KR20110128801A - Phase-variable device for engine - Google Patents

Abstract

[PROBLEMS] To transfer torque between clutch case and rotating drum by using oil film.
[Measures] In the phase shifting device of the engine which causes the relative rotation between the outer cylinder portion 10 and the inner cylinder portion 20 by changing the intermediate member 30 in the axial direction, and changes the opening / closing timing of the intake valve or exhaust valve. And an annular rotary drum 44 connected to the intermediate member 30, and an electromagnetic clutch 42 for controlling braking force on the rotary drum 44 according to the operating state of the engine. An inner side of the clutch case 60 is provided with an annular clutch case 60 disposed opposite to each other on the rotating drum 44 and an electromagnetic coil 62 for generating a braking force against the rotating drum 44 at the time of energization. Grooves 66 and 67 are formed in the end face 63a of the circumferential wall 63 and the end face 64a of the outer circumferential wall 64 to transfer the torque between the rotary drum 44 and the clutch case 60. (66, 67) and the oil film formed around it.

Description

Phase variable unit of engine {PHASE-VARIABLE DEVICE FOR ENGINE}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a phase shifting device of an engine that applies a braking force to a rotating drum by an electromagnetic clutch to change the rotational phase of the camshaft relative to the sprocket to change the opening and closing timing of the valve.

As this type of phase variable device, for example, the sprocket to which the driving force of the crankshaft of an engine is transmitted and the camshaft which comprises the same valve mechanism are comprised so that it may rotate, and the sprocket and the camshaft rotate synchronously, When the braking force is applied to the rotating drum by the electromagnetic brake means, it is proposed that the rotating drum loses the rotational delay with respect to the sprocket, and that the phase of the camshaft with respect to the sprocket is changed in conjunction with the rotational delay of the rotating drum (patent). See Document 1).

In this phase shifting device, the relative sliding portion between the friction material of the clutch case and the rotating drum includes an oil passage provided in the camshaft, an oil pool provided in the radially inner side of the clutch case, and an edge portion of the inner peripheral wall of the clutch case. Since the structure in which engine oil is introduced through the cut-out part for oil introduction provided is employ | adopted, the relative sliding surface of a friction material and a rotating drum can be cooled.

Patent Document 1: Japanese Patent Application Laid-Open No. 2002-371814 (see pages 4 to 6, see FIGS. 1 to 4).

(Initiation of invention)

(Tasks to be solved by the invention)

The phase variable apparatus described in patent document 1 is a clutch case which prevented rotation of the electromagnetic clutch which comprises an electromagnetic brake means in the circumferential direction by the cross-section C-shaped round ring shape which opens toward the disk surface of a rotating drum, and a clutch case. It consists of a received electromagnetic coil, a friction material holding plate fixed inside the opening of the clutch case, and a flat friction material bonded to the friction material holding plate, the surface of which slightly protrudes from the front edge of the inner and outer circumferential walls of the clutch case. Since the friction material is used, the suction force generated from the electromagnetic clutch can be converted into brake torque and transmitted reliably to the rotating drum.

However, when the fibrous friction material is used continuously, it causes clogging and a significant decrease in μ. For this reason, when the fibrous friction material is used for the electromagnetic clutch, the frequency of use in the actual vehicle is limited.

In addition, in order to suppress the deviation of the suction force generated from the electromagnetic clutch, the surface of the fibrous friction material and the gap (air gap) between the clutch case and the rotating drum must be precisely processed. However, it is inevitable to use special equipment to precisely process the air gap or to measure the processing state of the air gap.

This invention is made | formed in view of the subject of the said prior art, The objective is to provide the phase change apparatus of the engine which can transmit the torque between a clutch case and a rotating drum using an oil film.

In order to achieve the above object, in the engine variable phase apparatus according to claim 1, the outer cylinder portion to which the rotation of the crankshaft of the engine is transmitted and the camshaft which is relatively rotatable and opens and closes the intake valve or exhaust valve of the engine And an intermediate member disposed between the outer cylinder portion and the inner cylinder portion to transmit a rotational force of the outer cylinder portion to the inner cylinder portion, and between the outer cylinder portion and the inner cylinder portion by moving the intermediate member in an axial direction. A phase shifting apparatus of an engine which causes relative rotation to change opening and closing timings of the intake valves or exhaust valves, comprising: an annular rotating drum disposed around the inner cylinder portion and connected to the intermediate member, and in accordance with an operating state of the engine An electromagnetic clutch for controlling a braking force for the rotating drum, wherein the electromagnetic clutch And an annular clutch case disposed opposite to each other on the rotary drum, and an electromagnetic coil for moving the clutch case toward the rotary drum side to generate braking force for the rotary drum when energized. At least one of the opposing surfaces of the clutch case or the opposing surface of the clutch case with the rotary drum is provided with a groove forming a passage for engine oil, and the torque between the rotary drum and the clutch case is increased. The delivery was carried out through the groove and the oil film formed around the groove.

(Action) When the electromagnetic coil is energized, the clutch case moves to the rotating drum side, and a braking force is generated from the electromagnetic coil to the rotating drum. At this time, an oil film is formed in the grooves formed on the opposite surface of the rotating drum to the clutch case or on the opposite surface of the clutch case to the rotating drum, and thus an oil film is used to transfer torque between the clutch case and the rotating drum. This can be done. Therefore, when the torque is transmitted between the clutch case and the rotating drum, a high µ (friction coefficient) can be obtained without attaching a fibrous friction material or the like between the clutch case and the rotating drum.

In the phase variable device of an engine according to claim 2, in the phase variable device of the engine according to claim 1, the annular clutch case has a U-shaped cross section and is formed in the annular groove surrounded by an inner circumferential wall and an outer circumferential wall. A coil is accommodated, the groove is formed on the opposite surface of the outer circumferential wall to the rotating drum, a gap is formed between the inner circumferential wall and the rotating drum, and transfer of torque between the rotating drum and the clutch case. The configuration was carried out through the groove formed with the outer circumferential wall and the oil film formed around the groove.

(Operation) When the torque is transmitted between the clutch case and the rotating drum by using an oil film, a groove formed in the outer circumferential wall and an oil film formed around the outer circumferential wall can be performed with a gap formed between the inner circumferential wall and the rotating drum. have. For this reason, the gap (air gap) between an inner peripheral wall and a rotating drum can be adjusted easily.

As is clear from the above description, according to the phase variable apparatus of the engine according to claim 1, a high μ can be obtained even without mounting a fibrous friction material or the like between the clutch case and the rotating drum.

According to the phase variable apparatus of the engine of Claim 2, the clearance gap (air gap) between an inner peripheral wall and a rotating drum can be adjusted easily.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view of a phase variable device of an engine showing a first embodiment of the present invention.
2 is a perspective view showing the internal structure of a phase variable device of the engine according to the present invention;
3 is a front view of the clutch case;
4 is a cross-sectional view taken along line AA of FIG. 3.
Fig. 5 is a sectional view of principal parts of the clutch case and the rotating drum in the first embodiment of the present invention.
6 is an enlarged cross-sectional view of a groove formed in the clutch case;
7 is a sectional view of principal parts of a clutch case and a rotating drum, showing a second embodiment of the present invention;
8 is a sectional view of principal parts of a clutch case and a rotating drum, showing a third embodiment of the present invention;
9 is a sectional view of principal parts of a clutch case and a rotating drum, showing a fourth embodiment of the present invention;
10 is a front view of principal parts of a clutch case showing a fourth embodiment of the present invention.
Fig. 11 is a sectional view of principal parts of a clutch case and a rotating drum, showing a fifth embodiment of the present invention.
12 is a sectional view of principal parts of a clutch case and a rotating drum, showing a sixth embodiment of the present invention;

(The best mode for carrying out the invention)

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described based on drawing. 1 is a longitudinal cross-sectional view of a phase variable device of an engine which is a first embodiment of the present invention, FIG. 2 is a perspective view showing the internal structure of the device, FIG. 3 is a front view of the clutch case, and FIG. 4 is an AA line of FIG. 5 is a sectional view of an essential part of the clutch case and the rotating drum in the first embodiment of the present invention, FIG. 6 is an enlarged sectional view of a groove formed in the clutch case, and FIG. 7 is a clutch showing the second embodiment of the present invention. 8 is a sectional view of an essential part of a case and a rotating drum, FIG. 8 is a sectional view of an essential part of a clutch case and a rotating drum, and FIG. 9 is a sectional view of a main part of a clutch case and a rotating drum, showing a fourth embodiment of the present invention; Fig. 10 is a front view of the main part of the clutch case showing the fourth embodiment of the present invention, Fig. 11 is a sectional view of the main part of the clutch case and the rotating drum showing the fifth embodiment of the present invention. It is sectional drawing of the principal part of the clutch case and rotating drum which show 6th Embodiment of this invention.

1 and 2, the phase variable apparatus of the engine in this embodiment is used, for example, in an engine oil atmosphere in an integrated form in an automobile engine, and the intake / exhaust valve is opened and closed in synchronization with the rotation of the crankshaft. It is configured as a device for transmitting the rotation of the crankshaft to the camshaft so as to change the timing of opening and closing of the intake / exhaust valve of the engine in accordance with the operating state such as the load of the engine and the rotational speed thereof.

Specifically, the phase shifting device of the engine is disposed coaxially with the outer annular outer cylinder portion 10 and the outer cylinder portion 10, which is a sprocket to which the driving force of the crankshaft of the engine is transmitted, and can be rotated relative to the outer cylinder portion 10, A helical spline meshes with the circular annular inner cylinder portion 20 and the outer cylinder portion 10 and the inner cylinder portion 20 on the driven side constituting a part of the cam shaft 2, respectively, so that the outer cylinder portion 10 and the inner cylinder portion 20 are fitted. It is interposed between and is provided in the intermediate member 30 which moves axially and changes the phase of the inner cylinder part 20 with respect to the outer cylinder part 10, and the camshaft 2 non-arrangement side of the inner cylinder part 20, It is comprised by the electromagnetic brake means 40 which moves the intermediate member 30 to an axial direction, and the electromagnetic brake means 40 is attached to the cover (engine case) 8. As shown in FIG.

The outer cylinder portion 10 is in close contact with the sprocket main body 12 provided with a ring-shaped recess 13 at the inner circumferential edge and the side surface of the sprocket main body 12, and cooperates with the recess 13 to form a flange engaging groove 13A. The inner flange plate 14 constituting the () and the inner flange plate 14 is fastened together to the sprocket body 12 and fixed, and the spline engaging portion with the intermediate member 30 is composed of the spline case 16 formed in the inner circumference. It is.

Between the large diameter recessed part 13a of the opening side of the recessed part 13, and the small diameter recessed part 13b inside the recessed part 13, the flange 24 of the inner cylinder part 20 side mentioned later A step portion 13c facing the outer circumferential edge is provided.

Rotation of the crankshaft of the engine is transmitted to the outer cylinder part 10 (sprocket body 12) which is a sprocket through the chain C. As shown in FIG. Reference numeral 11 denotes a fastening screw for fixedly unifying the sprocket body 12, the inner flange plate 14, and the spline case 16, and the sprocket body 12, the inner flange plate 14, and the spline case 16. By forming the outer cylinder part 10, 13 A of flange engagement grooves are easy to form, and the formation of the spline engaging part 17 in the outer cylinder part 10 (spline case 16) is also easy.

Male and female helical splines 32 and 33 are provided on the inner and outer circumferential surfaces of the intermediate member 30, and male helical splines 23 are provided on the outer circumferential surface of the inner cylinder portion 20. The female helical spline 17 is provided on the inner circumferential surface of the spline case 16. And since the splines 32 and 33 inside and outside the intermediate member 30 are formed as a reverse helical spline, the inner cylinder part 20 with respect to the outer cylinder part 10 by the slight movement to the axial direction of the intermediate member 30 is carried out. You can change the phase of) greatly. The male screw part 31 is formed in the outer peripheral surface of the intermediate member 30. As shown in FIG.

The electromagnetic brake means 40 is rotatably supported by the inner cylinder part 20 by the electromagnetic clutch 42 supported by the cover (engine case) 8 and the bearing 22, and of the intermediate member 30 The male thread part 31 is screwed together, and the torsion coil spring 46 interposed between the rotating drum 44 and the outer drum part 10 and the rotating drum 44 to which the braking force of the electromagnetic clutch 42 is transmitted is 46 ) Is configured.

The electromagnetic clutch 42 is attached to the outer peripheral side of the boss portion 8a of the cover 8. A female angle screw portion 45 is provided on the inner circumferential surface of the rotary drum 44, and the rotary drum 44 and the intermediate member 30 can be rotated relative to the circumferential direction along the angle screw portions 45 and 31. As shown in FIG. That is, the intermediate member 30 can move in the axial direction while rotating along the angled screw portions 45 and 31.

In addition, the rotating drum 44 and the outer cylinder portion 10 are connected by a torsion coil spring 46 wound up, and in a state where the braking force does not act on the rotating drum 44, the outer cylinder portion 10 and the inner cylinder portion 20 ), The intermediate member 30 and the rotating drum 44 are integrally rotated. In addition, since the torsion coil spring 46 interposed between the rotary drum 44 and the outer cylinder portion 10 (spline case 16) is interposed in the axial direction, the entire phase variable device extends in the axial direction by that amount, It is compact in the radial direction.

Then, by controlling the ON / OFF of the electromagnetic clutch 42 and the energization amount to the electromagnetic clutch 42, the intermediate member 30 moves in the axial direction while rotating along the angled screw portions 45 and 31, thereby. The phase of the outer cylinder part 10 and the inner cylinder part 20 changes, and the timing of opening and closing of the valve by the cam 2a of the camshaft 2 is adjusted.

That is, before turning ON the electromagnetic clutch 42 (at the time of non-energization), the electromagnetic clutch 42 is in the position shown by the virtual line of FIG. 1, and has a clearance gap between the rotating drum 44 and the electromagnetic clutch 42. S) is formed, and the outer cylinder part 10 and the inner cylinder part 20 are integrally rotating without phase difference. Then, when the electromagnetic clutch 42 is turned on (energized), the electromagnetic clutch 42 slides in the rightward direction in FIG. 1 to attract the rotating drum 44, whereby the rotating clutch 44 has the electromagnetic clutch 42. The braking force transmitted from it acts.

Then, a rotational delay with respect to the outer cylinder portion 10 occurs in the rotating drum 44 to which the braking force is applied, that is, the intermediate member 30 is advanced by the threaded portions 31 and 45 (moves in the right direction in FIG. 1). The inner cylinder part 20 (camshaft 2) is rotated with respect to the outer cylinder part 10 (sprocket main body 12) by the inner and outer helical splines 32 and 33 of the intermediate member 30, and the phase changes. . Then, the rotary drum 44 is maintained at a position where the braking force transmitted and the spring force of the torsion coil spring 46 are balanced (inner cylinder portion 20 has a predetermined phase difference with respect to outer cylinder portion 10).

On the other hand, when the electromagnetic clutch 42 is turned OFF, the braking force is not transmitted to the rotating drum 44, so that the intermediate member 30, in which only the spring force of the coil spring 46 acts, is an angle screw portion 31, 45. Retreat (move to the left in Fig. 1) to the original position, during which the inner cylinder portion 20 (camshaft 2) moves forward or relative to the outer cylinder portion 10 (sprocket body 12). Rotation in the reverse direction eliminates the phase difference.

In addition, a flange 24 is provided on an outer circumferential surface of the inner cylinder portion 20 (journal surface with the sprocket main body 12), and a flange 24 hangs on an inner circumferential surface of the outer cylinder portion 10 (sprocket body 12). 13A of flange engagement grooves to be fitted are provided, and friction torque adding members 51 and 55 are interposed between the side surface of the flange 24 and the side surface of the flange engagement groove 13A. As a result, the frictional torque of the relative sliding portion between the outer cylinder portion 10 and the inner cylinder portion 20 increases, and the helical spline engaging portion 23 between the intermediate member 30 and the outer cylinder portion 10 and the inner cylinder portion 20 is increased. 32, 33, 17 and generation | occurrence | production of the rattling sound which the teeth hit in the each screw part 31 and 45 are suppressed.

As shown in FIGS. 3 to 5, the electromagnetic clutch 42 is formed in a cross-sectional U-shaped circular ring shape and opened toward the disk surface 44a of the rotating drum 44, and the clutch. The electromagnetic coil 62 accommodated in the case 60 is comprised. The electromagnetic coil 62 is fixed by the resin mold in the annular groove 65 between the inner circumferential wall 63 and the outer circumferential wall 64 of the clutch case 60.

A plurality of pins 68 protrude from the rear side of the clutch case 60 along the circumferential direction thereof. Each pin 68 is engaged with the hole 8b on the cover 8 side. That is, the clutch case 60 is fixed to the cover 8 in a state of being prevented from rotating in the circumferential direction and can slide in the axial direction of the cam shaft 2, but is constrained so as not to move in the circumferential direction.

At this time, the clutch case 60 is formed as an opposing surface in which the end surface 63a of the inner circumferential wall 63 and the end surface 64a of the outer circumferential wall 64 oppose each other with the disk surface 44a of the rotary drum 44, respectively. For example, between an end surface 63a of the inner circumferential wall 63 and the disk surface 44a and between the end face 64a of the outer circumferential wall 64 and the disk surface 44a, an oil film having a thickness of 1 μm or less, for example, Formed.

That is, in the end face 63a of the inner circumferential wall 63 and the end face 64a of the outer circumferential wall 64, a plurality of grooves 66 and 67 as oil passages are formed, for example, 90 pieces. The grooves 66 and 67 are arranged at equal intervals every 4 ° in the circumferential direction of the end face 63a of the inner circumferential wall 63 and the end face 64a of the outer circumferential wall 64, and the diameter of the clutch case 60 is reduced. It is formed along the direction.

As shown in Fig. 6, each of the grooves 66 and 67 has a substantially semi-circular shape in cross section, and is formed with a width of 0.5 mm and a depth of 0.15 mm, and each groove 66 and 67 has an oil pool portion ( Engine oil is always supplied from 74).

Specifically, in the radially inner side of the clutch case 60, as shown in FIG. 1, it communicates with the oil passage 70 in the camshaft 2, and also the clutch case 60 and the rotating drum 44 The oil holding part 74 which communicates with the space part of this structure is comprised by the cover 8. As shown in FIG. In the oil passage 70 in the cam shaft 2, the engine oil is pumped to the pump P through the oil port of the journal bearing 73 of the cam shaft 2 and the side hole 73a of the cam shaft 2. It is pushed by.

The engine oil supplied to the oil passage 70 is introduced into the oil chamber 74 through the side hole 73b. The engine oil in the oil chamber 74 is discharged through the gap between the disk surface 44a of the rotary drum 44 and the clutch case 60 when the electromagnetic clutch 42 is not energized, and the oil is drawn out. It is led to the front side of the rotating drum 44 through the hole 80.

On the other hand, when the electromagnetic clutch 42 is energized, the disk surface 44a of the rotary drum 44 and the clutch case 60 are close to each other, so that the engine oil in the oil pool 74 is the clutch case 60. It is discharged through the groove 66 formed on the end surface 63a of the inner circumferential wall 63 of the inner wall 63 and the groove 67 formed on the end surface 64a of the outer circumferential wall 64 of the inner circumferential wall 63, and the rotary drum through the oil extraction hole 80. It is derived to the front side of 44.

For this reason, at the time of non-energization and energization of the electromagnetic clutch 42, the disk surface 44a of the rotating drum 44 and the end surfaces 63a, 64a of the clutch case 60 are cooled effectively by engine oil.

In addition, when the engine oil is supplied to the grooves 66 and 67 from the oil holding portion 74, the groove 66 and the rotating drum 44 formed on the end surface 63a of the inner circumferential wall 63 of the clutch case 60. Between the grooves 67 and 67 and the periphery of the grooves 67 formed in the end face 64a of the outer circumferential wall 64 and the disc face 44a of the rotary drum 44. An oil film is formed over.

Thereby, transmission of the torque between the rotating drum 44 and the clutch case 60 can be performed through the oil film formed in each groove 66 and 67 and its periphery.

According to this embodiment, since the transmission of torque between the rotary drum 44 and the clutch case 60 is performed through the grooves 66 and 67 and the oil film formed around the clutch case 60, A high mu (friction coefficient) can be obtained even if no fibrous friction material is attached between the rotating drums 44.

In addition, according to this embodiment, the following effects can be obtained.

(1) Since the friction material is not mounted in the annular groove 65 of the clutch case 60, it is possible to prevent the fall due to the blockage of the friction material.

(2) By making the friction material unnecessary, the number of parts can be reduced and the cost can be reduced.

(3) Even if the rotary drum 44 is made of an alloy and the clutch case 60 is made of soft iron, wear of the clutch case 60 can be suppressed by setting the difference in surface hardness of each other to a certain value. .

Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment, the gap S as the air gap AG is formed between the end face 63a of the inner circumferential wall 63 of the clutch case 60 and the disk face 44a of the rotary drum 44. The other configuration is the same as in the first embodiment.

According to this embodiment, since the transmission of torque between the rotary drum 44 and the clutch case 60 is performed through each groove 67 and the oil film formed around the clutch case 60 and the rotary drum, A high µ (friction coefficient) can be obtained even if no fibrous friction material is provided between the 44 parts.

In addition, according to this embodiment, the same effects as in the first embodiment can be obtained, and the air gap due to the initial affinity by the rotating drum 44 and the clutch case 60 and the so-called affinity between metals is reduced. By increasing the suction force, the initial μ reduction (torque reduction) can be compensated for.

In addition, according to this embodiment, since the rigidity with respect to the clutch case 60 can be made high enough, adjustment and measurement of an air gap can be performed in a stable state.

Next, a third embodiment of the present invention will be described with reference to FIG. In this embodiment, the end face 64a of the outer circumferential wall 64 of the clutch case 60 is tapered, and the groove 67 (not shown) is formed on the tapered end face 64a. Is the same as in the second embodiment.

According to this embodiment, since the transmission of torque between the rotary drum 44 and the clutch case 60 is carried out through each groove 67 and the oil film formed around it, the same effect as in the second embodiment is achieved. You can get it.

Next, a fourth embodiment of the present invention will be described with reference to FIGS. 9 and 10. In this embodiment, grooves 69 inclined with respect to an imaginary line orthogonal to the axis of the inner cylinder portion 20 are formed on the end face 64a of the outer circumferential wall 64 of the clutch case 60 as an oil flow. The other configuration is the same as in the second embodiment.

According to this embodiment, since the transmission of torque between the rotating drum 44 and the clutch case 60 is performed through the oil film formed around each groove 69 and its surroundings, the same effects as in the second embodiment are obtained. You can get it.

Next, a fifth embodiment of the present invention will be described with reference to FIG. In this embodiment, the step side portion 76 is formed by dividing the opening side end portion of the outer circumferential wall 64 of the clutch case 60 into two stages, and the groove 67 is formed at the end surface 76a of the step portion 76. (Not shown) was formed as an oil flow, and the other structure is the same as that of 2nd Example.

According to this embodiment, since the transmission of torque between the rotary drum 44 and the clutch case 60 is carried out through each groove 67 and the oil film formed around it, the same effect as in the second embodiment is achieved. You can get it.

In addition, according to the present embodiment, the step side portion 76 is formed by dividing the opening side end portion of the outer circumferential wall 64 of the clutch case 60 in two stages, and a groove is formed on the end surface 76a of the step portion 76. Since 67 is formed, the degree of freedom of the width (length in the radial direction) of the stepped portion 76 can be increased, and the suction force can be easily controlled.

A sixth embodiment of the present invention will be described with reference to FIG. In the present embodiment, a round annular tapered portion 77 is formed at the opening side end of the outer circumferential wall 64 of the clutch case 60, and the taper 44 is tapered on the disk surface 44a of the rotating drum 44. A round annular tapered portion 78 is formed to face the portion 77, and a groove 67 (not shown) is formed on the surface of the tapered portion 77 as an oil flow. Same as the embodiment.

According to this embodiment, since the transmission of torque between the rotary drum 44 and the clutch case 60 is carried out through each groove 67 and the oil film formed around it, the same effect as in the second embodiment is achieved. You can get it.

Further, according to the present embodiment, since the torque is transmitted between the rotary drum 44 and the clutch case 60 through the oil film formed between the taper portion 77 and the taper portion 78, the electromagnetic clutch 42 The suction force in the axial direction can be increased to compensate for the torque.

In addition, in each embodiment, although forming grooves 66, 67, and 69 in the clutch case 60 was described, even if a plurality of grooves are formed in the disk surface 44a of the rotating drum 44, the rotating drum Transmission of torque between the 44 and clutch cases 60 can be performed through oil grooves formed around the grooves and the periphery of the disk surface 44a.

10 Round ring-shaped outer cylinder
20 Round ring inner cylinder
30 intermediate members
42 electronic clutch
44 rotary drum
44a disk surface
60 clutch case
62 electronic coil
63 inner wall
63a end face
64 outer walls
64a end face
66, 67 home

Claims (2)

An outer cylinder portion to which rotation of the crankshaft of the engine is transmitted, an inner cylinder portion which is relatively rotatable to the outer cylinder portion, and connected to a cam shaft for opening and closing an intake valve or exhaust valve of the engine, and disposed between the outer cylinder portion and the inner cylinder portion, And an intermediate member for transmitting the rotational force of the inner cylinder portion, and moving the intermediate member in the axial direction to generate a relative rotation between the outer cylinder portion and the inner cylinder portion, thereby changing the opening and closing timing of the intake valve or exhaust valve. In the phase variable device of the engine,
An annular rotating drum disposed around the inner cylinder portion and connected to the intermediate member, and an electromagnetic clutch for controlling a braking force for the rotating drum according to an operating state of the engine,
The electromagnetic clutch,
An annular clutch case disposed opposite to each other on the rotating drum, and an electromagnetic coil for moving the clutch case to the rotating drum side to generate braking force for the rotating drum when energized;
A groove forming a passage for engine oil is formed on at least one of the opposing surfaces of the rotary drum and the opposing surface of the clutch case or the opposing surface of the clutch case, and the rotary drum and the A phase shifting device for an engine, characterized in that the transmission of torque between clutch cases is carried out through the groove and an oil film formed around the groove. The method of claim 1,
The annular clutch case has a U-shaped cross section, the electromagnetic coil is accommodated in an annular groove surrounded by an inner circumferential wall and an outer circumferential wall, and the groove is formed on an opposite surface of the outer circumferential wall to the rotating drum. A gap is formed between the inner circumferential wall and the rotating drum, and the torque is transmitted between the rotating drum and the clutch case through the groove formed in the outer circumferential wall and an oil film formed around the outer circumferential wall. Phase variable device of the engine.

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