively and engage and be installed between urceolus portion 10 and the inner cylinder portion 20, change the intermediate member 30 of inner cylinder portion 20 moving axially with respect to the phase place of urceolus portion 10; The camshaft 2 of inner cylinder portion 20 is arranged on the non-side that sets, makes intermediate member 30 in axially movable electromagnetic braking mechanism 40, electromagnetic braking mechanism 40 is installed on the cover (engine case) 8.
Urceolus portion 10 by the chain wheel body 12 of the recess that is provided with ring-type on the inner circumference edge 13, with the side of chain wheel body 12 closely contact and and recess 13 concerted actions and be divided into the convex listrium 14 of flange engagement groove 13A and with convex listrium 14 and chain wheel body 12 fastening fixing and forming in interior week and intermediate member 30 between the spline case 16 of spline engagement portion constitute.
Between the path recess 13b of the inboard of the big footpath recess 13a of the opening side of recess 13 and recess 13, be provided with after inner cylinder portion 20 sides stated flange 24 outer periphery over against stepped part 13c.
In urceolus portion 10 (chain wheel body 12), transmit the rotation of the bent axle of motor through chain C as sprocket wheel.Symbol 11 is the fastening screw trip bolts with chain wheel body 12, convex listrium 14 and spline case 16 being fixed as one; Through constitute sprocket wheel (urceolus portion 10) by chain wheel body 12, convex listrium 14 and spline case 16; The formation of flange engagement groove 13A is easy, and the formation of the spline engagement portion 17 in the urceolus portion 10 (spline case 16) also becomes easy.
In addition, on the inner and outer circumferential surfaces of intermediate member 30, be provided with internal and external screw spline 32,33, on the outer circumferential face of inner cylinder portion 20, be provided with outer spiral spline 23.On the inner peripheral surface of spline case 16, be provided with internal thread spline 17.And, because the inside and outside spline of intermediate member 30 32,33 forms as helical splines in the other direction, so axial mobile a little through to intermediate member 30 can make inner cylinder portion 20 get greatly with respect to the phase change of urceolus portion 10.On the outer circumferential face of intermediate member 30, formed foreign side screw section 31.
In addition, rotary drum 44 is linked by the torsion-coil spring of rolling 46 with urceolus portion 10, does not act under the state on the rotary drum 44 in braking force, and urceolus portion 10, inner cylinder portion 20, intermediate member 30 and rotary drum 44 rotate with becoming one.In addition, be installed in the twist coil spring 46 between rotary drum 44 and the urceolus portion 10 (spline case 16),,, but radially becoming compact so phase variable device integral body is correspondingly extending axially because axially clamping.
And; Through controlling to the ON of magnetic clutch 42, OFF and to the energising amount of magnetic clutch 42; Intermediate member 30 rotates along square thread portion 45,31 and is moving axially simultaneously; Thus, the phase place of urceolus portion 10 and inner cylinder portion 20 changes, the switching opportunity of the valve that adjustment is undertaken by the cam 2a of camshaft 2.
That is, before making magnetic clutch 42ON when energising (non-), magnetic clutch 42 is in the position shown in the dotted line of Fig. 1, between rotary drum 44 and magnetic clutch 42, has formed gap S, and urceolus portion 10 does not have phase difference with inner cylinder portion 20, integratedly rotation.And if make magnetic clutch 42ON (energising), then magnetic clutch 42 slides and attraction rotary drum 44 to Fig. 1 dextrad, and thus, the braking force of transmitting from magnetic clutch 42 acts on the rotary drum 44.
And; On the rotary drum 44 of braking force effect, produce rotational latency with respect to urceolus portion 10; That is, intermediate member 30 relies on square thread portion 31,45 to advance (moving to Fig. 1 dextrad), relies on the internal and external screw spline 32,33 of intermediate member 30; Inner cylinder portion 20 (camshaft 2) is rotated with respect to urceolus portion 10 (chain wheel body 12), its phase change.And rotary drum 44 is maintained at the position (inner cylinder portion 20 has the position of the phase difference of regulation with respect to urceolus portion 10) of the Spring balanced of the braking force transmitted and twist coil spring 46.
On the other hand; If make magnetic clutch 42 be OFF; Then be not delivered to rotary drum 44, so the intermediate member 30 of the only elastic force effect of coil spring 46 relies on square thread portions 31,45 to retreat (moving to Fig. 1 left-hand) and become original position, during this period because of its braking force; Inner cylinder portion 20 (camshaft 2) is moving to suitable direction or counter rotation with respect to urceolus portion 10 (chain wheel body 12), its phase difference vanishing.
In addition; Outer circumferential face (and the journal surface between the chain wheel body 12) in inner cylinder portion 20 upward is provided with flange 24 at circumferencial direction; On the other hand; On the inner peripheral surface of urceolus portion 10 (chain wheel body 12), at circumferencial direction the flange engagement groove 13A of flange 24 engaging is set, between the side of the side of flange 24 and flange engagement groove 13A, clamped friction torque additional member 51,55.Thus; The friction torque of the slide relative portion between urceolus portion 10 and the inner cylinder portion 20 improves, and the generation of the strike note that the helical spline engagement portion 23,32,33,17 between intermediate member 30 and urceolus portion 10 and the inner cylinder portion 20, the tooth portion in the square thread portion 31,45 collide each other is suppressed.
Magnetic clutch 42, like Fig. 3 to shown in Figure 5, possess form transverse section コ font circularly towards the clutch box 60 of the disc face 44a of rotary drum 44 opening be housed in the electromagnetic coil 62 in the clutch box 60.Electromagnetic coil 62 is fixed in the inner circle wall 63 and the annular slot 65 between the periphery wall 64 of clutch box 60 by the resin module.
In the back side of clutch box 60, be provided with a plurality of pins 68 along its circumferencial direction is outstanding.Each sell 68 with the cover 8 sides hole 8b engage.That is, clutch box 60, be locked in be fixed under the state of circumferencial direction the cover 8 on, axially can sliding of camshaft 2, can not move to circumferencial direction but be constrained for.
At this moment; Clutch box 60; The end face 63a of its inner circle wall 63 and the end face 64a of periphery wall 64 the disc face 44a forward surface in opposite directions of conduct and rotary drum 44 respectively form; Between the end face 63a of inner circle wall 63 and the disc face 44a and between the end face 64a and disc face 44a of periphery wall 64, for example, formed the oil film below the thickness 1 μ m.
That is, on the end face 64a of the end face 63a of inner circle wall 63 and periphery wall 64, formed the groove 66,67 of the oily path of a plurality of conducts respectively, for example 90.Each groove 66,67, on the circumferencial direction of the end face 64a of the end face 63a of inner circle wall 63 and periphery wall 64, every at a distance from 4 ° of ground uniformly-spaced to dispose, along the radially formation of clutch box 60.
Each groove 66,67, as shown in Figure 6, section is a half-circle-arc shape roughly, forms width 0.5mm, degree of depth 0.15mm, accumulates portion 74 to each groove 66,67 supply engines oil from oil often.
Specifically, as shown in Figure 1 at the radially inner side of clutch box 60, is communicated with oily paths 70 in the camshaft 2, and the oil that is communicated with the space portion of clutch box 60 and rotary drum 44 accumulates portion 74 and forms by covering 8 divisions.Engine oil by pump P through the neck of camshaft 2 to the hydraulic fluid port of bearing 73 and oily path 70 force feeds of side opening 73a in camshaft 2 of camshaft 20.
Be sent to the engine oil of oily path 70, imported oil through side opening 73b and accumulate portion 74.Oil accumulates the engine oil in the portion 74, when magnetic clutch 42 non-energisings, discharges through the disc face 44a and the gap between the clutch box 60 of rotary drum 44, derives through the front face side of oily leadout hole 80 to rotary drum 44 simultaneously.
On the other hand; When magnetic clutch 42 energisings; Because the disc face 44a of rotary drum 44 and clutch box 60 are approaching each other; So oil accumulates the engine oil in the portion 74, the groove 67 that warp forms on groove 66 that forms on the end face 63a of the inner circle wall 63 of clutch box 60 and the end face 64a at periphery wall 64 is discharged, and derives through the front face side of oily leadout hole 80 to rotary drum 44 simultaneously.
Therefore, when magnetic clutch 42 non-energisings and when energising, end face 63a, the 64a of the disc face 44a of rotary drum 44 and clutch box 60 are cooled off by engine oil effectively.
In addition; If accumulate portion 74 to each groove 66,67 supply engines oil from oil; Then, spread all over each groove 66,67 and form oil film peripherally between the disc face 44a of groove 66 on the end face 63a of the inner circle wall that is formed at clutch box 60 63 and rotary drum 44 and be formed between the disc face 44a of groove 67 and rotary drum 44 on the end face 64a of periphery wall 64.
Thus, can be through the transmission of the torque between each groove 66,67 and oil film execution rotary drum 44 that forms on every side and clutch box 60.
According to present embodiment; Because transmission through the torque between each groove 66,67 and oil film execution rotary drum 44 that forms on every side and clutch box 60; Even, also can access high μ (friction factor) so between clutch box 60 and rotary drum 44, the fiber friction material is not installed.
In addition, according to present embodiment, can play the effect of following that kind.
(1), reduces so can prevent the μ that the obstruction by friction material causes owing in the annular slot 65 of clutch box 60, friction material is not installed.
(2),, can realize that cost reduces simultaneously so can reduce the part number because do not need friction material.
(3) even rotary drum 44 is made up of alloy, clutch box 60 is made up of soft iron, through mutual surface hardness difference is made certain certain value, also can suppress clutch box 60 wearing and tearing.
Then, according to Fig. 7 the 2nd embodiment of the present invention is described.Present embodiment has formed the gap S as air gap (AG) between the disc face 44a of the end face 63a of the inner circle wall 63 of clutch box 60 and rotary drum 44, other structure is identical with the 1st embodiment.
According to present embodiment; Because transmission through the torque between each groove 67 and oil film execution rotary drum 44 that forms on every side and clutch box 60; Even, also can access high μ (friction factor) so between clutch box 60 and rotary drum 44, the fiber friction material is not installed.
In addition, according to present embodiment, can play the effect same with the 1st embodiment; Simultaneously, through the initial stage break-in of being undertaken by rotary drum 44 and clutch box 60, the air gap that is produced by the initial stage break-in each other of so-called metal is reduced; Attraction force is increased, can remedy initial stage μ and reduce (torque reduction).
And then, enough high with respect to the rigidity of clutch box 60 according to present embodiment owing to making, so can under stable status, carry out the adjustment and the mensuration of air gap.
Then, according to Fig. 8 the 3rd embodiment of the present invention is described.Present embodiment forms taper with the end face 64a of the periphery wall 64 of clutch box 60, on taper end face 64a, has formed groove 67 (not shown), and other structure is identical with the 2nd embodiment.
According to present embodiment, because through carry out the transmission of the torque between rotary drum 44 and the clutch box 60 at the oil film of each groove 67 and formation on every side thereof, so can play the effect same with the 2nd embodiment.
Then, according to Fig. 9 and Figure 10 the 4th embodiment of the present invention is described.Present embodiment on the end face 64a of the periphery wall 64 of clutch box 60, has formed the groove 69 that tilts with respect to the dotted line with the axle center quadrature of inner cylinder portion 20 for oil flow, other structure is identical with the 2nd embodiment.
According to present embodiment, because through carry out the transmission of the torque between rotary drum 44 and the clutch box 60 at the oil film of each groove 69 and formation on every side thereof, so can play the effect same with the 2nd embodiment.
Then, according to Figure 11 the 5th embodiment of the present invention is described.Present embodiment is divided into two sections and form stepped part 76 with the opening side end of the periphery wall 64 of clutch box 60, on the end face 76a of stepped part 76, has formed groove 67 (not shown) for oil flow, and other structure is identical with the 2nd embodiment.
According to present embodiment, because through carry out the transmission of the torque between rotary drum 44 and the clutch box 60 at the oil film of each groove 67 and formation on every side thereof, so can play the effect same with the 2nd embodiment.
In addition; According to present embodiment; Because the opening side end of the periphery wall 64 of clutch box 60 is divided into two sections and form stepped part 76; On the end face 76a of stepped part 76, formed groove 67,, can easily control attraction force simultaneously so can improve the degrees of freedom of the width (length radially) of stepped part 76.
According to Figure 12 the 6th embodiment of the present invention is described.Present embodiment; Opening side end at the periphery wall 64 of clutch box 60 forms circular tapering 77; On the disc face 44a of rotary drum 44, form and circular tapering 78 in opposite directions, tapering 77 simultaneously; 77 the surface in the tapering has formed groove 67 (not shown) for oil flow, other structure is identical with the 2nd embodiment.
According to present embodiment, because through carry out the transmission of the torque between rotary drum 44 and the clutch box 60 at the oil film of each groove 67 and formation on every side thereof, so can play the effect same with the 2nd embodiment.
In addition, according to present embodiment because through between rotary drum 44 and clutch box 60, carrying out the transmission of torque at the oil film that forms between tapering 77 and the tapering 78, thus can make magnetic clutch 42 axially on attraction force increase and remedy torque.
In addition; In each embodiment; Structure on clutch box 60, forming groove 66,67,69 is narrated; Even but on the disc face 44a of rotary drum 44, form a plurality of grooves, also can be through the transmission of the torque between each groove of disc face 44a and oil film execution rotary drum 44 that forms on every side and clutch box 60.
Claims (2)
1. the phase variable device of a motor possesses: the urceolus portion of the rotation of the bent axle of transmission motor; Can rotate the inner cylinder portion that the camshaft that opens and closes with the Aspirating valves that makes motor or outlet valve links with this urceolus portion relatively; Be configured between above-mentioned urceolus portion and the above-mentioned inner cylinder portion; The rotating force of above-mentioned urceolus portion is passed to the intermediate member of above-mentioned inner cylinder portion; Through this intermediate member is being moved axially, make above-mentioned urceolus portion and above-mentioned inner cylinder portion between produce rotation relatively, the switching of above-mentioned Aspirating valves or outlet valve is changed opportunity; It is characterized in that
Possess: be configured in above-mentioned inner cylinder portion around, the rotary drum of the ring-type that links with above-mentioned intermediate member; Correspondingly control magnetic clutch with the operating condition of motor to the braking force of above-mentioned rotary drum,
Above-mentioned magnetic clutch possesses: the clutch box of the ring-type that disposes in opposite directions with above-mentioned rotary drum; When energising, make above-mentioned clutch box produce electromagnetic coil to the braking force of above-mentioned rotary drum to above-mentioned rotary drum side shifting,
On at least one side's among above-mentioned rotary drum and forward surface above-mentioned clutch box or above-mentioned clutch box and the forward surface above-mentioned rotary drum forward surface; Formed the groove of the path of engine oil, through carry out the transmission of the torque between above-mentioned rotary drum and the above-mentioned clutch box at the oil film of above-mentioned groove and formation on every side thereof.
2. like the phase variable device of the motor of claim 1 record, it is characterized in that,
The clutch box of above-mentioned ring-type; Its transverse section forms the コ font; In the annular slot that surrounds by inner circle wall and periphery wall, take in above-mentioned electromagnetic coil; On above-mentioned periphery wall and forward surface above-mentioned rotary drum, form above-mentioned groove, between above-mentioned inner circle wall and above-mentioned rotary drum, form the gap, through carry out the transmission of the torque between above-mentioned rotary drum and the above-mentioned clutch box on every side at the above-mentioned groove that forms on the above-mentioned periphery wall and the oil film that forms thereof.
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 (2)
| Publication Number | Publication Date |
|---|---|
| CN102325968A true CN102325968A (en) | 2012-01-18 |
| CN102325968B CN102325968B (en) | 2015-07-01 |
Family
ID=42633557
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980157192.4A Expired - Fee Related CN102325968B (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 (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105612316A (en) * | 2013-10-08 | 2016-05-25 | 舍弗勒技术股份两合公司 | Camshaft adjusting device |
| CN109026250A (en) * | 2014-02-27 | 2018-12-18 | 爱信精机株式会社 | Valve opens and closes arrangement for controlling timing |
| CN109209547A (en) * | 2017-06-29 | 2019-01-15 | 现代自动车株式会社 | One-way clutch variable valve timing apparatus and its engine system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014009726A1 (en) * | 2014-06-28 | 2015-12-31 | Daimler Ag | Camshaft adjusting device with an electromechanical brake unit |
Family Cites Families (13)
| 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 |
| JP3911982B2 (en) * | 2000-09-25 | 2007-05-09 | 日産自動車株式会社 | Variable valve timing device for internal combustion engine |
| 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 |
| JP3958665B2 (en) * | 2002-10-10 | 2007-08-15 | 日鍛バルブ株式会社 | Camshaft phase varying device for automobile engine |
| US20090260590A1 (en) * | 2004-09-01 | 2009-10-22 | Nittan Valve Co., Ltd. | 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 |
| JP4673265B2 (en) * | 2006-07-31 | 2011-04-20 | 日鍛バルブ株式会社 | Engine phase variable device |
| KR101047917B1 (en) * | 2006-09-29 | 2011-07-08 | 니탄 밸브 가부시키가이샤 | Valve control unit of engine |
| KR101273389B1 (en) * | 2006-12-11 | 2013-06-11 | 니탄 밸브 가부시키가이샤 | Phase variable device of engine |
-
2009
- 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
- 2009-02-23 CN CN200980157192.4A patent/CN102325968B/en not_active Expired - Fee Related
- 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 WO PCT/JP2009/053150 patent/WO2010095257A1/en active Application Filing
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105612316A (en) * | 2013-10-08 | 2016-05-25 | 舍弗勒技术股份两合公司 | Camshaft adjusting device |
| CN105612316B (en) * | 2013-10-08 | 2018-05-22 | 舍弗勒技术股份两合公司 | Camshaft adjustment device |
| CN109026250A (en) * | 2014-02-27 | 2018-12-18 | 爱信精机株式会社 | Valve opens and closes arrangement for controlling timing |
| CN109026250B (en) * | 2014-02-27 | 2021-01-19 | 爱信精机株式会社 | Valve opening and closing timing control apparatus |
| CN109209547A (en) * | 2017-06-29 | 2019-01-15 | 现代自动车株式会社 | One-way clutch variable valve timing apparatus and its engine system |
| CN109209547B (en) * | 2017-06-29 | 2021-11-09 | 现代自动车株式会社 | One-way clutch type variable valve timing apparatus and engine system thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2400121A4 (en) | 2012-12-05 |
| EP2400121A1 (en) | 2011-12-28 |
| WO2010095257A1 (en) | 2010-08-26 |
| JP5222392B2 (en) | 2013-06-26 |
| KR101463129B1 (en) | 2014-11-20 |
| KR20110128801A (en) | 2011-11-30 |
| JPWO2010095257A1 (en) | 2012-08-16 |
| EP2400121B1 (en) | 2014-07-02 |
| CN102325968B (en) | 2015-07-01 |
| US20110297114A1 (en) | 2011-12-08 |
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