WO2017183149A1

WO2017183149A1 - Variable phase device for vehicular engine

Info

Publication number: WO2017183149A1
Application number: PCT/JP2016/062606
Authority: WO
Inventors: 正昭新納
Original assignee: 日鍛バルブ株式会社
Priority date: 2016-04-21
Filing date: 2016-04-21
Publication date: 2017-10-26
Also published as: DE112016006774T5; JPWO2017183149A1

Abstract

The purpose of the present invention is to provide a variable phase device having a short axial length, capable of achieving fine variable phase adjustment, and exhibiting excellent responsiveness. The device is for changing phase between a driving-side outer cylinder section and a driven-side inner cylinder section that are coaxially arranged with each other. The device is a variable phase device that utilizes either: an electromagnetic brake driving system equipped with an intermediate member (30) engaged via helical splines with the inner/outer cylinder sections, a return spring supported on the inner cylinder section in such a manner as to return a rotary drum (44) engaged via a thread with the intermediate member (30) to an initial position thereof, and an electromagnetic clutch (40) for applying a braking force to a rotary drum (44); or a hydraulic driving system equipped with a return spring for returning an integrated vane rotor (210) with the inner cylinder section to an initial position thereof and a pump (P) for supplying a working fluid to hydraulic chambers (116a, 116b) partitioned by the vane rotor (210). The return spring consists of a spiral coil spring in which spiral spring parts (81, 85) are integrated together while being arranged parallel to each other in an axial direction.

Description

自動車用エンジンにおける位相可変装置Phase variable device for automobile engine

　本発明は、クランクシャフトの駆動力が伝達されるスプロケットを備えた駆動側の円環状外筒部に対し、カムシャフトに延びる従動側の円環状内筒部が同軸状に回動可能に組み付けられ、内筒部に支承された回転ドラムと外筒部間に復帰ばねを介装し、回転ドラムを電磁クラッチで制動する電磁ブレーキ駆動方式、または内筒部に一体化したベーンロータと外筒部間に復帰ばねを介装し、ベーンロータを油圧で回動させる油圧駆動方式によって、外筒部と内筒部間の位相を変えるように構成された、自動車用エンジンにおける位相可変装置に関する。 According to the present invention, a driven annular inner tube portion extending to a camshaft is rotatably and coaxially assembled to a drive-side annular outer tube portion provided with a sprocket to which a crankshaft driving force is transmitted. An electromagnetic brake drive system in which a return spring is interposed between the rotating drum supported on the inner cylinder and the outer cylinder, and the rotating drum is braked by an electromagnetic clutch, or between the vane rotor integrated with the inner cylinder and the outer cylinder The present invention relates to a phase variable device in an automobile engine configured to change a phase between an outer cylinder part and an inner cylinder part by a hydraulic drive system in which a return spring is interposed and a vane rotor is rotated hydraulically.

　詳しくは、内筒部および外筒部にそれぞれヘリカルスプライン係合する中間部材を軸方向に移動させることで、外筒部（クランクシャフト）に対する内筒部（カムシャフト）の位相が変わる構造で、内筒部に回転可能に支承され、かつ中間部材に螺合して外筒部と同軸状に配置された回転ドラムと、前記外筒部との間に、復帰ばねが介装されるとともに、電磁クラッチを介して前記回転ドラムに電磁ブレーキ（制動力）が作用するように構成された、電磁ブレーキ駆動方式の位相可変装置、
　または、内筒部に一体化したベーンロータを外筒部に対し周方向に回動させることで、外筒部（クランクシャフト）に対する内筒部（カムシャフト）の位相が変わる構造で、外筒部の内側に形成された凹部を周方向に遅角油圧室と進角油圧室に区画するベーンロータと、前記外筒部との間に、復帰ばねが介装されるとともに、油圧ポンプを介して前記遅角油圧室と進角油圧室に作動油が供給されるように構成された、油圧駆動方式の位相可変装置に関する。 Specifically, the structure is such that the phase of the inner cylinder part (camshaft) with respect to the outer cylinder part (crankshaft) changes by moving the intermediate member that engages the helical spline to the inner cylinder part and the outer cylinder part in the axial direction. A return spring is interposed between the rotating drum that is rotatably supported by the inner cylinder portion and is screwed to the intermediate member and arranged coaxially with the outer cylinder portion, and the outer cylinder portion, An electromagnetic brake drive type phase variable device configured such that an electromagnetic brake (braking force) acts on the rotating drum via an electromagnetic clutch;
Alternatively, by rotating the vane rotor integrated with the inner cylinder part in the circumferential direction with respect to the outer cylinder part, the phase of the inner cylinder part (camshaft) with respect to the outer cylinder part (crankshaft) changes, and the outer cylinder part A return spring is interposed between the outer cylinder portion and a vane rotor that divides a recess formed on the inner side into a retarded hydraulic chamber and an advanced hydraulic chamber in the circumferential direction, and the hydraulic pump is used to The present invention relates to a hydraulically driven phase variable device configured to supply hydraulic oil to a retarded hydraulic chamber and an advanced hydraulic chamber.

　この種の位相可変装置としては、例えば、下記特許文献１が知られている。これは、電磁ブレーキ駆動方式の位相可変装置で、図１５に示すように、エンジンのクランクシャフトの駆動力が伝達されるスプロケット１２を一体化した外筒部１０の内周に、カムシャフト２に延びる従動側の内筒部２０が同軸状に回動可能に組み付けられ、外筒部１０と内筒部２０間には、両者１０，２０にそれぞれヘリカルスプライン係合し、軸方向に移動して両者１０，２０間、即ちクランクシャフトとカムシャフト２間の位相を変える中間部材３０が介装されている。外筒部１０におけるスプロケット１２と反対側には、雌角ねじ部４５を介して中間部材３０に螺合しかつ軸受け２２を介して内筒部２０に回転可能に支承された回転ドラム４４が、外筒部１０と対向して設けられている。回転ドラム４４と外筒部１０間には、「捩りコイルばね」で構成された復帰ばね４６が介装され、回転ドラム４４には、エンジンケース８に支持された電磁クラッチ４０によって制動力が作用するように構成されている。符号３２，３３は、内外のヘリカルスプライン係合部、符号３１は、中間部材３０に設けた雄角ねじ部である。 As this type of phase variable device, for example, the following Patent Document 1 is known. This is an electromagnetic brake drive phase varying device, as shown in FIG. 15, on the camshaft 2 on the inner periphery of the outer cylindrical portion 10 integrated with the sprocket 12 to which the driving force of the crankshaft of the engine is transmitted. The extended inner cylinder part 20 on the driven side is assembled so as to be rotatable coaxially, and between the outer cylinder part 10 and the inner cylinder part 20, both are engaged by helical splines and moved in the axial direction. An intermediate member 30 that changes the phase between the two

shafts

10 and 20, that is, between the crankshaft and the camshaft 2 is interposed. On the opposite side of the sprocket 12 in the outer cylindrical portion 10, there is a rotating drum 44 that is screwed into the intermediate member 30 via a female screw portion 45 and rotatably supported on the inner cylindrical portion 20 via a bearing 22. It is provided to face the outer cylinder portion 10. A return spring 46 composed of a “torsion coil spring” is interposed between the rotary drum 44 and the outer cylinder portion 10, and a braking force is applied to the rotary drum 44 by the electromagnetic clutch 40 supported by the engine case 8. Is configured to do.

Reference numerals

32 and 33 are inner and outer helical spline engaging portions, and reference numeral 31 is a male screw portion provided on the intermediate member 30.

　そして、電磁クラッチ４０のＯＮ／ＯＦＦ制御により、電磁クラッチ４０の制動力が回転ドラム５に作用し、復帰ばね(捩りコイルばね)４６が巻き上げられ、中間部材３０が角ねじ部３１，４５によって回動しながら前進（図１５右方向に移動）し、ヘリカルスプライン係合部３２、３３によって外筒部１０（スプロケット１２）と内筒部２０（カムシャフト２）間の位相が変わるようになっている。特に、外筒部１０と内筒部２０間に介装する中間部材３０の内外周面には、逆ヘリカルスプライン係合部３２，３３を設けたので、中間部材３０の軸方向への移動量に対し、外筒部１０と内筒部２０間の位相、即ちクランクシャフトとカムシャフト２間の位相を大きく変えることができる。 Then, by the ON / OFF control of the electromagnetic clutch 40, the braking force of the electromagnetic clutch 40 acts on the rotary drum 5, the return spring (torsion coil spring) 46 is wound up, and the intermediate member 30 is rotated by the

square screw portions

31, 45. It moves forward (moves to the right in FIG. 15) while moving, and the phase between the outer cylinder part 10 (sprocket 12) and the inner cylinder part 20 (camshaft 2) is changed by the helical

spline engaging parts

32, 33. Yes. In particular, since the reverse helical

spline engaging portions

32 and 33 are provided on the inner and outer peripheral surfaces of the intermediate member 30 interposed between the outer cylinder portion 10 and the inner cylinder portion 20, the amount of movement of the intermediate member 30 in the axial direction is provided. On the other hand, the phase between the outer cylinder portion 10 and the inner cylinder portion 20, that is, the phase between the crankshaft and the camshaft 2 can be greatly changed.

　また、復帰ばね４６は、線材コイルが軸方向に連続する「捩りコイルばね」で構成されて、断面円形のばね線材の全長が長い分、ばね定数が比較的小さい。したがって、線材コイルは変形し易いが、電磁クラッチ４０の制動力が回転ドラム４４に作用して、コイルばね４６が巻き上げられる際、各線材コイルが均等に縮径するため、各線材コイルが互いに接触することはない。即ち、ヒステリシス（コイルばねに発生する、巻上げと巻き戻しの際の捩りトルクの差）が小さい。 Further, the return spring 46 is constituted by a “torsion coil spring” in which wire coils are continuous in the axial direction, and the spring constant having a circular cross section is long, so that the spring constant is relatively small. Therefore, the wire coils are easily deformed, but when the braking force of the electromagnetic clutch 40 acts on the rotating drum 44 and the coil spring 46 is wound up, the diameters of the wire coils are uniformly reduced, so that the wire coils come into contact with each other. Never do. That is, the hysteresis (difference in torsional torque generated in the coil spring during winding and unwinding) is small.

　そして、回転ドラム４４に作用する制動トルク（捩りコイルばね４６に作用する捩じりトルク）の大きさを縦軸、外筒部１０に対する回転ドラム４４の回動角度（捩りコイルばね４６の捩じり角度）を横軸として、復帰ばね（捩りコイルばね）４６の捩りトルク特性を図で示すと、図１６に示すように、右肩上がりの比較的緩やかな傾斜の直線Ａとなる。この図から、捩りコイルばね４６に作用する捩じりトルクは、「ばね」が巻上げられる際は右肩上がりに上昇し、巻き戻される際はほぼ同じように左肩上がりに下降し、ヒステリシスが小さいことがわかる。 The magnitude of the braking torque acting on the rotating drum 44 (torsional torque acting on the torsion coil spring 46) is the vertical axis, and the rotation angle of the rotating drum 44 relative to the outer cylinder portion 10 (twisting of the torsion coil spring 46). When the torsional torque characteristic of the return spring (torsion coil spring) 46 is shown in the figure with the horizontal axis as the horizontal axis, as shown in FIG. From this figure, the torsional torque acting on the torsion coil spring 46 rises to the right shoulder when the “spring” is wound up, and falls to the left shoulder in the same manner when the “spring” is wound up, and the hysteresis is small. I understand that.

　さらに、この図からわかるように、直線Ａの傾斜、即ち、外筒部１０に対する回転ドラム４４の所定回動角度（捩りコイルばね４６の所定捩じり角度）に対する捩りトルク (以下、これを単位捩りトルクという) ΔＴ/Δθが比較的小さいので、それだけきめ細かい位相可変調整ができる。 Further, as can be seen from this figure, the torsional torque に対する (hereinafter referred to as a unit) with respect to the inclination of the straight line A, that is, the predetermined rotation angle of the rotating drum 44 with respect to the outer cylinder portion 10 (the predetermined torsion angle of the torsion coil spring 46). Since ΔT / Δθ (referred to torsion torque) is relatively small, fine phase variable adjustment can be made accordingly.

　また、電磁クラッチ４０により回転ドラム４４の回転が制動されて、「復帰ばね」が巻上げを開始する際の、復帰ばねに作用する捩りトルクを「復帰ばね」の設定トルクというが、回転ドラム４４と外筒部１０間に介装された復帰ばね４６は、予め僅かに巻き上げられて所定の設定トルクが作用する形態にセットされている。即ち、電磁クラッチ４０をＯＮさせない状態では、復帰ばね４６の設定トルク（捩りトルク）相当、例えば、中間部材３０が回転ドラム４４に当接する軸方向所定位置（初期位置）に付勢保持（図１５左方向に付勢保持）されて、外筒部１０，中間部材３０，内筒部２０およびカムシャフト２が一体となって回転し、即ち、外筒部１０と内筒部２０は位相差なく一体に回転できる。 The torsional torque that acts on the return spring when the rotation of the rotary drum 44 is braked by the electromagnetic clutch 40 and the “return spring” starts to wind is referred to as the set torque of the “return spring”. The return spring 46 interposed between the outer cylinder portions 10 is set in a form in which a predetermined set torque acts by being slightly wound up in advance. That is, in a state where the electromagnetic clutch 40 is not turned on, the biasing is held at a predetermined position (initial position) in the axial direction corresponding to the set torque (torsional torque) of the return spring 46, for example, the intermediate member 30 abuts the rotating drum 44 (FIG. The outer cylinder part 10, the intermediate member 30, the inner cylinder part 20, and the camshaft 2 rotate together, that is, the outer cylinder part 10 and the inner cylinder part 20 have no phase difference. Can rotate together.

　そして、位相可変制御では、設定トルク以上の制動トルクを回転ドラム４４に作用させる、即ち、復帰ばね（捩りコイルばね）４６に設定トルク以上の捩りトルクを作用させるが、ばね定数がもともと小さい「捩りコイルばね」では、図１６の符号Ｔ１で示すように、それほど高くはない比較的低い値が設定トルクとして設定される。 In the variable phase control, a braking torque greater than the set torque is applied to the rotating drum 44, that is, a torsion torque greater than the set torque is applied to the return spring (torsion coil spring) 46. In the “coil spring”, a relatively low value that is not so high is set as the set torque, as indicated by reference numeral T1 in FIG.

　一方、特許文献２の実施例には、特許文献１と同様の電磁ブレーキ駆動方式の位相可変装置であるが、図１７に示すように、回転ドラム５と外筒部（スプロケット１）間に介装する復帰ばね６として、「渦巻きばね」を用いた構造が記載されている。 On the other hand, the example of Patent Document 2 is an electromagnetic brake drive type phase variable device similar to Patent Document 1, but as shown in FIG. 17, it is interposed between the rotating drum 5 and the outer cylinder part (sprocket 1). As the return spring 6 to be worn, a structure using a “spiral spring” is described.

　「渦巻きばね」は、断面矩形状の帯状のばね線材が同一平面上を渦巻き状に旋回する形態の「ばね」であり、ばね線材が渦巻き状に旋回する回数、即ち線材コイルの巻き数が制限されて、ばね線材の全長が「捩りコイルばね」に比べて短い。したがって、「捩りコイルばね」に比べて、ばね定数が大きく、線材コイルはそれだけ変形しにくい。なお、ばね線材が旋回するにつれ中心から遠ざかるか、または中心に近づく曲線を「渦巻き」と定義する。 A “spiral spring” is a “spring” in which a strip-shaped spring wire with a rectangular cross-section swirls on the same plane spirally, and the number of turns of the spring wire spirally, that is, the number of turns of the wire coil is limited. Thus, the overall length of the spring wire is shorter than that of the “torsion coil spring”. Therefore, the spring constant is larger than that of the “torsion coil spring”, and the wire coil is not easily deformed accordingly. A curve that moves away from the center or approaches the center as the spring wire turns is defined as “spiral”.

　そして、「渦巻きばね」６の捩じりトルク特性は、図１８に示すように、右肩上がりの急傾斜の直線Ｂとなり、直線Ｂの傾斜、即ち、単位捩りトルクΔＴ/Δθが大きいので、それだけ粗い位相可変調整しかできない。 As shown in FIG. 18, the torsional torque characteristic of the “spiral spring” 6 is a straight line B with a steep upward slope, and the inclination of the straight line B, that is, the unit torsion torque ΔT / Δθ is large. Only coarse phase variable adjustment is possible.

　また、電磁クラッチ４の制動力が回転ドラム５に作用すると、「渦巻きばね」を構成する各線材コイルが均一には変形（縮径）せず、特に、外側の線材コイルほど変形量（縮径量）が大きく、線材コイル同士が接触しやすい。即ち、ヒステリシス（渦巻きばねに発生する、巻上げと巻き戻しの際の捩りトルクの差）が大きくなり易い。 Further, when the braking force of the electromagnetic clutch 4 acts on the rotary drum 5, the wire coils constituting the “spiral spring” do not deform (reduced diameter) uniformly. The amount) is large and the wire coils are easy to contact each other. That is, hysteresis (difference in torsional torque during winding and unwinding that occurs in the spiral spring) tends to increase.

　また、復帰ばね６として、ヒステリシスの大きい「渦巻きばね」を用いた位相可変装置（図１７参照）において、正確な位相可変調整を行うには、できるだけヒステリシスの影響を受けない範囲での使用に限られることから、図１８の符号Ｔ２で示されるように、「捩りコイルばね」の設定トルクＴ１よりも低い値が設定トルクとして設定される。 Further, in a phase variable device using a “spiral spring” having a large hysteresis as the return spring 6 (see FIG. 17), in order to perform accurate phase variable adjustment, it is limited to use within a range that is not affected by hysteresis as much as possible. Therefore, as indicated by reference numeral T2 in FIG. 18, a value lower than the set torque T1 of the “torsion coil spring” is set as the set torque.

　また、下記特許文献３には、クランクシャフトの駆動力が伝達されるスプロケット１２を備えた駆動側の外筒部であるハウジング１１に対し、カムシャフト２０に延びる従動側の内筒部であるベーンロータ２１が同軸状に回動可能に組み付けられ、ベーンロータ２１を外筒部（ハウジング１１）に対し周方向に回動させることで、外筒部（クランクシャフト）に対する内筒部（カムシャフト）の位相が変わる、油圧駆動方式の位相可変装置が記載されている。 Further, in Patent Document 3 below, a vane rotor that is a driven inner cylinder portion that extends to the camshaft 20 with respect to a housing 11 that is a drive side outer cylinder portion provided with a sprocket 12 to which the driving force of the crankshaft is transmitted. 21 is rotatably assembled coaxially, and the vane rotor 21 is rotated in the circumferential direction with respect to the outer cylinder part (housing 11), so that the phase of the inner cylinder part (camshaft) with respect to the outer cylinder part (crankshaft). A hydraulically driven phase variable device is described that changes.

　詳しくは、外筒部（ハウジング１１）の内側に形成された周方向四箇所の凹部それぞれを、周方向に遅角油圧室４１，４２，４３，４４と進角油圧室５１，５２，５３，５４に区画するベーンロータ２１と、ハウジング１１（のフロントプレート１５）との間に、復帰ばね（捩りコイルばね）１８が介装されるとともに、遅角油圧室と進角油圧室には、油圧ポンプ１を介して作動油がそれぞれ供給される。 Specifically, the four recessed portions formed in the circumferential direction on the inner side of the outer cylinder portion (housing 11) are respectively connected to the retard

hydraulic chambers

41, 42, 43, 44 and the advanced hydraulic chambers 51, 52, 53, circumferentially. A return spring (torsion coil spring) 18 is interposed between the vane rotor 21 partitioned into 54 and the housing 11 (front plate 15 thereof), and a hydraulic pump is provided in the retard hydraulic chamber and the advanced hydraulic chamber. The hydraulic oil is supplied through 1.

　そして、遅角油圧室４１，４２，４３，４４と進角油圧室５１，５２，５３，５４への作動油の給排制御により生じる、遅角油圧室と進角油圧室間の圧力差によって、ベーンロータ２１に生じる外筒部１１に対する回転遅れに連係して、外筒部（ハウジング１１）と内筒部（カムシャフト）間の位相が変わるようになっている。 Then, due to the pressure difference between the retarded hydraulic chamber and the advanced hydraulic chamber generated by the hydraulic oil supply / discharge control to the retarded

hydraulic chambers

41, 42, 43, 44 and the advanced hydraulic chambers 51, 52, 53, 54. The phase between the outer cylinder part (housing 11) and the inner cylinder part (camshaft) is changed in association with the rotation delay with respect to the outer cylinder part 11 generated in the vane rotor 21.

特開2002-364314号JP 2002-364314 A 特開平7-26917号JP 7-26917 A 特開2007-138730号JP 2007-138730

　特許文献１では、回転ドラム４４と外筒部１０（スプロケット１２）間に介装された復帰ばね４６が、軸方向の寸法が大きい「捩りコイルばね」で構成されているため、回転ドラム４４と外筒部１０（スプロケット１２）間がそれだけ大きく離間し、位相可変装置が軸方向に長くなる、という第１の問題がある。 In Patent Document 1, the return spring 46 interposed between the rotary drum 44 and the outer cylinder portion 10 (sprocket 12) is configured by a “torsion coil spring” having a large axial dimension. There is a first problem that the outer cylinder portion 10 (sprocket 12) is far away from the outer cylinder portion 10 (sprocket 12) and the phase variable device becomes longer in the axial direction.

　また、「捩りコイルばね」の捩りトルク特性は、図１６に示すように、その傾斜が緩やかな直線Ａで示され、きめ細かい位相可変調整ができるが、ばね定数が小さいという「捩りコイルばね」の特性上、設定トルクＴ１はある程度低めとならざるを得ず、電磁クラッチ４０をＯＦＦにした後の位相可変の高い応答性を求めるメーカーの最新のニーズに応えることが難しい、という第２の問題もある。 Further, as shown in FIG. 16, the torsional torque characteristic of the “torsion coil spring” is indicated by a straight line A having a gentle slope, and fine phase variable adjustment can be performed, but the “torsion coil spring” has a small spring constant. Due to the characteristics, the set torque T1 must be reduced to some extent, and there is also a second problem that it is difficult to meet the latest needs of manufacturers seeking high responsiveness with variable phase after the electromagnetic clutch 40 is turned off. is there.

　なお、「コイルばね」の線材コイル数を少なくすれば、軸方向の長さが短くなるとともに、ばね定数も上がり、捩りトルク特性Ａの傾斜も急となるため、設定トルクＴ１の値を上げることができるが、ばねの耐久性が著しく低下し、復帰ばねとしては利用できない。 If the number of wire coils of the “coil spring” is reduced, the axial length is shortened, the spring constant is increased, and the torsional torque characteristic A is steeply inclined. Therefore, the value of the set torque T1 is increased. However, the durability of the spring is significantly reduced and it cannot be used as a return spring.

　一方、特許文献２に記載されている「渦巻きばね」は、確かに、「捩りコイルばね」と比べて、軸方向の寸法が小さい分、回転ドラム５と外筒部（スプロケット１）を接近させて配置でき、この結果、位相可変装置を軸方向に短縮できる。 On the other hand, the “spiral spring” described in Patent Document 2 certainly brings the rotating drum 5 and the outer cylinder portion (sprocket 1) closer to each other because the axial dimension is smaller than that of the “torsion coil spring”. As a result, the phase varying device can be shortened in the axial direction.

　しかし、「渦巻きばね」の捩じりトルク特性は、前記したように、急傾斜の右肩上がりで、しかもヒステリシスの大きな直線Ｂ(図１８参照）で、設定トルクＴ２は、「捩りコイルばね」の設定トルクＴ１よりもさらに低いことから、前記した第２の問題には対応できない。 However, as described above, the torsional torque characteristic of the “spiral spring” is a straight line B (see FIG. 18) with a steeply rising right shoulder and a large hysteresis, and the set torque T2 is “torsion coil spring”. Therefore, the second problem cannot be dealt with.

　なお、「渦巻きばね」を構成する線材コイルの間隔を大きくすれば、線材コイル同士は接触しにくくなって、ヒステリシスは低下する。しかし、「渦巻きばね」全体の外径が大きくなって、位相可変装置が径方向に拡大してしまう。このため、復帰ばね４６として、「渦巻きばね」をそのまま採用することは、到底考えられない。 In addition, if the space | interval of the wire rod coil which comprises a "spiral spring" is enlarged, wire rod coils will become difficult to contact and hysteresis will fall. However, the outer diameter of the entire “spiral spring” increases, and the phase variable device expands in the radial direction. For this reason, it is unlikely that the “spiral spring” is used as the return spring 46 as it is.

　また、特許文献１，２（電磁ブレーキ駆動方式の位相可変装置）において提示した前記第１，第２の問題は、特許文献３（油圧駆動方式の位相可変装置）においても、同様にいえることである。 Further, the first and second problems presented in Patent Documents 1 and 2 (electromagnetic brake drive type phase variable device) can be said similarly in Patent Document 3 (hydraulic drive type phase variable device). is there.

　そこで、発明者は、電磁ブレーキ駆動方式では、回転ドラムと外筒部との間（油圧駆動方式では、ベーンロータと外筒部との間）に介装する復帰ばねの形態として、軸方向の寸法が小さい「渦巻きばね」の形態を前程として、「捩りコイルばね」のようにヒステリシスが小さく、かつ「捩りコイルばね」よりも大きな設定トルクを確保できる新たな形態について検討した。 Therefore, the inventor has determined that the dimension in the axial direction is a form of a return spring interposed between the rotating drum and the outer cylinder part in the electromagnetic brake driving system (between the vane rotor and the outer cylinder part in the hydraulic driving system). With the “spiral spring” in the form of a small spring, a new form that has a small hysteresis like the “torsion coil spring” and that can ensure a larger set torque than the “torsion coil spring” was studied.

　まず、ばね定数の大きな「渦巻きばね」に発生するヒステリシスの要因である線材コイル同士の接触に注目した。「渦巻きばね」では、捩り角度（図１８の横軸）が増えると、線材コイルが径方向に大きく縮もうとして、内外の線材コイル同士が接触することで、ヒステリシスが発生するが、「渦巻きばね」の線材コイル同士の接触を回避できる形態であれば、大きな設定トルクを設定できる、と考えた。 First, attention was paid to the contact between wire coils, which is a factor of hysteresis that occurs in a “spiral spring” having a large spring constant. In the “spiral spring”, when the torsion angle (horizontal axis in FIG. 18) increases, the wire coil tends to shrink greatly in the radial direction, and hysteresis occurs due to contact between the inner and outer wire coils. If it is the form which can avoid the contact of wire rod coils of ", I thought that big setting torque can be set.

　そして、発明者は、「渦巻きばね」について捩りトルク試験を何度も行い、そのデータを詳細に検討することで、渦巻状に１回以上旋回する線材コイルの平均直径Dm、同線材コイルの巻き数N、同線材コイルの捩り角度θ、同線材コイルの径方向の収縮量ΔDmには、
　ΔDm=Dm×［1-N/(N＋θ/360)］という相関関係があることを見出した。 Then, the inventor conducted torsion torque tests on the “spiral spring” many times and examined the data in detail, so that the average diameter Dm of the wire coil swirled at least once in a spiral shape, the winding of the wire coil The number N, the twist angle θ of the wire coil, and the amount of shrinkage ΔDm in the radial direction of the wire coil are:
It has been found that there is a correlation of ΔDm = Dm × [1-N / (N + θ / 360)].

　そして、この相関関係によれば、ヒステリシスの発生を抑制するには、線材コイルの径方向の収縮量ΔDmを小さくすればよく、そのためには、線材コイルの平均直径Dmを小さくするか、または線材コイルの巻き数Nを増やせばよい。 According to this correlation, in order to suppress the occurrence of hysteresis, it is only necessary to reduce the amount of contraction ΔDm in the radial direction of the wire coil. To that end, the average diameter Dm of the wire coil is reduced or the wire rod is reduced. It is only necessary to increase the number of turns N of the coil.

　しかし、線材コイルの平均直径Dmを小さくすると、内外の線材コイル間の隙間が狭くなって、線材コイル同士が接触し易くなるため、採用できない。一方、線材コイルの巻き数Nを増やすと、「渦巻きばね」の外径が大きくなり、限界がある。 However, if the average diameter Dm of the wire coils is reduced, the gap between the inner and outer wire coils becomes narrower and the wire coils can easily come into contact with each other. On the other hand, increasing the number N of turns of the wire coil increases the outer diameter of the “spiral spring”, which has a limit.

　そこで、発明者は、「渦巻きばね」の外径を大きくすることなく、線材コイルの巻き数Nを増やすには、「渦巻きばね」を軸方向に並設一体化する、即ち、ばね線材が渦巻状に旋回する渦巻きばね部を「捩りコイルばね」のように軸方向に並設一体化した形態とすればよい、と考えた。 In order to increase the number N of windings of the wire coil without increasing the outer diameter of the “spiral spring”, the inventor integrates the “spiral spring” side by side in the axial direction. It was thought that the spiral spring part swirling in the shape of the coil may be configured to be integrated in the axial direction like a “torsion coil spring”.

　詳しくは、ばね線材の全長が短いため、ばね定数が比較的大きく、かつヒステリシスが大きいが、軸方向の寸法の短い「渦巻きばね」の形態と、ばね線材の全長が長いため、ばね定数が小さく、かつヒステリシスが小さいが、軸方向の寸法の長い「捩りコイルばね」の形態との双方を備えた、従来にはない全く新たな「渦巻きコイルばね」の形態を考えた。 Specifically, the spring constant is relatively large and the hysteresis is large because the total length of the spring wire is short, but the spring constant is small because the length of the “spiral spring” is short and the total length of the spring wire is long. In addition, an entirely new “spiral coil spring” that has both low hysteresis and a long axial dimension “torsion coil spring” has been considered.

　そして、この新たな「渦巻きコイルばね」を実際に試作し、軸方向の寸法，ばね定数，耐久性，ヒステリシス，単位捩りトルクΔＴ/Δθ，設定トルクなどの「復帰ばね」としての特性を検証した結果、「捩りコイルばね」よりも、軸方向の寸法が小さく、ばね定数が大きく、大きな設定トルクを設定できるという点で、従来の「捩りコイルばね」よりも優れ、一方、渦巻きばねよりも、ばね定数が小さく、耐久性に優れ、ヒステリシスも小さく、単位捩りトルクΔＴ/Δθが小さく、きめ細かな位相可変調整ができ、しかも大きな設定トルクを設定できるという点で、従来の「渦巻きばね」よりも優れていることが確認されたことを受けて、今回の特許出願に至ったものである。 This new “spiral coil spring” was actually prototyped, and its characteristics as a “return spring” such as axial dimensions, spring constant, durability, hysteresis, unit torsion torque ΔT / Δθ, and set torque were verified. As a result, it is superior to the conventional “torsion coil spring” in that the axial dimension is smaller than that of the “torsion coil spring”, the spring constant is large, and a large set torque can be set. Smaller spring constant, better durability, smaller hysteresis, smaller unit torsion torque ΔT / Δθ, fine phase variable adjustment, and larger setting torque than conventional “spiral spring” The application for this patent was made after it was confirmed that it was superior.

　本発明は、前記した従来技術の問題点に鑑みてなされたもので、その目的は、電磁ブレーキ駆動方式では、回転ドラムと外筒部間に介装する「復帰ばね」として、油圧駆動方式では、ベーンロータと外筒部間に介装する「復帰ばね」として、それぞれ「渦巻きコイルばね」を用いることで、装置の軸方向の長さを短縮できるとともに、きめ細かな位相可変調整ができる、応答性に優れた自動車用エンジンにおける位相可変装置を提供することにある。 The present invention has been made in view of the above-described problems of the prior art, and the purpose of the electromagnetic brake drive system is as a “return spring” interposed between the rotating drum and the outer cylinder portion, and in the hydraulic drive system. The use of a “coil spring” as a “return spring” interposed between the vane rotor and the outer cylinder part reduces the length of the device in the axial direction and enables fine phase variable adjustment. An object of the present invention is to provide a phase variable device in an automobile engine that is excellent in the above.

　前記目的を達成するために、本発明の第１の実施形態は、
　クランクシャフトの駆動力が伝達されるスプロケットを備えた円環状外筒部と、前記外筒部に対し同軸状に回動可能に組み付けられ、動弁機構を構成するカムシャフトに延びる従動側の内筒部と、前記外筒部と内筒部にそれぞれヘリカルスプライン係合して外筒部と内筒部間に配設され、軸方向に移動して外筒部に対する内筒部の位相を変える中間部材と、前記内筒部に回転可能に支承された回転ドラムと、前記回転ドラムと軸方向に正対する位置に設けられ、前記回転ドラムに制動力を作用させる円環状の電磁クラッチと、前記回転ドラムと前記外筒部間に介装された復帰ばねと、を備え、
　前記制動力によって、前記回転ドラムに生じる前記外筒部に対する回転遅れに連係して、前記外筒部と前記内筒部間の位相が変わる自動車用エンジンにおける位相可変装置において、
　前記復帰ばねは、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部が軸方向に接近するように並設一体化された渦巻きコイルばねで構成されたことを特徴とする。 In order to achieve the above object, the first embodiment of the present invention provides:
An annular outer cylinder portion having a sprocket to which the driving force of the crankshaft is transmitted, and an inner side of a driven side that is rotatably mounted coaxially with respect to the outer cylinder portion and extends to a camshaft constituting a valve operating mechanism. Helical spline engagement with the cylindrical portion, the outer cylindrical portion, and the inner cylindrical portion, respectively, is disposed between the outer cylindrical portion and the inner cylindrical portion, and moves in the axial direction to change the phase of the inner cylindrical portion with respect to the outer cylindrical portion. An intermediate member, a rotating drum rotatably supported by the inner cylinder portion, an annular electromagnetic clutch provided at a position facing the rotating drum in an axial direction, and applying a braking force to the rotating drum; A return spring interposed between the rotating drum and the outer cylinder portion,
In the phase variable device in the automobile engine, the phase between the outer cylinder part and the inner cylinder part changes in association with the rotation delay with respect to the outer cylinder part generated in the rotary drum by the braking force.
The return spring is formed of a spiral coil spring that is integrated in parallel so that a plurality of spiral spring portions in which a spring wire is spirally swung on the same plane approach in the axial direction.

　（作用）回転ドラムと外筒部間に介装される「渦巻きコイルばね」は、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部を軸方向に接近するように並設一体化した形態で、多数の線材コイルが軸方向に連続する形態である「捩りコイルばね」と比べて、軸方向の寸法が短くなる分、回転ドラムと外筒部を接近させて配置することで、位相可変装置の軸方向の長さが短くなる。 (Operation) The “spiral coil spring” interposed between the rotating drum and the outer cylinder portion is arranged in parallel so that a plurality of spiral spring portions in which the spring wire turns in a spiral shape on the same plane are approached in the axial direction. Compared to the “torsion coil spring” in which a large number of wire coils are continuous in the axial direction, the rotating drum and the outer cylinder portion are arranged closer to each other because the axial dimension is shorter. The axial length of the phase varying device is shortened.

　また、「渦巻きばね」は、ばね線材が同一平面上に渦巻状に旋回する形態で、線材コイルの巻き数には制約があり、ばね線材の全長が「捩りコイルばね」に比べて短い。このため、「渦巻きばね」は、ばね定数が大きく、捩り荷重に対し内外の線材コイルが均一に変形せず、線材コイル同士の接触によるヒステリシスが大きい。 Also, the “spiral spring” is a form in which the spring wire is spirally swung on the same plane, and the number of turns of the wire coil is limited, and the total length of the spring wire is shorter than that of the “torsion coil spring”. For this reason, the “spiral spring” has a large spring constant, the inner and outer wire coils are not uniformly deformed with respect to the torsional load, and the hysteresis due to the contact between the wire coils is large.

　一方、「渦巻きコイルばね」は、ばね線材が同一平面上に渦巻状に旋回する渦巻きばね部が複数、軸方向に接近するように並設された形態で、ばね線材が同一平面上に渦巻状に旋回するだけの形態である「渦巻きばね」よりも線材コイルの巻き数が多く、ばね線材の全長がそれだけ長い。このため、「渦巻きばね」と比較し、ばね定数が小さく、長期の使用に対しての耐久性に優れる。さらに、「捩りコイルばね」の特性「捩り荷重に対し各線材コイルが半径方向にそれぞれ均等に縮径する」と同じように、軸方向に並設された複数の渦巻きばね部が捩り荷重に対しそれぞれ縮径する分、各渦巻きばね部を構成する線材コイルにおける縮径量がそれぞれ減少し、それだけ線材コイル同士が接触しにくく、ヒステリシスが小さい。 On the other hand, the “spiral coil spring” is a form in which a plurality of spiral spring portions in which the spring wire turns spirally on the same plane are arranged side by side so as to approach the axial direction, and the spring wire is spirally arranged on the same plane. The number of windings of the wire coil is larger than that of the “spiral spring” that is simply swirled, and the total length of the spring wire is much longer. For this reason, compared with a "spiral spring", a spring constant is small and it is excellent in durability with respect to long-term use. In addition, as in the “torsion coil spring” characteristic “each wire coil is uniformly reduced in diameter in the radial direction with respect to the torsion load”, a plurality of spiral springs arranged in parallel in the axial direction are resistant to the torsion load. As the diameter is reduced, the amount of diameter reduction in the wire coil constituting each spiral spring portion is reduced, the wire coils are less likely to contact each other, and the hysteresis is small.

　この結果、「渦巻きコイルばね」の捩じりトルク特性は、図５の符号Ｃに示すように、「捩りコイルばね」の捩じりトルク特性を示す直線Ａ（図１６参照）よりも急傾斜で、一方、「渦巻きばね」の捩じりトルク特性を示す直線Ｂ（図１８参照）よりも緩傾斜で、「捩りコイルばね」や「渦巻きばね」よりもヒステリシスが小さく、かつ高い設定トルクＴ３の設定が可能な、右肩上がりの直線Ｃとなる。 As a result, the torsional torque characteristics of the “spiral coil spring” are steeper than the straight line A (see FIG. 16) indicating the torsional torque characteristics of the “torsion coil spring”, as indicated by reference numeral C in FIG. On the other hand, the set torque T3 is lower than the straight line B (see FIG. 18) indicating the torsion torque characteristics of the “spiral spring”, has a smaller hysteresis than the “torsion coil spring” and the “spiral spring”, and has a higher set torque T3. This is a straight line C that rises to the right.

　特に、「渦巻きコイルばね」の捩じりトルク特性を示す直線Ｃは、単位捩りトルクΔＴ/Δθが小さいという点で、「捩りコイルばね」の捩じりトルク特性Ａ(図１６)に近く、したがって、「捩りコイルばね」を復帰ばねとして採用する特許文献１ほどではないが、比較的きめ細かな位相可変調整ができる。 In particular, the straight line C indicating the torsion torque characteristic of the “spiral coil spring” is close to the torsion torque characteristic A (FIG. 16) of the “torsion coil spring” in that the unit torsion torque ΔT / Δθ is small. Therefore, although not as much as in Patent Document 1, which employs a “torsion coil spring” as a return spring, relatively fine phase variable adjustment can be performed.

　また、図５に示すように、従来の「捩りコイルばね」や「渦巻きばね」で得られる設定トルクＴ１，Ｔ２（図１６，１８参照）よりも高い設定トルクＴ３を設定できることから、電磁クラッチＯＦＦ後、復帰ばねが元の初期状態に戻るまでの位相可変がスピーディとなる分、位相可変調整の際の応答性が良好となる。 Further, as shown in FIG. 5, since the set torque T3 higher than the set torques T1 and T2 (see FIGS. 16 and 18) obtained by the conventional “torsion coil spring” and “spiral spring” can be set, the electromagnetic clutch is turned off. After that, the phase response until the return spring returns to the original initial state becomes speedy, and the response at the time of phase variable adjustment is improved.

　本発明の第２の実施形態は、本発明の第１の実施形態において、
　軸方向に互いに接近する前記渦巻きばね部は、各渦巻きばね部をそれぞれ構成する線材コイル同士が線材コイル延在方向に対し僅かに軸方向に傾斜するばね線材の共有旋回領域を介して一体化されたことを特徴とする。 The second embodiment of the present invention is the same as the first embodiment of the present invention.
The spiral spring portions that are close to each other in the axial direction are integrated via a shared swirl region of spring wire rods in which the wire coils constituting the spiral spring portions are slightly inclined in the axial direction with respect to the wire coil extending direction. It is characterized by that.

　(作用)　渦巻きコイルばねが巻き上げられる際、ばね線材の共有旋回領域を介して渦巻きばね部の線材コイルに捩りトルクが伝達されるが、互いに接近する渦巻きばね部の線材コイル同士は、線材コイル延在方向に対し大きく屈曲する共有旋回領域を介して連続するのではなく、線材コイル延在方向に対し僅かに軸方向に傾斜して滑らかに連続するばね線材の共有旋回領域を介して連続するので、渦巻きばね部同士を接続するばね線材の共有旋回領域に不測の応力が発生したり、応力が集中したりすることもなく、複数の渦巻きばね部に捩りトルクが等しく伝達される。 (Operation) When the spiral coil spring is wound up, the torsional torque is transmitted to the wire coil of the spiral spring part through the shared swirl region of the spring wire. Rather than continuing through a shared swirl region that bends greatly with respect to the current direction, it continues through a shared swirl region of the spring wire that is smoothly inclined with a slight inclination in the axial direction with respect to the wire coil extending direction. The torsional torque is equally transmitted to the plurality of spiral spring portions without any unexpected stress being generated or concentrated in the shared swirl region of the spring wire connecting the spiral spring portions.

　本発明の第３の実施形態は、本発明の第１または第２の実施形態において、
　前記内筒部の外周には、前記中間部材とヘリカルスプライン係合する前記回転ドラムの円筒軸が配設され、前記円筒軸の外周に、円環状に形成された前記電磁クラッチが配設されたことを特徴とする。 The third embodiment of the present invention is the same as the first or second embodiment of the present invention.
A cylindrical shaft of the rotating drum that engages with the intermediate member in a helical spline is disposed on the outer periphery of the inner cylinder portion, and the electromagnetic clutch formed in an annular shape is disposed on the outer periphery of the cylindrical shaft. It is characterized by that.

　（作用）内筒部の前端部外周の軸方向後方に回転ドラムおよび電磁クラッチが同軸状に配置（図１参照）されることで、内筒部前端部の軸方向前方に電磁クラッチを配置する従来構造（図１５参照)と比べて、内筒部前端部の軸方向前方に電磁クラッチが突出しない分、位相可変装置の軸方向の長さを短くできる。 (Operation) The rotating drum and the electromagnetic clutch are coaxially disposed on the axially rearward side of the outer periphery of the front end portion of the inner cylindrical portion (see FIG. 1), whereby the electromagnetic clutch is disposed in front of the inner cylindrical portion front end portion in the axial direction. Compared with the conventional structure (see FIG. 15), the length of the phase variable device in the axial direction can be shortened by the amount that the electromagnetic clutch does not protrude forward in the axial direction of the front end portion of the inner cylinder.

　なお、「渦巻きコイルばね」の具体的な形態としては、例えば、第４，第５の実施形態に示すように、渦巻きばね部を軸方向に２段並設（第１，第２の渦巻きばね部を軸方向に並設）した形態、第６，第７の実施形態に示すように、渦巻きばね部を軸方向に３段並設（第１，第２，第３の渦巻きばね部を軸方向に並設）した形態が考えられる。 In addition, as a specific form of the “spiral coil spring”, for example, as shown in the fourth and fifth embodiments, the spiral spring portions are arranged in two stages in the axial direction (first and second spiral springs). As shown in the sixth and seventh embodiments, the spiral spring portions are arranged in three stages in the axial direction (the first, second, and third spiral spring portions are pivoted). It is possible to consider a form that is arranged in parallel in the direction.

　即ち、本発明の第４の実施形態(図３，４参照）は、本発明の第２の実施形態において、
　前記渦巻きコイルばね８０は、外筒部側固定端８２ａが設けられ前記外筒部１０の回転方向と逆方向に旋回する最小径コイル８２の周りに渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１と、回転ドラム側固定端８６ｃが設けられ前記外筒部１０の回転方向に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１，８５の最大径コイル８３，８７同士がばね線材ｗの共有旋回領域８８を介して連続することを特徴とする。 That is, the fourth embodiment of the present invention (see FIGS. 3 and 4) is the same as the second embodiment of the present invention.
The spiral coil spring 80 is a first coil in which a spring wire w is swirled around a minimum diameter coil 82 provided with an outer tube portion side fixed end 82a and swirling in a direction opposite to the rotation direction of the outer tube portion 10. A spiral spring part 81, a second spiral spring part 85 provided with a rotating drum side fixed end 86c and having a spring wire w swirled around a minimum diameter coil 86 swirling in the rotation direction of the outer cylinder part 10; Are arranged so as to be separated from each other by a minute distance in the axial direction, and the maximum diameter coils 83 and 87 of the first and second

spiral spring portions

81 and 85 are continuously connected via the common swirl region 88 of the spring wire w. It is characterized by doing.

本発明の第５の実施形態(図６，７参照)は、本発明の第２の実施形態において、
　前記渦巻きコイルばね８０Ａは、外筒部側固定端８３ａが設けられ前記外筒部１０の回転方向と逆方向に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、回転ドラム側固定端８７ｂが設けられ前記外筒部１０の回転方向に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ａとが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ａ，８５Ａの最小径コイル８２，８６同士がばね線材ｗの共有旋回領域８９を介して連続することを特徴とする。 The fifth embodiment of the present invention (see FIGS. 6 and 7) is the same as the second embodiment of the present invention.
The spiral coil spring 80 A is a first coil in which a spring wire w swirls in a spiral shape inside a maximum diameter coil 83 that is provided with an outer tube portion side fixed end 83 a and revolves in a direction opposite to the rotation direction of the outer tube portion 10. A spiral spring portion 81A, a second spiral spring portion 85A in which a spring wire w swirls in a spiral shape inside a maximum diameter coil 87 that is provided with a rotating drum side fixed end 87b and swivels in the rotation direction of the outer cylinder portion 10; Are arranged so as to be separated from each other by a minute distance in the axial direction, and the minimum-

diameter coils

82 and 86 of the first and second

spiral spring portions

81A and 85A are continuously connected to each other via a shared turning area 89 of the spring wire w. It is characterized by doing.

本発明の第６の実施形態は、本発明の第２の実施形態において、
　前記渦巻きコイルばね８０Ｂ（図８，９参照）は、外筒部側固定端８２ａが設けられ前記外筒部１０の回転方向と逆方向に旋回する最小径コイル８２の周りに渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ｂと、前記外筒部１０の回転方向に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｂと、回転ドラム側固定端１８３ｂが設けられ前記外筒部１０の回転方向に旋回する最大径コイル１８３の内側に渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ｂ，８５Ｂの最大径コイル８３，８７同士がばね線材ｗの共有旋回領域８８Ａを介して連続し、前記第２，第３の渦巻きばね部８５Ｂ，１８１の最小径コイル８６，１８２同士がばね線材ｗの共有旋回領域８９Ａを介して連続することを特徴とする。 The sixth embodiment of the present invention is the same as the second embodiment of the present invention.
The spiral coil spring 80 B (see FIGS. 8 and 9) is a spring wire that spirals around a minimum diameter coil 82 that is provided with an outer cylinder side fixed end 82 a and rotates in the direction opposite to the rotation direction of the outer cylinder 10. a first spiral spring portion 81B in which w turns, a second spiral spring portion 85B in which the spring wire w turns in a spiral around the minimum diameter coil 86 that turns in the rotation direction of the outer cylinder portion 10, and rotation A third spiral spring portion 181 in which the spring wire w turns spirally inside the maximum diameter coil 183 provided with the drum side fixed end 183b and turning in the rotation direction of the outer cylinder portion 10 is a minute distance in the axial direction. The first and second

spiral spring portions

81B and 85B have the maximum diameter coils 83 and 87 continuous with each other via a shared swirl region 88A of the spring wire w, Third spiral spring 5B, the minimum diameter coil 86,182 each other 181 is characterized in that a continuous through the shared pivoting region 89A of the spring wire w.

本発明の第７の実施形態(図１０，１１参照）は、本発明の第２の実施形態において、
　前記渦巻きコイルばね８０Ｃは、外筒部側固定端８３ａが設けられ前記外筒部１０の回転方向と逆方向に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、前記外筒部１０の回転方向に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｃと、回転ドラム側固定端１８２ｂが設けられ前記外筒部１０の回転方向に旋回する最小径コイル１８２の周りに渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１Ａとが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ａ，８５Ｃの最小径コイル８２，８６同士がばね線材ｗの共有旋回領域８９Ａを介して連続し、前記第２，第３の渦巻きばね部８５Ｃ，１８１Ａの最大径コイル８７，１８３同士がばね線材ｗの共有旋回領域８８Ｂを介して連続することを特徴とする。 The seventh embodiment (see FIGS. 10 and 11) of the present invention is the same as the second embodiment of the present invention.
The spiral coil spring 80 C is a first in which a spring wire w swirls in a spiral shape inside a maximum diameter coil 83 that is provided with an outer tube portion side fixed end 83 a and revolves in a direction opposite to the rotation direction of the outer tube portion 10. A spiral spring portion 81A, a second spiral spring portion 85C in which the spring wire w turns in a spiral shape, and a rotating drum side fixed end 182b are provided inside the maximum diameter coil 87 that turns in the rotation direction of the outer cylinder portion 10. The third spiral spring portion 181A in which the spring wire w swirls around the minimum diameter coil 182 swirling in the rotation direction of the outer cylinder portion 10 is arranged in a form spaced apart by a minute distance in the axial direction. At the same time, the minimum diameter coils 82 and 86 of the first and second

spiral spring portions

81A and 85C are continuous with each other via a shared swirl region 89A of the spring wire w, and the second and third spiral spring portions 85C. 181 Wherein the maximum diameter coil 87,183 each other are continuous via a shared pivot region 88B of the spring wire w.

　（作用）第４，第５の実施形態における「渦巻きコイルばね」は、第１，第２の渦巻きばね部が軸方向に並設された形態であり、第６，第７の実施形態における「渦巻きコイルばね」は、第１，第２，第３の渦巻きばね部が軸方向に並設された形態であり、いずれの実施形態における「渦巻きコイルばね」も、軸方向に連続して配置された線材コイルの数が「捩りコイルばね」と比べて少ないため、「捩りコイルばね」よりも軸方向の寸法が短い。 (Operation) The “spiral coil spring” in the fourth and fifth embodiments is a form in which the first and second spiral spring portions are arranged in parallel in the axial direction. In the sixth and seventh embodiments, “ The “spiral coil spring” is a form in which the first, second, and third spiral spring portions are arranged in parallel in the axial direction, and the “spiral coil spring” in any of the embodiments is continuously arranged in the axial direction. Since the number of wire coils is smaller than that of the “torsion coil spring”, the axial dimension is shorter than that of the “torsion coil spring”.

　また、第６，第７の実施形態における「渦巻きコイルばね」は、第１，第２の渦巻きばね部に加えて第３の渦巻きばね部が軸方向に並設されている分、第４，第５の実施形態における「渦巻きコイルばね」よりも、軸方向の寸法が僅かに長いため、位相可変装置を軸方向に短縮するという作用については、第４，第５の実施形態における「渦巻きコイルばね」よりも僅かに劣る。 In addition, the “spiral coil spring” in the sixth and seventh embodiments includes a third spiral spring portion arranged in parallel in the axial direction in addition to the first and second spiral spring portions. Since the axial dimension is slightly longer than that of the “spiral coil spring” in the fifth embodiment, the action of shortening the phase varying device in the axial direction will be described in the “spiral coil” in the fourth and fifth embodiments. Slightly inferior to “spring”.

　然るに、並設された渦巻きばね部の数が多い分、線材コイルの数が増え、ばね線材の全長が長くなる分、第４，第５の実施形態における「渦巻きコイルばね」よりもばね定数が小さくなって、第４，第５の実施形態における「渦巻きコイルばね」において設定できる設定トルクよりも低い設定トルクを設定できる。 However, as the number of spiral spring portions arranged in parallel increases, the number of wire coils increases and the total length of the spring wire increases, so that the spring constant is larger than the “spiral coil spring” in the fourth and fifth embodiments. It becomes small and can set the setting torque lower than the setting torque which can be set in the “spiral coil spring” in the fourth and fifth embodiments.

　さらに、捩り荷重に対し第１，第２，第３の渦巻きばね部がそれぞれ径方向に縮径する分、各渦巻きばね部を構成する線材コイルにおける縮径量がいっそう減少し、それだけ線材コイル同士がさらに接触しにくくなって、ヒステリシスがいっそう小さくなる。 Further, the amount of diameter reduction in the wire coils constituting each spiral spring part is further reduced by the amount that the first, second, and third spiral spring parts are radially reduced in response to the torsional load, and the wire coils are correspondingly reduced. Becomes more difficult to contact and hysteresis is further reduced.

　前記目的を達成するために、本発明の第８の実施形態は、
　クランクシャフトの駆動力が伝達されるスプロケットを備えた駆動側の円環状外筒部と、前記外筒部に対し同軸状に回動可能に組み付けられ、動弁機構を構成するカムシャフトに延びる従動側の内筒部と、前記外筒部の内側に形成された凹部と、前記内筒部に一体化されて前記凹部を周方向に遅角油圧室と進角油圧室に区画するとともに、周方向に回動して外筒部に対する内筒部の位相を変えるベーンロータと、前記油圧室に作動油を供給する油圧ポンプと、前記ベーンロータと前記外筒部間に介装された復帰ばねと、を備え、
　前記遅角油圧室と進角油圧室の圧力差によって、前記ベーンロータに生じる前記外筒部に対する回転遅れに連係して、前記外筒部と前記内筒部間の位相が変わる自動車用エンジンにおける位相可変装置において、
　前記復帰ばねは、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部が軸方向に接近するように並設一体化された渦巻きコイルばねで構成されたことを特徴とする。 In order to achieve the above object, the eighth embodiment of the present invention provides:
A drive-side annular outer cylinder portion having a sprocket to which the driving force of the crankshaft is transmitted, and a follower that is rotatably mounted coaxially with respect to the outer cylinder portion and extends to a camshaft constituting the valve mechanism A side inner cylinder part, a recess formed inside the outer cylinder part, and an integral part of the inner cylinder part to divide the recess into a retarded hydraulic chamber and an advanced hydraulic chamber in the circumferential direction. A vane rotor that rotates in a direction to change the phase of the inner cylinder part relative to the outer cylinder part, a hydraulic pump that supplies hydraulic oil to the hydraulic chamber, a return spring interposed between the vane rotor and the outer cylinder part, With
The phase in the automobile engine in which the phase between the outer cylinder part and the inner cylinder part changes due to the rotation delay with respect to the outer cylinder part generated in the vane rotor due to the pressure difference between the retard hydraulic chamber and the advance hydraulic chamber. In the variable device,
The return spring is formed of a spiral coil spring that is integrated in parallel so that a plurality of spiral spring portions in which a spring wire is spirally swung on the same plane approach in the axial direction.

　（作用）ベーンロータと外筒部間に介装される「渦巻きコイルばね」は、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部を軸方向に接近するように並設一体化した形態で、多数の線材コイルが軸方向に連続する形態である「捩りコイルばね」と比べて、軸方向の寸法が短くなる分、外筒部側の復帰ばね取付面と内筒部側の復帰ばね取付面とを接近させて配置することで、位相可変装置の軸方向の長さが短くなる。 (Operation) The “spiral coil spring” interposed between the vane rotor and the outer cylinder part is integrated so that a plurality of spiral spring parts in which the spring wire turns spirally on the same plane approach in the axial direction. Compared to the “torsion coil spring” in which a large number of wire coils are axially continuous in this form, the axial dimension is shortened, so the return spring mounting surface on the outer cylinder side and the inner cylinder part side By arranging the return spring mounting surface close to each other, the axial length of the phase varying device is shortened.

　また、本発明の第８の実施形態（油圧駆動方式の位相可変装置）においても、本発明の第１の実施の形態（電磁ブレーキ駆動方式の位相可変装置）と同様の作用が奏される。 In the eighth embodiment (hydraulic drive type phase varying device) of the present invention, the same operation as the first embodiment (electromagnetic brake drive type phase varying device) of the present invention is exhibited.

　即ち、「渦巻きコイルばね」の捩じりトルク特性を示す直線Ｃは、単位捩りトルクΔＴ/Δθが小さいという点で、「捩りコイルばね」の捩じりトルク特性ＡＢ(図１６)に近く、したがって、「捩りコイルばね」を復帰ばねとして採用する特許文献３ほどではないが、比較的きめ細かな位相可変調整ができる。 That is, the straight line C indicating the torsion torque characteristic of the “spiral coil spring” is close to the torsion torque characteristic AB (FIG. 16) of the “torsion coil spring” in that the unit torsion torque ΔT / Δθ is small. Therefore, although not as much as in Patent Document 3, which employs a “torsion coil spring” as a return spring, relatively fine phase variable adjustment can be performed.

　また、図５に示すように、従来の「捩りコイルばね」や「渦巻きばね」で得られる設定トルクＴ１，Ｔ２（図１６，１８参照）よりも高い設定トルクＴ３を設定できることから、油圧室への作動油の供給を停止後、復帰ばねが元の初期状態に戻るまでの位相可変がスピーディとなる分、位相可変調整の際の応答性が良好となる。 Further, as shown in FIG. 5, a set torque T3 higher than the set torques T1 and T2 (see FIGS. 16 and 18) obtained by the conventional “torsion coil spring” and “spiral spring” can be set. Since the phase variable until the return spring returns to the original initial state after the supply of the hydraulic oil is stopped, the response at the time of phase variable adjustment is improved.

　本発明の第９の実施形態は、本発明の第８の実施形態において、
　軸方向に互いに接近する前記渦巻きばね部は、各渦巻きばね部をそれぞれ構成する線材コイル同士が線材コイル延在方向に対し僅かに軸方向に傾斜するばね線材の共有旋回領域を介して一体化されたことを特徴とする。 The ninth embodiment of the present invention is the same as the eighth embodiment of the present invention.
The spiral spring portions that are close to each other in the axial direction are integrated via a shared swirl region of spring wire rods in which the wire coils constituting the spiral spring portions are slightly inclined in the axial direction with respect to the wire coil extending direction. It is characterized by that.

　本発明の第９の実施形態の作用は、本発明の第２の実施形態における「渦巻きコイルばね」の前記した作用と同一であるので、その説明は省略する。 Since the operation of the ninth embodiment of the present invention is the same as the above-described operation of the “spiral coil spring” in the second embodiment of the present invention, description thereof is omitted.

　本発明の第１０の実施形態（図３，４参照）は、本発明の第９の実施形態において、
　前記渦巻きコイルばね８０は、ベーンロータ側固定端８２ａが設けられ前記外筒部１１０の回転方向と逆方向に旋回する最小径コイルの周りに渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１と、外筒部側固定端８６ｃが設けられ前記外筒部１１０の回転方向に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１，８５の最大径コイル８３，８７同士がばね線材ｗの共有旋回領域８８を介して連続することを特徴とする。 The tenth embodiment of the present invention (see FIGS. 3 and 4) is the same as the ninth embodiment of the present invention.
The spiral coil spring 80 is provided with a vane rotor side fixed end 82a, and a first spiral spring portion in which the spring wire w swirls around a minimum diameter coil swirling in a direction opposite to the rotation direction of the outer cylindrical portion 110. 81 and a second spiral spring portion 85 in which a spring wire w swirls around a minimum diameter coil 86 provided with an outer tube portion side fixed end 86c and swirling in the rotation direction of the outer tube portion 110, The coils are arranged in a form that is separated by a minute distance in the axial direction, and the maximum diameter coils 83 and 87 of the first and second

spiral spring portions

81 and 85 are continuous via a shared swirl region 88 of the spring wire w. It is characterized by.

　本発明の第１１の実施形態（図６，７参照）は、本発明の第９の実施形態において、
　前記渦巻きコイルばね８０Ａは、ベーンロータ側固定端８３ａが設けられ前記外筒部１１０の回転方向と逆方向に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、外筒部側固定端８７ｂが設けられ前記外筒部１１０の回転方向に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ａとが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ａ，８５Ａの最小径コイル８２，８６同士がばね線材ｗの共有旋回領域８９を介して連続することを特徴とする。 The eleventh embodiment (see FIGS. 6 and 7) of the present invention is the same as the ninth embodiment of the present invention.
The spiral coil spring 80A is a first spiral spring in which a spring wire w swirls in a spiral shape inside a maximum diameter coil 83 that is provided with a vane rotor-side fixed end 83a and swirls in a direction opposite to the rotation direction of the outer cylindrical portion 110. 81A and a second spiral spring portion 85A in which the spring wire w turns in a spiral shape inside the maximum diameter coil 87 provided with an outer tube portion side fixed end 87b and turning in the rotation direction of the outer tube portion 110. Are arranged so as to be separated from each other by a minute distance in the axial direction, and the minimum-

diameter coils

82 and 86 of the first and second

spiral spring portions

81A and 85A are continuous with each other via a shared turning area 89 of the spring wire w. It is characterized by that.

　本発明の第１２の実施形態（図８，９参照）は、本発明の第９の実施形態において、
　前記渦巻きコイルばね８０Ｂは、ベーンロータ側固定端８２ａが設けられ前記外筒部１１０の回転方向と逆方向に旋回する最小径コイル８２の周りに渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ｂと、前記外筒部１１０の回転方向に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｂと、外筒部側固定端１８３ｂが設けられ前記外筒部１１０の回転方向に旋回する最大径コイル１８３の内側に渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ｂ，８５Ｂの最大径コイル８３，８７同士がばね線材ｗの共有旋回領域８８Ａを介して連続し、前記第２，第３の渦巻きばね部８５Ｂ，１８１の最小径コイル８６，１８２同士がばね線材ｗの共有旋回領域８９Ａを介して連続することを特徴とする。 The twelfth embodiment (see FIGS. 8 and 9) of the present invention is the same as the ninth embodiment of the present invention.
The spiral coil spring 80B is a first spiral spring in which a spring wire w swirls around a minimum diameter coil 82 that is provided with a vane rotor-side fixed end 82a and swirls in a direction opposite to the rotation direction of the outer cylindrical portion 110. A second spiral spring portion 85B in which the spring wire w swirls around the minimum diameter coil 86 swirling in the rotation direction of the outer cylinder portion 110, and an outer tube portion side fixed end 183b are provided. The third spiral spring part 181 in which the spring wire w turns in a spiral shape is arranged inside the maximum diameter coil 183 that turns in the rotation direction of the outer cylinder part 110 so as to be separated by a minute distance in the axial direction. In addition, the maximum diameter coils 83 and 87 of the first and second

spiral spring portions

81B and 85B are continuous with each other via the shared swirl region 88A of the spring wire w, and the second and third

spiral spring portions

85B and 85B, Minimum diameter coil 86,182 each other 81, characterized in that a continuous through the shared pivoting region 89A of the spring wire w.

　本発明の第１３の実施形態（図１０，１１参照）は、本発明の第９の実施形態において、
　前記渦巻きコイルばねは、ベーンロータ側固定端８３ａが設けられ前記外筒部１１０の回転方向と逆方向に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、前記外筒部１１０の回転方向に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｃと、外筒部側固定端１８２ｂが設けられ前記外筒部１１０の回転方向に旋回する最小径コイル１８２の周りに渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１Ａとが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部８１Ａ，８５Ｃの最小径コイル８２，８６同士がばね線材ｗの共有旋回領域８９Ａを介して連続し、前記第２，第３の渦巻きばね部８５Ｃ，１８１Ａの最大径コイル８７，１８３同士がばね線材ｗの共有旋回領域８８Ｂを介して連続することを特徴とする。 The thirteenth embodiment of the present invention (see FIGS. 10 and 11) is the ninth embodiment of the present invention,
The spiral coil spring is provided with a vane rotor side fixed end 83a, and a first spiral spring portion in which a spring wire w swirls inside a maximum diameter coil 83 swirling in a direction opposite to the rotation direction of the outer cylindrical portion 110. 81A, a second spiral spring portion 85C in which a spring wire w swirls in a spiral shape, and an outer tube portion side fixed end 182b are provided inside a maximum diameter coil 87 swirling in the rotation direction of the outer tube portion 110, and The third spiral spring portion 181A in which the spring wire w swirls around the minimum diameter coil 182 swirling in the rotation direction of the outer cylinder portion 110 is arranged in a form spaced apart by a minute distance in the axial direction. The minimum diameter coils 82 and 86 of the first and second

spiral spring portions

81A and 85C are continuous with each other via a shared swirl region 89A of the spring wire w, and the second and third spiral spring portions 85C and 18 are connected. Wherein the maximum diameter coil 87,183 each other A is continuously via a shared pivot region 88B of the spring wire w.

　（作用）第１０，第１１の実施形態における「渦巻きコイルばね」は、いずれも第１，第２の渦巻きばね部が軸方向に並設された形態であり、第１２，第１３の実施形態における「渦巻きコイルばね」は、いずれも第１，第２，第３の渦巻きばね部が軸方向に並設された形態である。そして、第１０～第１３のいずれの実施形態における「渦巻きコイルばね」も、軸方向に連続して配置された線材コイルの数が「捩りコイルばね」と比べて少ないため、「捩りコイルばね」よりも軸方向の寸法が短い。 (Operation) The “spiral coil spring” in the tenth and eleventh embodiments is a form in which the first and second spiral spring parts are arranged in the axial direction, and the twelfth and thirteenth embodiments. The “spiral coil spring” is a form in which the first, second, and third spiral spring portions are arranged in parallel in the axial direction. The “spiral coil spring” in any of the tenth to thirteenth embodiments has a smaller number of wire coils continuously arranged in the axial direction than the “torsion coil spring”. The axial dimension is shorter.

　また、第１２，第１３の実施形態における「渦巻きコイルばね」は、第１，第２の渦巻きばね部に加えて第３の渦巻きばね部が軸方向に並設されている分、第１０，第１１の実施形態における「渦巻きコイルばね」よりも、軸方向の寸法が僅かに長いため、位相可変装置を軸方向に短縮するという作用については、第１０，第１１の実施形態における「渦巻きコイルばね」よりも僅かに劣る。 In addition, the “spiral coil spring” in the twelfth and thirteenth embodiments includes the third spiral spring part in parallel with the first and second spiral spring parts, and the tenth, Since the axial dimension is slightly longer than that of the “spiral coil spring” in the eleventh embodiment, the action of shortening the phase variable device in the axial direction is described in the “spiral coil” in the tenth and eleventh embodiments. Slightly inferior to “spring”.

　然るに、並設された渦巻きばね部の数が多い分、線材コイルの数が増え、ばね線材の全長が長くなる分、第１０，第１１の実施形態における「渦巻きコイルばね」よりもばね定数が小さくなって、第１０，第１１の実施形態における「渦巻きコイルばね」において設定できる設定トルクよりも低い設定トルクを設定できる。 However, as the number of spiral springs arranged in parallel increases, the number of wire coils increases, and the total length of the spring wire increases, so that the spring constant is greater than the “spiral coil spring” in the tenth and eleventh embodiments. It becomes small and can set the setting torque lower than the setting torque which can be set in the “spiral coil spring” in the tenth and eleventh embodiments.

　以上の説明から明らかなように、本発明の第１の実施形態によれば、回転ドラムと外筒部間に介装する復帰ばねとして、「渦巻きコイルばね」を採用することで、第１には、回転ドラムと外筒部間に介装する復帰ばねの軸方向の寸法が短くなる分、位相可変装置を軸方向に短縮できる。 As is clear from the above description, according to the first embodiment of the present invention, by adopting a “spiral coil spring” as a return spring interposed between the rotating drum and the outer cylinder portion, Since the dimension in the axial direction of the return spring interposed between the rotating drum and the outer cylinder portion is shortened, the phase varying device can be shortened in the axial direction.

　第２には、「渦巻きコイルばね」の捩じりトルク特性は、単位捩りトルクΔＴ/Δθが小さいという点で、「コイルばね」の捩じりトルク特性に近いので、それだけきめ細かな位相可変調整ができる。 Second, the torsional torque characteristics of the “spiral coil spring” are close to the torsional torque characteristics of the “coil spring” in that the unit torsion torque ΔT / Δθ is small. Can do.

　第３には、回転ドラムと外筒部間に介装する復帰ばねの設定トルクを従来よりも大きくすることで、位相可変の際の応答性に優れた位相可変装置を提供できる。 Thirdly, by setting the set torque of the return spring interposed between the rotating drum and the outer cylinder portion larger than before, it is possible to provide a phase variable device with excellent responsiveness at the time of phase variable.

　本発明の第８の実施形態によれば、ベーンロータと外筒部間に介装する復帰ばねとして、「渦巻きコイルばね」を採用することで、第１には、ベーンロータと外筒部間に介装する復帰ばねの軸方向の寸法が短くなる分、位相可変装置を軸方向に短縮できる。 According to the eighth embodiment of the present invention, by adopting a “spiral coil spring” as a return spring interposed between the vane rotor and the outer cylinder part, firstly, an interposition between the vane rotor and the outer cylinder part. The phase variable device can be shortened in the axial direction as the axial dimension of the return spring to be mounted is shortened.

　第２には、「渦巻きコイルばね」の捩じりトルク特性は、単位捩りトルクΔＴ/Δθが小さいという点で、「捩りコイルばね」の捩じりトルク特性に近いので、それだけきめ細かな位相可変調整ができる。 Secondly, the torsional torque characteristics of the “spiral coil spring” are close to the torsional torque characteristics of the “torsion coil spring” in that the unit torsion torque ΔT / Δθ is small. Can be adjusted.

　第３には、ベーンロータと外筒部間に介装する復帰ばねの設定トルクを従来よりも大きくすることで、位相可変の際の応答性に優れた位相可変装置を提供できる。 Thirdly, by setting the set torque of the return spring interposed between the vane rotor and the outer cylinder portion larger than before, it is possible to provide a phase variable device with excellent responsiveness during phase variable.

　本発明の第２の実施形態または第９の実施形態によれば、ばね線材の共有旋回領域に不測の応力が発生したり、応力が集中することもなく、隣接する複数の渦巻きばね部に捩りトルクが等しく伝達されるので、渦巻きコイルばねの耐久性が保証されて、長期間にわたり、バルブの開閉タイミングをきめ細かく的確に制御できる位相可変装置を提供できる。 According to the second embodiment or the ninth embodiment of the present invention, unexpected stress is not generated or concentrated in the shared swirl region of the spring wire, and twisting is performed on a plurality of adjacent spiral spring portions. Since the torque is transmitted equally, the durability of the spiral coil spring is guaranteed, and a phase variable device capable of finely and precisely controlling the opening / closing timing of the valve over a long period of time can be provided.

　本発明の第３の実施形態によれば、内筒部前端部の軸方向前方に電磁クラッチが突出しないので、位相可変装置を軸方向にいっそう短縮できる。 According to the third embodiment of the present invention, since the electromagnetic clutch does not protrude forward in the axial direction of the front end portion of the inner cylinder portion, the phase varying device can be further shortened in the axial direction.

　本発明の第４，第５，第６，第７の実施形態または第１０，第１１，第１２，第１３の実施形態によれば、並設する渦巻きばね部の数や渦巻きばね部を構成する線材コイル数によって復帰ばね（渦巻きコイルばね）の設定トルクが変化することを利用し、並設する渦巻きばね部の数や渦巻きばね部を構成する線材コイル数を適宜調整することで、復帰ばね（渦巻きコイルばね）の設定トルクを従来よりも大きめの所定値に設定することで、バルブの開閉タイミングをきめ細かく的確に制御できる、応答性に優れた位相可変装置を提供できる。 According to the fourth, fifth, sixth, and seventh embodiments or the tenth, eleventh, twelfth, and thirteenth embodiments of the present invention, the number of spiral spring portions arranged in parallel and the spiral spring portions are configured. By using the fact that the set torque of the return spring (spiral coil spring) changes depending on the number of wire coils to be used, the return spring can be adjusted by appropriately adjusting the number of spiral spring portions arranged in parallel and the number of wire coils constituting the spiral spring portion. By setting the set torque of the (coiled coil spring) to a predetermined value larger than the conventional value, it is possible to provide a phase variable device with excellent responsiveness that can precisely and precisely control the opening / closing timing of the valve.

　次に、本発明の実施の形態を実施例に基づいて説明する。 Next, embodiments of the present invention will be described based on examples.

　図１～図５は、本発明に係る位相可変装置の第１の実施例を示し、図１は本発明の第１の実施例である自動車用エンジンにおける位相可変装置の縦断面図、図２は同装置の内部構造を示す分解斜視図、図３は同装置の要部である渦巻きコイルばねの拡大斜視図、図４は同渦巻きコイルばねの具体的形態を示す図で、（ａ）は渦巻きコイルばねの平面図、（ｂ）は渦巻きコイルばねの正面図、（ｃ）は渦巻きコイルばねの右側面図、（ｄ）は渦巻きコイルばねの縦断面図（図４（ｂ）の線IV-IVに沿う断面図）、（ｅ）は渦巻きコイルばねの具体的形態を説明する斜視図、図５は同渦巻きコイルばねの捩りトルク特性を示す図である。 1 to 5 show a first embodiment of a phase varying device according to the present invention, and FIG. 1 is a longitudinal sectional view of the phase varying device in an automobile engine according to the first embodiment of the present invention. Is an exploded perspective view showing the internal structure of the device, FIG. 3 is an enlarged perspective view of a spiral coil spring, which is a main part of the device, and FIG. 4 is a diagram showing a specific form of the spiral coil spring. (B) is a front view of the spiral coil spring, (c) is a right side view of the spiral coil spring, and (d) is a longitudinal sectional view of the spiral coil spring (line IV in FIG. 4B). (E) is a perspective view for explaining a specific form of the spiral coil spring, and FIG. 5 is a diagram showing a torsional torque characteristic of the spiral coil spring.

　この第１の実施例に示す位相可変装置は、エンジンに組み付け一体化された形態で用いられ、クランクシャフトの回転に同期して吸・排気弁が開閉するようにクランクシャフトの回転をカムシャフトに伝達するとともに、エンジンの負荷や回転数などの運転状態によってエンジンの吸・排気弁の開閉のタイミングを変化させるための装置である。 The phase varying device shown in the first embodiment is used in an integrated form with the engine, and the camshaft rotates the crankshaft so that the intake / exhaust valve opens and closes in synchronization with the rotation of the crankshaft. It is a device for transmitting and changing the opening / closing timing of the intake / exhaust valves of the engine according to the operating state such as the engine load and the rotational speed.

　同装置は、電磁ブレーキ駆動方式の位相可変装置で、図１，２に示すように、エンジンのクランクシャフト（図示せず）の駆動力が伝達される円環状外筒部１０と、外筒部１０と同軸状に配置されて外筒部１０に対し相対回動可能で、カムシャフト２を連結一体化した従動側の円環状内筒部２０と、外筒部１０と内筒部２０にそれぞれヘリカルスプライン係合して外筒部１０と内筒部２０間に介装され、軸方向に移動して外筒部１０に対する内筒部２０の位相を変える中間部材３０と、内筒部２０前端部外周のカムシャフト２非配設側に設けられた回転ドラム４４と、回転ドラム４４に制動力を作用させて、中間部材３０を軸方向に移動させるブレーキ手段である電磁クラッチ４０と、回転ドラム４４と外筒部１０（のスプラインケース１６）間に介装された復帰ばね（渦巻きコイルばね）８０とを備えて構成されている。 The device is an electromagnetic brake drive type phase varying device, and as shown in FIGS. 1 and 2, an annular outer cylinder portion 10 to which a driving force of an engine crankshaft (not shown) is transmitted, and an outer cylinder portion 10 is arranged coaxially with the outer cylindrical portion 10 and is rotatable relative to the outer cylindrical portion 10. The driven annular inner cylindrical portion 20 connected to and integrated with the camshaft 2, and the outer cylindrical portion 10 and the inner cylindrical portion 20, respectively. An intermediate member 30 interposed between the outer cylinder part 10 and the inner cylinder part 20 through helical spline engagement and moving in the axial direction to change the phase of the inner cylinder part 20 with respect to the outer cylinder part 10, and the front end of the inner cylinder part 20 A rotating drum 44 provided on the outer periphery of the camshaft 2, an electromagnetic clutch 40 that is a brake means for moving the intermediate member 30 in the axial direction by applying a braking force to the rotating drum 44, and a rotating drum 44 and outer cylinder part 10 (spline case 1 ) Is constituted by a return spring (spiral spring) 80 interposed between.

　外筒部１０は、内周縁にリング状の凸部１２ａが設けられたスプロケット１２と、スプロケット１２の側面に密着するように固定され、凸部１２ａと協働してフランジ係合溝１３を画成するとともに、内周側が中間部材３０とスプライン係合するスプラインケース１６とから構成されている。スプロケット１２には、エンジンのクランクシャフトの回転がチェーンＣを介して伝達される。符号１１は、スプロケット１２とスプラインケース１６を固定一体化する締結ねじで、スプロケット１２とスプラインケース１６で外筒部１０を構成することで、フランジ係合溝１３の形成が容易で、外筒部１０（スプラインケース１６）内周面における雌ヘリカルスプライン１７の形成も容易となっている。 The outer cylindrical portion 10 is fixed so as to be in close contact with the side surface of the sprocket 12 having a ring-shaped convex portion 12a on the inner peripheral edge, and defines the flange engaging groove 13 in cooperation with the convex portion 12a. In addition, the inner peripheral side is constituted by a spline case 16 that is spline engaged with the intermediate member 30. The rotation of the crankshaft of the engine is transmitted to the sprocket 12 via the chain C. Reference numeral 11 denotes a fastening screw that fixes and integrates the sprocket 12 and the spline case 16. The outer cylinder portion 10 is configured by the sprocket 12 and the spline case 16, so that the flange engagement groove 13 can be easily formed. 10 (spline case 16) The female helical spline 17 can be easily formed on the inner peripheral surface.

　また、符号３２，３３は、中間部材３０の内外周面に設けられた雌雄ヘリカルスプライン、符号２３は、内筒部２０の外周面に設けられている雄ヘリカルスプラインである。そして、中間部材３０の内外のスプライン３２，３３は逆方向ヘリカルスプラインで、中間部材３０の軸方向への僅かな移動で、外筒部１０に対し内筒部２０の位相を大きく変化させることができる。符号３１は、中間部材３０の外周面に形成された雄角ねじ部、符号４５は、回転ドラム４４の円筒軸４４ａの内周面に設けられた雌角ねじ部である。

Reference numerals

32 and 33 are male and female helical splines provided on the inner and outer peripheral surfaces of the intermediate member 30, and reference numeral 23 is a male helical spline provided on the outer peripheral surface of the inner cylinder portion 20. The inner and

outer splines

32 and 33 of the intermediate member 30 are reverse helical splines, and the phase of the inner cylinder portion 20 can be greatly changed with respect to the outer cylinder portion 10 by a slight movement of the intermediate member 30 in the axial direction. it can. Reference numeral 31 is a male screw part formed on the outer peripheral surface of the intermediate member 30, and reference numeral 45 is a female screw part provided on the inner peripheral surface of the cylindrical shaft 44 a of the rotary drum 44.

　また、外筒部１０を構成するスプロケット１２の内周縁に形成されたリング状の凸部１２ａには、内筒部２０のフランジ２１が係合するとともに、外筒部１０を構成するスプラインケース１６の段差部１６ａと内筒部２０のフランジ２１間には、皿ばね積層体５０が収容されている。皿ばね積層体５０の反発力によって、内筒部２０と外筒部１０間の相対摺動部における摩擦トルクが上がり、中間部材３０と内外筒部２０，１０間のヘリカルスプライン係合部３２，２３；３３，１７に発生する歯打ち音（歯同士がぶつかる打音）を低減できるようになっている。 Further, a flange 21 of the inner cylinder portion 20 engages with a ring-shaped convex portion 12 a formed on the inner peripheral edge of the sprocket 12 constituting the outer cylinder portion 10, and a spline case 16 constituting the outer cylinder portion 10. The disc spring laminated body 50 is accommodated between the step portion 16 a of the inner cylinder 20 and the flange 21 of the inner cylinder portion 20. By the repulsive force of the disc spring laminated body 50, the friction torque at the relative sliding portion between the inner cylinder portion 20 and the outer cylinder portion 10 is increased, and the helical spline engaging portion 32 between the intermediate member 30 and the inner and

outer cylinder portions

20, 10 is provided. 23; 33, 17 can reduce the rattling noise (battering noise between teeth).

　回転ドラム４４は、軸受け２２を介して内筒部２０前端部に回転可能に支承されるとともに、回転ドラム４４の円筒軸４４ａが中間部材３０の雄角ねじ部３１に螺合するとともに、回転ドラム４４と外筒部１０（のスプラインケース１６）間には、渦巻きコイルばね８０が介装されている。回転ドラム４４と中間部材３０は、角ねじ部４５，３１に沿って周方向に相対回動できる。即ち、中間部材３０は、角ねじ部４５，３１に沿って回動しながら軸方向に移動する。 The rotating drum 44 is rotatably supported on the front end portion of the inner cylinder portion 20 via the bearing 22, and the cylindrical shaft 44 a of the rotating drum 44 is screwed into the male screw portion 31 of the intermediate member 30, and the rotating drum A spiral coil spring 80 is interposed between 44 and the outer cylinder portion 10 (the spline case 16 thereof). The rotating drum 44 and the intermediate member 30 can be rotated relative to each other in the circumferential direction along the

square screw portions

45 and 31. That is, the intermediate member 30 moves in the axial direction while rotating along the

square screw portions

45 and 31.

　また、渦巻きコイルばね８０は、図１，２に示すように、軸方向両端部に設けた回転ドラム側固定端（フック）８６ｃと外筒部側固定端（Ｌ字突起）８２ａを、回転ドラム４４から突出する係止ピン４４ｂと外筒部１０（のスプラインケース１６）に設けたスリット１６ｂにそれぞれ係止させることで、回転ドラム４４と外筒部１０（のスプラインケース１６）間に介装されている。また、渦巻きコイルばね８０は、予め僅かに巻き上げられて所定の設定トルク（例えば、2000Nmm）が作用する形態にセットされている。即ち、電磁クラッチ４０をＯＮさせない状態では、渦巻きコイルばね８０の設定トルク（捩りトルク）相当、例えば、中間部材３０が回転ドラム４４に当接する所定位置に付勢保持されて、外筒部１０，中間部材３０，内筒部２０およびカムシャフト２が一体となって回転、即ち、外筒部１０と内筒部２０は位相差なく一体に回転する。 As shown in FIGS. 1 and 2, the spiral coil spring 80 includes a rotary drum side fixed end (hook) 86c and an outer cylinder side fixed end (L-shaped protrusion) 82a provided at both ends in the axial direction. Interlocking between the rotating drum 44 and the outer cylinder portion 10 (the spline case 16) by engaging the locking pin 44b protruding from the shaft 44 and the slit 16b provided in the outer cylinder portion 10 (the spline case 16). Has been. Further, the spiral coil spring 80 is set in such a manner that it is slightly wound beforehand and a predetermined set torque (for example, 2000 Nmm) acts. That is, in a state where the electromagnetic clutch 40 is not turned on, it is biased and held at a predetermined position corresponding to the set torque (torsional torque) of the spiral coil spring 80, for example, the intermediate member 30 is in contact with the rotating drum 44. The intermediate member 30, the inner cylinder part 20, and the camshaft 2 rotate together, that is, the outer cylinder part 10 and the inner cylinder part 20 rotate integrally without a phase difference.

　そして、渦巻きコイルばね８０の具体的な形態は、後で詳しく説明するが、軸方向にその長さが短く、回転ドラム４４と外筒部１０間が接近して配置されている分、位相可変装置が軸方向にコンパクトとなっている。 The specific form of the spiral coil spring 80 will be described in detail later. However, the length of the spiral coil spring 80 is short in the axial direction, and the phase is variable because the rotating drum 44 and the outer cylinder portion 10 are arranged close to each other. The device is compact in the axial direction.

　また、内筒部２０の前端部外周には、中間部材３０と係合する回転ドラム４４の円筒軸４４ａが配設され、円筒軸４４ａの外周に円環状の電磁クラッチ４０が配設されることで、内筒部２０前端部外周の軸方向後方に回転ドラム４４および電磁クラッチ４０が同軸状に配置された構造で、内筒部２０前端部の軸方向外方に電磁クラッチを配置する従来構造(図１２）と比べて、内筒部２０前端部の軸方向前方に電磁クラッチ４０が突出しない分、位相可変装置の軸方向の長さを短くできる。即ち、シリンダヘッドに取り付け固定するエンジンケース８内(図１左方向)への突出量が小さく、それだけエンジンの位相可変装置配設方向における長さをコンパクトにできる。 A cylindrical shaft 44a of the rotary drum 44 that engages with the intermediate member 30 is disposed on the outer periphery of the front end portion of the inner cylindrical portion 20, and an annular electromagnetic clutch 40 is disposed on the outer periphery of the cylindrical shaft 44a. Thus, a conventional structure in which the rotating drum 44 and the electromagnetic clutch 40 are coaxially arranged at the rear in the axial direction of the outer periphery of the front end portion of the inner cylinder portion 20 and the electromagnetic clutch is arranged outward in the axial direction of the front end portion of the inner cylinder portion 20. Compared with (FIG. 12), the length of the phase variable device in the axial direction can be shortened by the amount that the electromagnetic clutch 40 does not protrude forward in the axial direction of the front end portion of the inner cylinder portion 20. That is, the amount of projection into the engine case 8 (left direction in FIG. 1) attached and fixed to the cylinder head is small, and the length of the engine in the direction in which the phase variable device is disposed can be made compact accordingly.

　回転ドラム４４に制動力を作用させるブレーキ手段である電磁クラッチ４０は、図１,２に示すように、回転ドラム４４のディスク面に向けて開口する横断面コ字型円環状で周方向に回り止めされたクラッチケース４１と、クラッチケース４１内に収容された電磁コイル４２と、クラッチケース４１の開口部内側に固定された金属製（非磁性金属であるステンレス製）の摩擦材保持プレート４３ａと、摩擦材保持プレート４３ａに接着により接合されて、その表面がクラッチケース４１の内外周壁４１ａ，４１ｂの前縁部より僅かに突出する偏平な摩擦材４３とを備えて構成されている。符号４１ｃは、クラッチケース４１の背面側周方向複数個所に突設されたピンで、このピン４１ｃがエンジンケース８裏面に設けた孔８ａに係合して、電磁クラッチ４０（クラッチケース４１）は、軸方向にスライドできるが、周方向には移動できないように拘束されている。 As shown in FIGS. 1 and 2, the electromagnetic clutch 40, which is a braking means that applies a braking force to the rotating drum 44, rotates in the circumferential direction with a U-shaped cross section that opens toward the disk surface of the rotating drum 44. A stopped clutch case 41, an electromagnetic coil 42 housed in the clutch case 41, and a metal (nonmagnetic metal stainless steel) friction material holding plate 43a fixed inside the opening of the clutch case 41; The friction material holding plate 43a is joined to the surface of the friction material holding plate 43a by bonding, and the surface of the friction material holding plate 43a is slightly flat and protrudes from the front edge portions of the inner and outer

peripheral walls

41a and 41b of the clutch case 41. Reference numeral 41c is a pin protruding at a plurality of locations in the circumferential direction on the back side of the clutch case 41. The pin 41c engages with a hole 8a provided on the back surface of the engine case 8, and the electromagnetic clutch 40 (clutch case 41) is Although it can slide in the axial direction, it is restrained so that it cannot move in the circumferential direction.

　また、電磁クラッチ４０の摩擦材４３と回転ドラム４４間の相対摺動面には、エンジンオイルが常に供給されて、両者４３，４４の摺動面温度の上昇が抑制されている。 Also, engine oil is always supplied to the relative sliding surface between the friction material 43 and the rotary drum 44 of the electromagnetic clutch 40, and the increase in the sliding surface temperature of both 43 and 44 is suppressed.

　即ち、図１の符号２ｂは、カムシャフト締結ボルトで、カムシャフト２の一部を構成する内筒部２０をカムシャフト本体２ａに一体化する。カムシャフト２（カムシャフト本体２ａ）内の締結ボルト２ｂの周りには、内筒部２０およびカムシャフト本体２ａの内周面との隙間によって、オイル通路７０が構成されている。 That is, reference numeral 2b in FIG. 1 is a camshaft fastening bolt that integrates the inner cylinder portion 20 constituting a part of the camshaft 2 into the camshaft body 2a. An oil passage 70 is formed around the fastening bolt 2b in the camshaft 2 (camshaft main body 2a) by a gap between the inner cylinder portion 20 and the inner peripheral surface of the camshaft main body 2a.

　カムシャフト締結ボルト２ｂの頭部２ｂ１の周りには、カムシャフト２内のオイル通路７０に連通し、かつクラッチケース４１と回転ドラム４４間の相対摺動部の内周側に連通するオイル溜り７４が、エンジンケース８によって画成されている。カムシャフト２内のオイル通路７０には、カムシャフト２のジャーナル軸受７３のオイルポートおよびカムシャフト２の側孔７３ａを介して、エンジンオイルがポンプＰによって圧送されている。符号７３ｂは、軸受け２２を内筒部２０前端部に固定保持する保持部材２２ａの前面に設けたオイル通路（溝）、符号２０ａは、内筒部２０前端面とボルト頭部２ｂ１の座面間に形成されたオイル通路（隙間）で、オイル通路７０は、これらのオイル通路２０ａ，７３ｂを介してオイル溜り７４に連通する。 Around the head 2b1 of the camshaft fastening bolt 2b, there is an oil reservoir 74 that communicates with the oil passage 70 in the camshaft 2 and communicates with the inner peripheral side of the relative sliding portion between the clutch case 41 and the rotary drum 44. Is defined by the engine case 8. Engine oil is pumped to the oil passage 70 in the camshaft 2 by the pump P through the oil port of the journal bearing 73 of the camshaft 2 and the side hole 73a of the camshaft 2. Reference numeral 73b denotes an oil passage (groove) provided in the front surface of the holding member 22a for fixing and holding the bearing 22 to the front end portion of the inner cylinder portion 20, and reference numeral 20a denotes between the front end surface of the inner cylinder portion 20 and the seating surface of the bolt head portion 2b1. The oil passage 70 is communicated with the oil reservoir 74 through the

oil passages

20a and 73b.

　また、図示しないが、クラッチケース４１の内周壁４１ａ前縁部には、クラッチケース４１側の摩擦材４３と回転ドラム４４間の相対摺動面にエンジンオイルを導入するオイル導入用の切り欠きが設けられ、一方、クラッチケースの外周壁４１ｂ前縁部には、クラッチケース４１側の摩擦材４３と回転ドラム４４間の相対摺動面のエンジンオイルを外方に導出するオイル導出用の切り欠き(図示せず)が設けられている。 Although not shown, an oil introduction notch for introducing engine oil to the relative sliding surface between the friction material 43 on the clutch case 41 side and the rotary drum 44 is provided at the front edge of the inner peripheral wall 41a of the clutch case 41. On the other hand, at the front edge of the outer peripheral wall 41b of the clutch case, an oil lead-out notch for leading out engine oil on the relative sliding surface between the friction material 43 on the clutch case 41 side and the rotary drum 44 to the outside. (Not shown) is provided.

　そして、クラッチケース４１側の摩擦材４３と回転ドラム４４間の相対摺動面には、図１矢印Ｘに示すように、カムシャフト２内に設けたオイル通路７０，オイル通路２０ａ，７３ｂ，オイル溜まり７４を介してエンジンオイルが積極的に導かれて、摩擦材４３と回転ドラム４４の相対摺動面を冷却するように構成されている。 An oil passage 70,

oil passages

20a, 73b provided in the camshaft 2 and oil are provided on the relative sliding surface between the friction material 43 on the clutch case 41 side and the rotary drum 44 as shown by an arrow X in FIG. The engine oil is positively guided through the pool 74 to cool the relative sliding surfaces of the friction material 43 and the rotary drum 44.

　そして、電磁クラッチ４０のＯＮ・ＯＦＦおよび電磁クラッチ４０への通電量を制御することによって、渦巻きコイルばね８０が巻き上げられるとともに、中間部材３０が角ねじ部４５，３１に沿って回動しながら軸方向に移動し、これによって外筒部１０と内筒部２０間の位相が変化して、カムシャフト２のカムによるバルブの開閉のタイミングが調整される。 Then, by controlling ON / OFF of the electromagnetic clutch 40 and the energization amount to the electromagnetic clutch 40, the spiral coil spring 80 is wound up, and the intermediate member 30 is pivoted along the

square screw portions

45, 31 while rotating. The phase between the outer cylinder part 10 and the inner cylinder part 20 changes accordingly, and the opening / closing timing of the valve by the cam of the camshaft 2 is adjusted.

　詳しくは、電磁クラッチ４０をＯＮにする前は、電磁クラッチ４０は、図１仮想線に示す位置にあって、回転ドラム４４と電磁クラッチ４０間には隙間が形成されており、回転ドラム４４は、外筒部１０，中間部材３０，内筒部２０およびカムシャフト２と一体となって回転する。即ち、外筒部１０と内筒部２０は位相差なく一体に回転している。そして、電磁クラッチ４０をＯＮにすると、電磁クラッチ４０が回転ドラム４４に吸引され、図１右方向にスライドし、回転ドラム４４には電磁クラッチ４０を介して制動力が作用する。このため渦巻きコイルばね８０が巻き上げられるとともに、中間部材３０が角ねじ部３１，４５によって前進（図１右方向に移動）し、中間部材３０の内外ヘリカルスプライン３２，３３によって、内筒部２０（カムシャフト２）が外筒部１０（スプロケット１２）に対し回動し、両者２０，１０間の位相が変わる。そして、回転ドラム４４は、電磁クラッチ４０から受ける制動力と渦巻きコイルばね８０の捩りトルクとがバランスする位置（内筒部２０が外筒部１０に対し所定の位相差をもつ位置）に保持された状態で、外筒部１０，中間部材３０，内筒部２０およびカムシャフト２と一体となって回転を継続する。 Specifically, before the electromagnetic clutch 40 is turned on, the electromagnetic clutch 40 is in the position indicated by the phantom line in FIG. 1, and a gap is formed between the rotary drum 44 and the electromagnetic clutch 40. The outer cylinder part 10, the intermediate member 30, the inner cylinder part 20 and the camshaft 2 rotate together. That is, the outer cylinder part 10 and the inner cylinder part 20 rotate integrally with no phase difference. When the electromagnetic clutch 40 is turned on, the electromagnetic clutch 40 is attracted to the rotating drum 44 and slides to the right in FIG. 1, and braking force acts on the rotating drum 44 via the electromagnetic clutch 40. Therefore, the spiral coil spring 80 is wound up, and the intermediate member 30 moves forward (moves in the right direction in FIG. 1) by the

square screw portions

31 and 45, and the inner cylinder portion 20 ( The camshaft 2) rotates relative to the outer cylinder portion 10 (sprocket 12), and the phase between the two 20 and 10 changes. The rotating drum 44 is held at a position where the braking force received from the electromagnetic clutch 40 and the torsion torque of the spiral coil spring 80 are balanced (position where the inner cylinder portion 20 has a predetermined phase difference with respect to the outer cylinder portion 10). In such a state, the outer cylinder part 10, the intermediate member 30, the inner cylinder part 20 and the camshaft 2 are integrally rotated.

　一方、電磁クラッチ４０をＯＦＦにすると、回転ドラム４４には、電磁クラッチ４０による制動力が作用しないため、渦巻きコイルばね８０の復元力（巻き戻す力）が作用する中間部材３０は、角ねじ部３１，４５によって後退（図１左方向に移動）して、元の位置となり、この間に、内筒部２０（カムシャフト２）が外筒部１０（スプロケット１２）に対し電磁クラッチＯＮ時と逆方向に回動して、内筒部２０と外筒部１０間の位相差がなくなる。 On the other hand, since the braking force by the electromagnetic clutch 40 does not act on the rotating drum 44 when the electromagnetic clutch 40 is turned OFF, the intermediate member 30 on which the restoring force (rewinding force) of the spiral coil spring 80 acts is a square screw portion. 31 and 45 (retracted to the left in FIG. 1) to return to the original position. During this time, the inner cylinder 20 (camshaft 2) is opposite to the outer cylinder 10 (sprocket 12) when the electromagnetic clutch is ON. The phase difference between the inner cylinder part 20 and the outer cylinder part 10 disappears.

　次に、回転ドラム４４と外筒部１０（のスプラインケース１６）間に介装されている渦巻きコイルばね８０について説明する。 Next, the spiral coil spring 80 interposed between the rotating drum 44 and the outer cylinder portion 10 (the spline case 16) will be described.

　渦巻きコイルばね８０は、図３，４に示すように、外筒部側固定端（Ｌ字突起）８２ａが設けられて外筒部１０の回転方向と逆方向（図では、左回り）に旋回する最小径コイル８２の周りに渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１と、回転ドラム側固定端（フック）８６ｃが設けられて外筒部１０の回転方向（図では、右回り）に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５とが、軸方向に微小所定距離（例えば、0.5mm）離間する形態に配置されている。そして、第１，第２の渦巻きばね部８１，８５の最大径コイル８３，８７同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８８を介して連続する形態に一体化されている。 As shown in FIGS. 3 and 4, the spiral coil spring 80 is provided with an outer cylinder side fixed end (L-shaped protrusion) 82 a and swivels in the direction opposite to the rotation direction of the outer cylinder 10 (counterclockwise in the figure). The first spiral spring part 81 in which the spring wire w swirls around the minimum diameter coil 82 and a rotating drum side fixed end (hook) 86c are provided to rotate the outer cylinder part 10 in the rotational direction (in the drawing, The second spiral spring portion 85 in which the spring wire w turns in a spiral shape around the minimum diameter coil 86 that turns in the clockwise direction is arranged in a form that is separated by a minute predetermined distance (for example, 0.5 mm) in the axial direction. ing. And the largest diameter coils 83 and 87 of the 1st, 2nd

spiral spring parts

81 and 85 continue through the common turning area | region 88 of the spring wire w which inclines slightly to an axial direction with respect to the wire coil extension direction. It is integrated in the form to do.

　即ち、大中小の三重の線材コイルで構成された第１渦巻きばね部８１の最大径コイル８３と、大中の二重の線材コイルで構成された第２渦巻きばね部８５の最大径コイル８７とが、線材コイル延在方向に対し軸方向に僅かに傾斜する共有旋回領域８８を介して連続する形態に一体化されている。 That is, the maximum diameter coil 83 of the first spiral spring part 81 composed of large, medium and small triple wire coils, and the maximum diameter coil 87 of the second spiral spring part 85 composed of large, medium and double wire coils. Are integrated into a continuous form via a common swivel region 88 that is slightly inclined in the axial direction with respect to the wire coil extending direction.

　渦巻きコイルばね８０は、図１に示すように、回転ドラム４４の外径を超えない大きさに形成されており、渦巻きコイルばね８０のばね線材ｗは、例えば、縦横2.3×3.2mmの矩形状断面を有し、第１渦巻きばね部８１と第２の渦巻きばね部８５間に跨る共有旋回領域８８は、図４（ａ）に示すように、最大径コイル８３，８７に対し平面視θ１（例えば、約２５度）傾斜して延在する。 As shown in FIG. 1, the spiral coil spring 80 is formed in a size that does not exceed the outer diameter of the rotating drum 44, and the spring wire w of the spiral coil spring 80 is, for example, a rectangular shape of 2.3 × 3.2 mm in length and width. A shared swirl region 88 having a cross section and straddling between the first spiral spring portion 81 and the second spiral spring portion 85 is, as shown in FIG. For example, it extends with an inclination of about 25 degrees.

　渦巻きコイルばね８０が巻き上げられる際の捩りトルクは、共有旋回領域８８を介して渦巻きばね部８１，８５間で伝達されるが、共有旋回領域８８は、線材コイル延在方向に対し大きく屈曲することなく軸方向に僅かに傾斜して、渦巻きばね部８１，８５を構成する線材コイルに連続しているので、共有旋回領域８８に不測の応力が発生したり、応力が集中することもなく、渦巻きばね部８１，８５に捩りトルクが等しく伝達される。 Torsional torque when the spiral coil spring 80 is wound up is transmitted between the

spiral spring portions

81 and 85 via the common swirl region 88, but the common swirl region 88 is greatly bent with respect to the wire coil extending direction. Since it is slightly inclined in the axial direction and is continuous with the wire coil constituting the

spiral spring portions

81 and 85, unexpected stress is not generated in the common swirl region 88, and stress is not concentrated. Torsion torque is equally transmitted to the

spring portions

81 and 85.

　そして、渦巻きコイルばね８０の作用・効果は、以下のように説明できる。 And the action and effect of the spiral coil spring 80 can be explained as follows.

　渦巻きコイルばね８０は、ばね線材ｗが同一平面上を渦巻状に旋回する渦巻きばね部８１，８５を軸方向に並設一体化した形態で、多数の線材コイルが軸方向に連続する形態の「捩りコイルばね」に比べて軸方向の寸法が短い分、回転ドラム４４と内筒部２０を接近させて配置することで、位相可変装置の軸方向の長さが短くなる。 The spiral coil spring 80 is a form in which the

spiral wire portions

81 and 85 in which the spring wire w swirls spirally on the same plane are arranged side by side in the axial direction, and a large number of wire coils continue in the axial direction. Since the axial dimension is shorter than that of the “torsion coil spring”, the axial length of the phase varying device is shortened by arranging the rotating drum 44 and the inner cylinder portion 20 closer to each other.

　一方、「渦巻きばね」は、断面矩形状のばね線材が同一平面上に渦巻状に旋回する形態で、渦巻状の線材コイルの巻き数には制約があり、ばね線材の全長が「捩りコイルばね」に比べて短い。このため、「渦巻きばね」は、ばね定数が大きく、捩り荷重に対し内外の線材コイルが均一に変形せず、線材コイル同士が接触しやすく、それだけヒステリシスが大きい（図１８参照）。 On the other hand, a “spiral spring” is a form in which a spring wire having a rectangular cross section is spirally swung on the same plane, the number of turns of the spiral wire rod coil is limited, and the total length of the spring wire rod is “torsion coil spring”. Is shorter than For this reason, the “spiral spring” has a large spring constant, the inner and outer wire coils are not uniformly deformed with respect to the torsional load, the wire coils easily come into contact with each other, and the hysteresis is accordingly large (see FIG. 18).

　これに対し、ばね線材ｗが同一平面上に渦巻状に旋回する形態の渦巻きばね部８１，８５を軸方向に並設一体化した形態の渦巻きコイルばね８０は、ばね線材が同一平面上に渦巻状に旋回するだけの形態である「渦巻きばね」よりも線材コイルの巻き数が多く、ばね線材の全長がそれだけ長い。このため、「渦巻きばね」と比較し、ばね定数が小さく、長期の使用に対しての耐久性に優れる。さらに、「捩りコイルばね」の特性「捩り荷重に対し各線材コイルが半径方向にそれぞれ均等に縮径する」と同じように、軸方向に並設された複数の渦巻きばね部８１，８５が捩り荷重に対しそれぞれ縮径する分、各渦巻きばね部８１，８５を構成する線材コイルにおける縮径量がそれぞれ減少し、それだけ線材コイル同士が接触しにくく、ヒステリシスが小さい（図５参照）。 On the other hand, in the spiral coil spring 80 in which the

spiral spring portions

81 and 85 in which the spring wire w is swirled on the same plane are integrated in the axial direction, the spring wire is spirally wound on the same plane. The number of windings of the wire coil is larger than that of the “spiral spring” which is a form that simply turns, and the total length of the spring wire is longer. For this reason, compared with a "spiral spring", a spring constant is small and it is excellent in durability with respect to long-term use. In addition, as in the “torsion coil spring” characteristic “each wire coil is uniformly reduced in diameter in the radial direction with respect to a torsion load”, a plurality of

spiral spring portions

81 and 85 arranged in parallel in the axial direction are twisted. The amount of diameter reduction in the wire coils constituting the

spiral spring portions

81 and 85 is reduced by the amount of diameter reduction with respect to the load, respectively, the wire coils are less likely to contact each other, and the hysteresis is small (see FIG. 5).

　この結果、渦巻きコイルばね８０の捩じりトルク特性は、図５に示すように、「捩りコイルばね」の捩じりトルク特性を示す直線Ａ（図１６参照）よりも急傾斜で、一方、「渦巻きばね」の捩じりトルク特性を示す直線Ｂ（図１８参照）よりも緩傾斜で、「捩りコイルばね」や「渦巻きばね」よりもヒステリシスが小さく、かつ高い設定トルク（例えば、2000Nmm）Ｔ３を設定できる、右肩上がりの直線Ｃとなる。 As a result, the torsion torque characteristic of the spiral coil spring 80 is steeper than the straight line A (see FIG. 16) indicating the torsion torque characteristic of the “torsion coil spring”, as shown in FIG. Torque torque characteristics of the “spiral spring” are gentler than the straight line B (see FIG. 18), have a smaller hysteresis than the “torsion coil spring” and “spiral spring”, and have a higher set torque (for example, 2000 Nmm) It becomes a straight line C that rises to the right where T3 can be set.

　特に、渦巻きコイルばね８０の捩じりトルク特性を示す直線Ｃは、単位捩りトルクΔＴ/Δθが小さいという点で、「捩りコイルばね」の捩じりトルク特性Ａ(図１６)に近く、したがって、「捩りコイルばね」を復帰ばねとして採用する特許文献１ほどではないが、比較的きめ細かい位相可変調整ができる。 In particular, the straight line C indicating the torsional torque characteristic of the spiral coil spring 80 is close to the torsional torque characteristic A (FIG. 16) of the “torsion coil spring” in that the unit torsion torque ΔT / Δθ is small. Although not as much as in Patent Document 1, which employs a “torsion coil spring” as a return spring, a relatively fine phase variable adjustment can be performed.

　また、図５に示すように、従来の「捩りコイルばね」や「渦巻きばね」で得られる設定トルクＴ１，Ｔ２（図１６，１８参照）よりも高い所定の設定トルクＴ３を設定することで、位相可変調整の際の応答性が改善されている。 Further, as shown in FIG. 5, by setting a predetermined set torque T3 higher than the set torques T1 and T2 (see FIGS. 16 and 18) obtained by the conventional “torsion coil spring” and “spiral spring”, Responsiveness during phase variable adjustment is improved.

　詳しくは、渦巻きコイルばね８０を予め僅かに巻き上げて、回転ドラム４４と内筒部１０（のスプラインケース１７）間にセットすることで、渦巻きコイルばね８０には、所定の大きな設定トルク（例えば、2000Nmm）Ｔ３が設定されている。 Specifically, the spiral coil spring 80 is slightly wound in advance and set between the rotating drum 44 and the inner cylinder portion 10 (the spline case 17 thereof), whereby a predetermined large set torque (for example, 2000Nmm) T3 is set.

　電磁クラッチ４０をＯＮすると、回転ドラム４４には電磁クラッチ４０を介して制動力が作用し、回転が抑制される。このため渦巻きコイルばね８０が巻き上げられ、前進（図１右方向に移動）する中間部材３０を介して、内筒部２０（カムシャフト２）が外筒部１０（スプロケット１２）に対し回動して、内筒部２０の外筒部１０に対する位相が変化する。一方、電磁クラッチ４０をＯＦＦにすると、渦巻きコイルばね８０が巻き戻され、後退（図１左方向に移動）する中間部材３３を介して、内筒部２０が外筒部１０に対し逆方向に回動して、内筒部２０の外筒部１０に対する位相差がなくなるが、渦巻きコイルばね８０には、大きい値（例えば、2000Nmm）の設定トルクＴ３が設定されているので、電磁クラッチＯＦＦ後、渦巻きコイルばね８０が元の初期状態に戻るまでの位相可変がスピーディとなる分、位相可変調整の際の応答性が良好となり、より速い応答性を求めるメーカーのニーズに対応できる。 When the electromagnetic clutch 40 is turned on, a braking force is applied to the rotating drum 44 via the electromagnetic clutch 40, and the rotation is suppressed. For this reason, the spiral coil spring 80 is wound up, and the inner cylinder part 20 (camshaft 2) rotates relative to the outer cylinder part 10 (sprocket 12) via the intermediate member 30 that moves forward (moves in the right direction in FIG. 1). Thus, the phase of the inner cylinder part 20 with respect to the outer cylinder part 10 changes. On the other hand, when the electromagnetic clutch 40 is turned OFF, the spiral coil spring 80 is rewound, and the inner cylinder portion 20 is reverse to the outer cylinder portion 10 via the intermediate member 33 that moves backward (moves leftward in FIG. 1). Although the rotation causes the phase difference between the inner cylinder part 20 and the outer cylinder part 10 to disappear, a large set torque T3 (for example, 2000 Nmm) is set in the spiral coil spring 80. Since the phase variable until the spiral coil spring 80 returns to the original initial state becomes speedy, the response at the time of variable phase adjustment is improved, and it is possible to meet the needs of manufacturers who require faster response.

　なお、回転ドラム４４と外筒部１０（のスプラインケース１６）間に介装する復帰ばね（渦巻きコイルばね）８０としては、本実施例に示す形態(図３，４）の他に、図６～図１１に示すように、種々の変形例８０Ａ～８０Ｃが考えられる。 As a return spring (spiral coil spring) 80 interposed between the rotary drum 44 and the outer cylinder portion 10 (spline case 16 thereof), in addition to the embodiment shown in this embodiment (FIGS. 3 and 4), FIG. As shown in FIG. 11, various modifications 80A to 80C are conceivable.

変形例１の渦巻きコイルばね８０Ａは、図６，７に示すように、外筒部側固定端８３ａが設けられて外筒部１０の回転方向と逆方向（図では、左回り）に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、回転ドラム側固定端(Ｌ字状突起)８７ｂが設けられて外筒部１０の回転方向（図では、右回り）に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ａとが、軸方向に微小所定距離（例えば、0.5mm）離間する形態に配置されている。そして、第１，第２の渦巻きばね部８１Ａ，８５Ａの最小径コイル８２，８６同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８８を介して連続する形態に一体化されている。 As shown in FIGS. 6 and 7, the spiral coil spring 80 A of Modification 1 is provided with an outer cylinder side fixed end 83 a and swivels in the direction opposite to the rotation direction of the outer cylinder 10 (counterclockwise in the figure). A first spiral spring portion 81A in which the spring wire w turns in a spiral shape and a rotating drum side fixed end (L-shaped projection) 87b are provided inside the maximum diameter coil 83 and the rotational direction of the outer cylinder portion 10 (see FIG. Then, the second spiral spring portion 85A in which the spring wire w swirls spirally inside the maximum diameter coil 87 swiveling clockwise is separated by a minute predetermined distance (for example, 0.5 mm) in the axial direction. Has been placed. The minimum diameter coils 82 and 86 of the first and second

spiral spring portions

81A and 85A are continuously connected via a shared swirl region 88 of the spring wire w that is slightly inclined in the axial direction with respect to the wire coil extending direction. It is integrated in the form to do.

　即ち、大中小の三重の線材コイルで構成された第１の渦巻きばね部８１Ａの最小径コイル８２と、大中小の三重の線材コイルで構成された第２の渦巻きばね部８５Ａの最小径コイル８６とが共有旋回領域８９を介して連続する形態に一体化されている。 That is, the minimum diameter coil 82 of the first spiral spring portion 81A composed of large, medium and small triple wire coils and the minimum diameter coil 86 of the second spiral spring portion 85A composed of large, medium and small triple wire coils. Are integrated in a continuous form via a common swivel area 89.

　渦巻きコイルばね８０Ａを構成するばね線材ｗの断面形状は、渦巻きコイルばね８０を構成するばね線材ｗと同じ矩形状で、共有旋回領域８９は、図７に示すように、最小径コイル８２，８６に対し、平面視θ２（約３０度）傾斜するように形成されている。 The cross-sectional shape of the spring wire w constituting the spiral coil spring 80A is the same rectangular shape as that of the spring wire w constituting the spiral coil spring 80, and the common swirl region 89 has minimum diameter coils 82 and 86 as shown in FIG. On the other hand, it is formed so as to incline in plan view θ2 (about 30 degrees).

　前記した実施例の渦巻きコイルばね８０では、第２の渦巻きばね部８５が大中の二重の線材コイルで構成されているのに対し、変形例１の渦巻きコイルばね８０Ａでは、第２の渦巻きばね部８５Ａが大中小の三重の線材コイルで構成されている。即ち、渦巻きコイルばね８０Ａでは、渦巻きコイルばね８０よりも線材コイルの数が１本多い分、ばね線材の全長がそれだけ長く、ばね定数が小さくなるので、設定できる設定トルクは、渦巻きコイルばね８０で設定できる設定トルクよりも幾分低くなる。 In the spiral coil spring 80 of the above-described embodiment, the second spiral spring portion 85 is composed of large and medium double wire coils, whereas in the spiral coil spring 80A of the first modification, the second spiral spring 80A is configured. The spring portion 85A is composed of large, medium and small triple wire coils. That is, in the spiral coil spring 80A, since the number of wire coils is one more than that of the spiral coil spring 80, the total length of the spring wire is longer and the spring constant becomes smaller. It is somewhat lower than the set torque that can be set.

　しかし、渦巻きコイルばね８０Ａを予め所定角度巻き上げた状態で回転ドラム４４と外筒部１０間にセットする、即ち、所定のセット荷重(捩りトルク)が予め作用するようにセットすることで、渦巻きコイルばね８０で設定できると同程度の大きさの所定の設定トルクＴ３を設定できる。 However, the spiral coil spring 80A is set between the rotating drum 44 and the outer cylinder portion 10 in a state where the spiral coil spring 80A is wound in advance by a predetermined angle, that is, by setting so that a predetermined set load (torsion torque) acts in advance. A predetermined set torque T3 having the same magnitude as that set by the spring 80 can be set.

変形例２の渦巻きコイルばね８０Ｂは、図８，９に示すように、外筒部側固定端（Ｌ字突起）８２ａが設けられて外筒部１０の回転方向と逆方向に旋回する最小径コイル８２の周りに、渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ｂと、外筒部１０の回転方向に旋回する最小径コイル８６の周りに渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｂと、回転ドラム側固定端（Ｌ字突起）１８３ｂが設けられて外筒部１０の回転方向に旋回する最大径コイル１８３の内側に、渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１とが、軸方向に微小所定距離（例えば、0.5mm）ずつ離間する形態に配置されている。そして、第１，第２の渦巻きばね部８１Ｂ，８５Ｂの最大径コイル８３，８７同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８８Ａを介して連続し、第２，第３の渦巻きばね部８５Ｂ，１８１の最小径コイル８６，１８２同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８９Ａを介して連続する形態に一体化されている。 As shown in FIGS. 8 and 9, the spiral coil spring 80 B of Modification 2 is provided with an outer cylinder side fixed end (L-shaped projection) 82 a and has a minimum diameter that turns in the direction opposite to the rotation direction of the outer cylinder 10. Around the coil 82, the spring wire w swirls around the first spiral spring portion 81 B in which the spring wire w swirls in a spiral shape and around the minimum diameter coil 86 swirling in the rotation direction of the outer cylinder portion 10. A spring wire w swirls in a spiral shape on the inner side of a maximum diameter coil 183 provided with a second spiral spring portion 85B and a rotating drum side fixed end (L-shaped projection) 183b and swiveling in the rotation direction of the outer cylinder portion 10. The third spiral spring portion 181 is arranged so as to be separated by a minute predetermined distance (for example, 0.5 mm) in the axial direction. The maximum diameter coils 83 and 87 of the first and second

spiral spring portions

81B and 85B are continuous with each other via a shared swirl region 88A of the spring wire w that is slightly inclined in the axial direction with respect to the wire coil extending direction. In addition, the minimum diameter coils 86 and 182 of the second and third

spiral spring portions

85B and 181 are continuously connected to each other via a common swirl region 89A of the spring wire w that is slightly inclined in the axial direction with respect to the wire coil extending direction. It is integrated in the form to do.

　即ち、大中小の線材コイルが渦巻状に三重に連続する第１渦巻きばね部８１Ｂの最大径コイル８３と、大中小の線材コイルが渦巻状に三重に連続する第２渦巻きばね部８５Ｂの最大径コイル８７とが、ばね線材ｗの共有旋回領域８８Ａを介して連続する形態に一体化されるとともに、第２渦巻きばね部８５Ｂの最小径コイル８６と第３の渦巻きばね部１８１の最小径コイル１８２とが、ばね線材ｗの共有旋回領域８９Ａを介して連続する形態に一体化されている。 That is, the maximum diameter coil 83 of the first spiral spring part 81B in which large, medium, and small wire coils are continuously tripled in a spiral shape, and the maximum diameter of a second spiral spring part 85B in which large, medium, and small wire coils are continuously tripled in a spiral shape. The coil 87 is integrated into a continuous form via the shared swirl region 88A of the spring wire w, and the minimum diameter coil 86 of the second spiral spring part 85B and the minimum diameter coil 182 of the third spiral spring part 181 are combined. Are integrated in a continuous form through the shared turning area 89A of the spring wire w.

　渦巻きコイルばね８０Ｂを構成するばね線材ｗの断面形状は、渦巻きコイルばね８０を構成するばね線材ｗと同じ矩形状で、ばね線材ｗの共有旋回領域８８Ａは、図９に示すように、最大径コイル８３，８７に対し、平面視θ３（約２０度）だけ傾斜するように形成され、共有旋回領域８９Ａは、最小径コイル８６，１８２に対し、平面視θ４（約３０度）度傾斜するように形成されている。 The cross-sectional shape of the spring wire material w constituting the spiral coil spring 80B is the same rectangular shape as the spring wire material w constituting the spiral coil spring 80, and the shared swirl region 88A of the spring wire material w has a maximum diameter as shown in FIG. The

coil

83, 87 is formed so as to be inclined by θ3 (about 20 degrees) in plan view, and the common turning area 89A is inclined by θ4 (about 30 degrees) in plan view with respect to the minimum diameter coils 86, 182. Is formed.

　前記した実施例や変形例１の渦巻きコイルばね８０，８０Ａは、第１，第２の渦巻きばね部８１，８５；８１Ａ，８５Ａが軸方向に並設一体化されているのに対し、変形例２の渦巻きコイルばね８０Ｂは、第１，第２，第３の渦巻きばね部８１Ｂ，８５Ｂ，１８１が軸方向に並設一体化されており、捩り荷重に対し渦巻きばね部８１Ｂ，８５Ｂ，１８１がそれぞれ縮径する分、各渦巻きばね部８１Ｂ，８５Ｂ，１８１を構成する線材コイルにおける縮径量が減少し、それだけ線材コイル同士が接触しにくくなって、ヒステリシスが小さく、変形例２の渦巻きコイルばね８０Ｂを用いた方が高精度の位相可変調整が可能となる。 In the spiral coil springs 80 and 80A of the above-described embodiment and modification 1, the first and second

spiral spring parts

81 and 85; 81A and 85A are integrated in parallel in the axial direction. In the second spiral coil spring 80B, the first, second, and third

spiral spring portions

81B, 85B, and 181 are integrated in parallel in the axial direction, and the

spiral spring portions

81B, 85B, and 181 are against the torsional load. The amount of diameter reduction in the wire coils constituting each

spiral spring part

81B, 85B, 181 is reduced by the amount of diameter reduction, the wire coils are less likely to contact each other, the hysteresis is small, and the spiral coil spring of Modification 2 Using 80B enables highly accurate variable phase adjustment.

また、変形例２の渦巻きコイルばね８０Ｂの線材コイル数の総数は９で、渦巻きコイルばね８０の線材コイル数の総数５よりも多く、ばね線材ｗの全長が長くなる分、ばね定数が小さくなるため、渦巻きコイルばね８０Ｂで設定できる設定トルクは、渦巻きコイルばね８０で設定できる設定トルクよりも低くなる。 Further, the total number of wire coils of the spiral coil spring 80B of Modification 2 is 9, which is larger than the total number of wire coils of the spiral coil spring 80, and the spring constant becomes smaller as the total length of the spring wire w becomes longer. Therefore, the set torque that can be set by the spiral coil spring 80 B is lower than the set torque that can be set by the spiral coil spring 80.

　しかし、渦巻きコイルばね８０Ｂを予め所定角度巻き上げた状態で回転ドラム４４と外筒部１０間にセットする、即ち、所定のセット荷重(捩りトルク)が予め作用するようにセットすることで、渦巻きコイルばね８０で設定できると同程度の大きさの所定の設定トルクＴ３を設定できる。 However, by setting the spiral coil spring 80B between the rotating drum 44 and the outer cylinder portion 10 in a state where the spiral coil spring 80B has been wound in advance by a predetermined angle, that is, by setting so that a predetermined set load (torsion torque) acts in advance, the spiral coil A predetermined set torque T3 having the same magnitude as that set by the spring 80 can be set.

変形例３の渦巻きコイルばね８０Ｃは、図１０，１１に示すように、外筒部側固定端（Ｌ字突起）８３ａが設けられて外筒部１０の回転方向と逆方向に旋回する最大径コイル８３の内側に渦巻状にばね線材ｗが旋回する第１の渦巻きばね部８１Ａと、外筒部１０の回転方向に旋回する最大径コイル８７の内側に渦巻状にばね線材ｗが旋回する第２の渦巻きばね部８５Ｃと、回転ドラム側固定端（Ｌ字突起）１８２ｂが設けられ外筒部１０の回転方向に旋回する最小径コイル１８２の周りに渦巻状にばね線材ｗが旋回する第３の渦巻きばね部１８１Ａとが、軸方向に微小所定距離（例えば、0.5mm）ずつ離間する形態に配置されている。 As shown in FIGS. 10 and 11, the spiral coil spring 80 C of Modification 3 is provided with an outer tube portion side fixed end (L-shaped protrusion) 83 a and has a maximum diameter that turns in the direction opposite to the rotation direction of the outer tube portion 10. The first spiral spring portion 81A in which the spring wire w turns in a spiral shape inside the coil 83, and the first spiral spring portion w in which the spring wire w turns in a spiral shape inside the maximum diameter coil 87 which turns in the rotation direction of the outer cylinder portion 10. The spring wire w is swirled around a minimum diameter coil 182 that is provided with the second spiral spring portion 85C and the rotating drum side fixed end (L-shaped projection) 182b and swivels in the rotating direction of the outer cylinder portion 10. The spiral spring portion 181 A is arranged so as to be separated by a minute predetermined distance (for example, 0.5 mm) in the axial direction.

　そして、第１，第２の渦巻きばね部８１Ａ，８５Ｃの最小径コイル８２，８６同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８９Ａを介して連続し、第２，第３の渦巻きばね部８５Ｃ，１８１Ａの最大径コイル８７，１８３同士が、線材コイル延在方向に対し軸方向に僅かに傾斜するばね線材ｗの共有旋回領域８８Ｂを介して連続する形態に一体化されている。 Then, the minimum diameter coils 82 and 86 of the first and second

spiral spring portions

81A and 85C are continuously connected to each other via a shared swirl region 89A of the spring wire w that is slightly inclined in the axial direction with respect to the wire coil extending direction. The maximum diameter coils 87 and 183 of the second and third

spiral spring portions

85C and 181A are continuous with each other via a shared swirl region 88B of the spring wire w that is slightly inclined in the axial direction with respect to the wire coil extending direction. It is integrated in the form to do.

　即ち、大中小の線材コイルが渦巻状に三重に連続する第１渦巻きばね部８１Ａの最小径コイル８２と、大中小の線材コイルが渦巻状に三重に連続する第２渦巻きばね部８５Ｃの最小径コイル８６とが、ばね線材ｗの共有旋回領域８９Ａを介して連続する形態に一体化されるとともに、第２渦巻きばね部８５Ｃの最大径コイル８７と、大中の線材コイルが渦巻状に二重に連続する第３の渦巻きばね部１８１の最大径コイル１８３とが、ばね線材ｗの共有旋回領域８８Ｂを介して連続する形態に一体化されている。 In other words, the minimum diameter coil 82 of the first spiral spring portion 81A in which large, medium, and small wire coils are spirally continued in triplicate, and the minimum diameter of the second spiral spring portion 85C in which large, medium, and small wire rod coils are continuously spirally tripled. The coil 86 is integrated into a continuous form via the shared swirl region 89A of the spring wire w, and the maximum diameter coil 87 of the second spiral spring portion 85C and the large and medium wire rods are doubled in a spiral shape. And the third spiral spring portion 181 having the maximum diameter coil 183 are integrated into a continuous form via the shared swirl region 88B of the spring wire w.

渦巻きコイルばね８０Ｃを構成するばね線材ｗの断面形状は、渦巻きコイルばね８０を構成するばね線材ｗと同じ矩形状で、共有旋回領域８８Ｂは、図１１に示すように、最大径コイル１８３，８７に対し、平面視θ５（約２０度）傾斜するように形成され、共有旋回領域８９Ａは、最小径コイル８２，８６に対し、平面視θ６（約３０度）傾斜するように形成されている。
また、変形例３の渦巻きコイルばね８０Ｃの線材コイルの総数は８で、渦巻きコイルばね８０の線材コイルの総数５よりも多く、ばね線材ｗの全長が長くなる分、ばね定数が小さくなるため、渦巻きコイルばね８０Ｃで設定できる設定トルクは、渦巻きコイルばね８０で設定できる設定トルクよりも低くなる。 The cross-sectional shape of the spring wire w constituting the spiral coil spring 80C is the same rectangular shape as that of the spring wire w constituting the spiral coil spring 80, and the shared swirl region 88B has maximum diameter coils 183 and 87 as shown in FIG. On the other hand, the common swivel region 89A is formed so as to be inclined with respect to the minimum diameter coils 82 and 86 in a plan view θ6 (about 30 degrees).
In addition, the total number of wire coils of the spiral coil spring 80C of Modification 3 is 8, which is greater than the total number of wire coils 5 of the spiral coil spring 80, and the spring constant becomes smaller as the total length of the spring wire w increases. The set torque that can be set by the spiral coil spring 80 C is lower than the set torque that can be set by the spiral coil spring 80.

　しかし、渦巻きコイルばね８０Ｃを予め所定角度巻き上げた状態で回転ドラム４４と外筒部１０間にセットする、即ち、所定のセット荷重(捩りトルク)が予め作用するようにセットすることで、渦巻きコイルばね８０で設定できると同程度の大きさの所定の設定トルクＴ３を設定できる。 However, the spiral coil spring 80C is set between the rotating drum 44 and the outer cylindrical portion 10 in a state in which the spiral coil spring 80C has been wound in advance by a predetermined angle, that is, by setting so that a predetermined set load (torsion torque) acts in advance. A predetermined set torque T3 having the same magnitude as that set by the spring 80 can be set.

　前記した実施例や変形例１～３では、回転ドラム４４と内筒部２０間に介装される「渦巻きコイルばね」の種々の形態について説明したが、並設する渦巻きばね部の数や渦巻きばね部を構成する線材コイルの数によって「渦巻きコイルばね」のばね定数が変わり、したがって、設定できる設定トルクも変化することから、並設する渦巻きばね部の数や線材コイルの数を適宜選択し、さらには、所定の捩りトルクが予め作用するように渦巻きコイルばねをセットすることで、復帰ばね（渦巻きコイルばね）の設定トルクを位相可変調整の応答性を改善できる所定値とすることで、バルブの開閉タイミングをきめ細かく的確に制御できる、応答性に優れた位相可変装置を提供することができる。 In the above-described embodiments and modifications 1 to 3, various forms of the “spiral coil spring” interposed between the rotary drum 44 and the inner cylinder portion 20 have been described, but the number of spiral spring portions arranged in parallel and the spiral The spring constant of the “spiral coil spring” changes depending on the number of wire coils constituting the spring part, and therefore the set torque that can be set also changes. Therefore, the number of spiral spring parts and the number of wire coils to be arranged side by side are appropriately selected. Furthermore, by setting the spiral coil spring so that the predetermined torsion torque acts in advance, the set torque of the return spring (spiral coil spring) is set to a predetermined value that can improve the response of the variable phase adjustment, It is possible to provide a phase variable device with excellent responsiveness capable of finely and precisely controlling the opening and closing timing of the valve.

　なお、前記した実施例では、軸方向に互いに接近する渦巻きばね部の線材コイル同士を接続する共有旋回領域は、軸方向に直交する平面上を渦巻状に旋回する線材コイルに対し所定角度(例えば、２０度、２５度、３０度)傾斜するように形成されているが、この傾斜は小さい方が望ましいが、共有旋回領域が１周旋回するまでの間に渦巻きばね部同士を一体化できる傾斜であれば、何度でもかまわない。 In the above-described embodiment, the common swirl region for connecting the wire coils of the spiral spring portions that are close to each other in the axial direction has a predetermined angle (for example, with respect to the wire coil that swirls spirally on a plane orthogonal to the axial direction) , 20 degrees, 25 degrees, 30 degrees), but it is desirable that this inclination is smaller, but the inclination that allows the spiral spring parts to be integrated before the shared swirl region makes one turn If so, it doesn't matter how many times.

　また、前記した実施例では、軸方向に隣接する渦巻きコイルばね部間の微小距離は、ばねの製造上の誤差を考慮して、ばねの巻き上げ・巻き戻しの際に、軸方向に隣接する線材コイル同士が干渉しない、例えば0.5ｍｍに設定されているが、この値に限るものではなく、それ以下でも、それ以上であってもよい。 Further, in the above-described embodiment, the minute distance between the spiral coil spring portions adjacent in the axial direction is determined by taking into account errors in manufacturing the spring, and the wire rod adjacent in the axial direction when the spring is wound or unwound. The coil does not interfere with each other, for example, is set to 0.5 mm, but is not limited to this value, and may be less or more.

　また、前記した実施例では、渦巻きコイルばね８０を構成するばね線材ｗの断面を、例えば、縦横2.3×3.2mmの矩形状と説明したが、矩形状であれは、縦横2.3×3.2mmの寸法に限るものではない。 Further, in the above-described embodiment, the cross section of the spring wire w constituting the spiral coil spring 80 has been described as a rectangular shape having, for example, a size of 2.3 × 3.2 mm in length and width. It is not limited to.

　図１２，１３，１４は、本発明に係る位相可変装置の第２の実施例を示し、図１２は、本発明の第２の実施例である位相可変装置の縦断面図、図１３は、同装置の内部構造を示す正面図（図１２に示す線XIII-XIIIに沿う正面図）、図１４は、同装置の油圧回路の構成を示す概略図である。 12, 13 and 14 show a second embodiment of the phase variable device according to the present invention, FIG. 12 is a longitudinal sectional view of the phase variable device according to the second embodiment of the present invention, and FIG. FIG. 14 is a schematic view showing the configuration of the hydraulic circuit of the apparatus, and FIG. 14 is a front view showing the internal structure of the apparatus (front view along the line XIII-XIII shown in FIG. 12).

　これらの図において、この第２の実施例に係る位相可変装置は、油圧駆動方式の位相可変装置で、エンジンのクランクシャフト（図示せず）の駆動力が伝達される円環状外筒部１１０と、外筒部１１０と同軸に配置されて外筒部１１０に対し相対回動可能で、カムシャフト２に延びる従動側の円環状内筒部１２０を備えている。 In these drawings, the phase varying device according to the second embodiment is a hydraulically driven phase varying device, and an annular outer cylindrical portion 110 to which a driving force of an engine crankshaft (not shown) is transmitted, and A driven annular inner cylinder portion 120 is provided which is disposed coaxially with the outer cylinder portion 110 and is rotatable relative to the outer cylinder portion 110 and extends to the camshaft 2.

　外筒部１１０は、円盤状のスプロケット１１２と、スプロケット１１２の側面に密着するように固定一体化された円筒形状のシューハウジング１１３と、シューハウジング１１３の開口側を覆うフロントプレート１１４で構成されている。　シューハウジング１１３の周壁１１３ａ内側には、図１３に示すように、仕切り部材としての略台形状のシュー１１５が周方向略等分４箇所に形成され、周方向に隣接するシュー１１５，１１５間には、後述するベーン２１２が収容される凹部１１６が形成されている。即ち、スプロケット１１２，シューハウジング１１３およびフロントプレート１１４によって、ベーン２１２を覆うベーンハウジングが構成されている。 The outer cylinder portion 110 includes a disc-shaped sprocket 112, a cylindrical shoe housing 113 that is fixed and integrated so as to be in close contact with the side surface of the sprocket 112, and a front plate 114 that covers the opening side of the shoe housing 113. Yes. Inside the peripheral wall 113a of the shoe housing 113, as shown in FIG. 13, substantially trapezoidal shoes 115 as partition members are formed at substantially equal four locations in the circumferential direction, and between the

shoes

115, 115 adjacent in the circumferential direction. Is formed with a recess 116 in which a vane 212 described later is accommodated. That is, the sprocket 112, the shoe housing 113, and the front plate 114 constitute a vane housing that covers the vane 212.

　一方、円環状内筒部１２０は、周方向略等分４箇所にベーン２１２を有するベーンロータ２１０で構成されており、カムシャフト締結ボルト２ｂによって、ベーンロータ２１０の肉厚に形成されたボス部２１１がカムシャフト２（カムシャフト本体２ａ）に固定一体化されている。シューハウジング１１３内側の凹部１１６には、ベーンロータ２１０のベーン２１２がそれぞれ収容されて、各凹部１１６が周方向に遅角油圧室１１６ａと進角油圧室１１６ｂに区画されている。 On the other hand, the annular inner cylindrical portion 120 is composed of a vane rotor 210 having vanes 212 at approximately four locations in the circumferential direction, and a boss portion 211 formed in the thickness of the vane rotor 210 by a camshaft fastening bolt 2b. The camshaft 2 (camshaft body 2a) is fixed and integrated. The vanes 212 of the vane rotor 210 are accommodated in the recesses 116 inside the shoe housing 113, and each recess 116 is partitioned into a retarded hydraulic chamber 116a and an advanced hydraulic chamber 116b in the circumferential direction.

　シューハウジング１１３の周壁１１３ａとベーン２１２との間、およびシュー１１５とベーンロータ２１０のボス部２１１外周との間には、シール部材１３０がそれぞれ介装されて、遅角油圧室１１６ａと進角油圧室１１６ｂ間の液密性が確保されている。 Seal members 130 are interposed between the peripheral wall 113a of the shoe housing 113 and the vane 212, and between the shoe 115 and the outer periphery of the boss 211 of the vane rotor 210, respectively, so that the retard hydraulic chamber 116a and the advance hydraulic chamber. Liquid tightness between 116b is ensured.

　また、ベーンロータ２１０のボス部２１１前端面には、ばね収容室２１４が形成され、該ばね収容室２１４には、復帰ばねである渦巻きコイルばね８０（図３，４参照）が収容されて、ベーンロータ２１０の４個のベーン２１２の一つ２１２ａ（図１３参照）が対応するシュー１１５ａの進角油圧室１１６ｂに臨む側面１１５ａに付勢当接する形態に保持されている。 A spring accommodating chamber 214 is formed on the front end surface of the boss 211 of the vane rotor 210, and a spiral coil spring 80 (see FIGS. 3 and 4), which is a return spring, is accommodated in the spring accommodating chamber 214. One of the four vanes 212, 210a (see FIG. 13), is held in a form of being in urging contact with the side surface 115a of the corresponding shoe 115a facing the advance hydraulic chamber 116b.

　詳しくは、渦巻きコイルばね８０は、一方の固定端（フック）８６ｃがフロントプレート１１４裏面に突設された係止ピン１１４ａに係止されるとともに、他方の固定端（Ｌ字突起）８２ａがベーンロータ２１０のばね収容室２１４に設けた係止孔２１２ａに係止されている。渦巻きコイルばね８０は、所定（例えば、2000Nmm）の設定トルクＴ３が作用するように予め僅かに巻き上げた形態（遅角側に設定トルクＴ３相当の付勢力が作用する形態）にして、外筒部１１０（のフロントプレート１１４）とベーンロータ２１０間に介装されて、ベーンロータ２１０は常に遅角側（反時計回り）に付勢された形態に保持されている。 Specifically, in the spiral coil spring 80, one fixed end (hook) 86c is locked to a locking pin 114a projecting from the back surface of the front plate 114, and the other fixed end (L-shaped protrusion) 82a is a vane rotor. It is locked in a locking hole 212 a provided in the spring accommodating chamber 214 of 210. The spiral coil spring 80 is formed in a form slightly wound in advance (form in which an urging force equivalent to the set torque T3 acts on the retard side) so that a predetermined (for example, 2000 Nmm) set torque T3 acts. 110 (the front plate 114) and the vane rotor 210 are interposed between the vane rotor 210 and the vane rotor 210. The vane rotor 210 is always held in a form biased to the retard side (counterclockwise).

　即ち、この第２の実施例の位相可変装置に採用されている渦巻きコイルばね８０は、第１の実施例で採用されている渦巻きコイルばね８０と同一構造であるが、第２の実施例では、外筒部側固定端（Ｌ字突起）８２ａをベーンロータ側固定端として、回転ドラム側固定端（フック）８６ｃを外筒部（フロントプレート）側固定端として、外筒部１１０（のフロントプレート１１４）とベーンロータ２１０間に介装されている点が相違する。 That is, the spiral coil spring 80 employed in the phase varying device of the second embodiment has the same structure as the spiral coil spring 80 employed in the first embodiment, but in the second embodiment, The outer cylinder part 110 (the front plate of the outer cylinder part 110) is formed with the outer cylinder part fixed end (L-shaped projection) 82a as the vane rotor side fixed end and the rotating drum side fixed end (hook) 86c as the outer cylinder part (front plate) side fixed end. 114) and the vane rotor 210 are different.

　この渦巻きコイルばね８０の構成については、前記した第１の実施例において詳しく説明しているので、その重複する説明は省略する。 Since the configuration of the spiral coil spring 80 has been described in detail in the first embodiment, the overlapping description is omitted.

　また、カムシャフト２，内筒部１２０（ベーンロータ２１０）および外筒部１１０には、図１２，１４に示すように、遅角油圧室１１６ａに連通する遅角通路１１７ａ～１１７ｄ、進角油圧室１１６ｂに連通する進角通路１１８ａ～１１８ｄが設けられている。そして、油圧ポンプＰは、オイルタンクＴのエンジンオイル（作動油）を、遅角通路１１７，１１７ａ～１１７ｄを介して遅角油圧室１１６ａに供給し、進角通路１１８，１１８ａ～１１８ｄを介して進角油圧室１１６ｂに供給する。符号２００は、遅角通路１１７と進角通路１１８間でオイル通路を切り替える切替弁である。 Further, as shown in FIGS. 12 and 14, the camshaft 2, the inner cylinder portion 120 (vane rotor 210) and the outer cylinder portion 110 are provided with retard passages 117a to 117d communicating with the retard hydraulic chamber 116a, and an advance hydraulic chamber. Advance passages 118a to 118d communicating with 116b are provided. The hydraulic pump P supplies engine oil (hydraulic oil) in the oil tank T to the retarded hydraulic chamber 116a via the

retarded passages

117, 117a to 117d, and via the

advanced passages

118, 118a to 118d. Supply to the advance hydraulic chamber 116b. Reference numeral 200 is a switching valve that switches the oil passage between the retard passage 117 and the advance passage 118.

　そして、オイルタンクＴのエンジンオイルが進角通路１１８，１１８ａ～１１８ｄを介して進角油圧室１１６ｂに供給される場合は、遅角油圧室１１６ａのエンジンオイルが遅角通路１１７ａ～１１７ｄ，１１７を介してオイルタンクＴに戻り、ベーンロータ２１０が進角側（時計回り）に回動して、位相が進角側にずれる。 When engine oil in the oil tank T is supplied to the advance hydraulic chamber 116b via the

advance passages

118, 118a to 118d, the engine oil in the retard hydraulic chamber 116a passes through the retard passages 117a to 117d, 117. Through the oil tank T, the vane rotor 210 rotates to the advance side (clockwise), and the phase shifts to the advance side.

　逆に、オイルタンクＴのエンジンオイルが遅角通路１１７，１１７ａ～１１７ｄを介して遅角油圧室１１６ａに供給される場合は、進角油圧室１１６ｂのエンジンオイルが進角通路１１８ａ～１１８ｄ，１１８を介してオイルタンクＴに戻り、ベーンロータ２１０が遅角側（反時計回り）に回動して、位相が遅角側にずれる。 Conversely, when engine oil in the oil tank T is supplied to the retarded hydraulic chamber 116a via the

retarded passages

117, 117a to 117d, the engine oil in the advanced hydraulic chamber 116b is advanced to the advanced passages 118a to 118d, 118. The vane rotor 210 is rotated to the retard side (counterclockwise) and the phase is shifted to the retard side.

　そして、ベーンロータ２１０が目標位置に到達すると、ＥＣＵ２２０は、切替弁２００を動作させて、進角通路１１８および遅角通路１１７と、油圧ポンプＰおよびオイルタンクＴとの接続を遮断し、遅角油圧室１１６ａおよび進角油圧室１１６ｂからオイルタンクＴにエンジンオイルが排出されることを防止することで、ベーンロータ２１０が目標位置に保持される。 When the vane rotor 210 reaches the target position, the ECU 220 operates the switching valve 200 to disconnect the advance passage 118 and the retard passage 117 from the hydraulic pump P and the oil tank T, thereby retarding the hydraulic pressure. By preventing the engine oil from being discharged into the oil tank T from the chamber 116a and the advance hydraulic chamber 116b, the vane rotor 210 is held at the target position.

　特に、本実施例では、ベーンロータ２１０が遅角側（反時計回り）に回動する際、復帰ばねである渦巻きコイルばね８０の設定トルク（例えば、2000Nmm）相当の付勢力もベーンロータ２１０を遅角側（反時計回り）に回動させる力として作用するため、位相が遅角側にずれる速度が速い。 In particular, in this embodiment, when the vane rotor 210 rotates to the retard side (counterclockwise), the biasing force equivalent to the set torque (for example, 2000 Nmm) of the spiral coil spring 80 that is the return spring also retards the vane rotor 210. Since this acts as a force for rotating the lens to the side (counterclockwise), the speed at which the phase shifts to the retard angle side is high.

　このように、遅角油圧室１１６ａと進角油圧室１１６ｂへのエンジンオイルの給排制御により、遅角油圧室１１６ａと進角油圧室１１６ｂの圧力差によって、ベーンロータ２１０（内筒部１２０）に生じる外筒部１１０に対する回転遅れに連係して、外筒部１１０と内筒部１２０間の位相、即ちクランクシャフトに対するカムシャフト２の位相が変化するように構成されている。 As described above, the engine oil supply / discharge control to the retarded hydraulic chamber 116a and the advanced hydraulic chamber 116b causes the pressure difference between the retarded hydraulic chamber 116a and the advanced hydraulic chamber 116b to be applied to the vane rotor 210 (inner cylinder portion 120). The phase between the outer cylinder part 110 and the inner cylinder part 120, that is, the phase of the camshaft 2 with respect to the crankshaft is changed in association with the generated rotation delay with respect to the outer cylinder part 110.

　この第２の実施例において、渦巻きコイルばね８０を用いたことによる効果は、前記した第１の実施例（電磁ブレーキ駆動式の位相可変装置）で用いた渦巻きコイルばね８０を用いたことによる作用・効果と同じであるため、簡単に説明し、その重複した説明は省略する。 In this 2nd Example, the effect by using the spiral coil spring 80 is the effect | action by having used the spiral coil spring 80 used in the above-mentioned 1st Example (electromagnetic brake drive type phase variable apparatus). -Since it is the same as an effect, it demonstrates easily and the duplicate description is abbreviate | omitted.

　第１に、渦巻きコイルばね８０は、捩りコイルばねに比べて軸方向の寸法が短い分、外筒部１１０（フロントプレート１１４）側のばね取付面と内筒部１２０（ベーンロータ２１０）側のばね取付面を接近させて配置することで、位相可変装置１０の軸方向の長さが短くなる。 First, the spiral coil spring 80 is shorter in the axial direction than the torsion coil spring, and thus the spring mounting surface on the outer cylinder part 110 (front plate 114) side and the spring on the inner cylinder part 120 (vane rotor 210) side. By arranging the mounting surfaces close to each other, the axial length of the phase varying device 10 is shortened.

　特に、第２の実施例では、ベーンロータ２１０のボス部２１１前端面に設けたばね収容室２１４に、復帰ばねである渦巻きコイルばね８０を収容するとともに、渦巻きコイルばね８０やカムシャフト締結ボルト２ｂ（の頭部２ｂ１）がフロントプレート１１４外方に突出しないように配置したので、それだけ位相可変装置の軸方向の長さがいっそう短くなる。 In particular, in the second embodiment, a spiral coil spring 80 as a return spring is accommodated in a spring accommodating chamber 214 provided on the front end surface of the boss portion 211 of the vane rotor 210, and the spiral coil spring 80 and the camshaft fastening bolt 2b ( Since the head 2b1) is arranged so as not to protrude outward from the front plate 114, the axial length of the phase variable device is further shortened accordingly.

　第２に、渦巻きコイルばね８０は、図５に示すように、ヒステリシスが小さく、単位捩りトルクΔＴ/Δθが小さいという点で、第２の実施例の位相可変装置では、きめ細かい位相可変調整ができる。 Second, as shown in FIG. 5, the spiral coil spring 80 has a small hysteresis and a small unit torsion torque ΔT / Δθ, so that the phase variable device of the second embodiment can perform fine phase variable adjustment. .

　第３に、従来の「捩りコイルばね」や「渦巻きばね」で得られる設定トルクＴ１，Ｔ２（図１６，１８参照）よりも高い所定（例えば、2000Nmm）の設定トルクＴ３を設定する（図５参照）ことで、特に、遅角側の位相可変調整の応答性を上げることができる。 Third, a predetermined set torque T3 (for example, 2000 Nmm) higher than the set torques T1 and T2 (see FIGS. 16 and 18) obtained by the conventional “torsion coil spring” and “spiral spring” is set (FIG. 5). In particular, the responsiveness of the variable phase adjustment on the retard side can be improved.

　また、ベーンロータ２１０（のボス部２１１）と外筒部１１０（のフロントプレート１１４）間に介装する復帰ばね（渦巻きコイルばね）８０としては、図３，４に示す形態の他に、図６～図１１に示すように、種々の変形例８０Ａ～８０Ｃが考えられる。 Further, as the return spring (spiral coil spring) 80 interposed between the vane rotor 210 (the boss portion 211 thereof) and the outer cylinder portion 110 (the front plate 114 thereof), in addition to the forms shown in FIGS. As shown in FIG. 11, various modifications 80A to 80C are conceivable.

　即ち、渦巻きコイルばね８０Ａは、一方の固定端８３ａをベーンロータ側固定端とし、他方の固定端８７ｂを外筒部側固定端として、外筒部１１０（のフロントプレート１１４）とベーンロータ２１０間に介装される。 That is, the spiral coil spring 80A has one fixed end 83a as the vane rotor side fixed end and the other fixed end 87b as the outer cylinder portion side fixed end, and is interposed between the outer cylinder portion 110 (the front plate 114) and the vane rotor 210. Be dressed.

　また、渦巻きコイルばね８０Ｂは、一方の固定端８２ａをベーンロータ側固定端とし、他方の固定端１８３ｂを外筒部側固定端として、外筒部１１０（のフロントプレート１１４）とベーンロータ２１０間に介装される。 Further, the spiral coil spring 80B has one fixed end 82a as a vane rotor side fixed end and the other fixed end 183b as an outer cylinder side fixed end, and is interposed between the outer cylinder portion 110 (the front plate 114) and the vane rotor 210. Be dressed.

　また、渦巻きコイルばね８０Ｃは、一方の固定端８３ａをベーンロータ側固定端とし、他方の固定端１８２ｂを外筒部側固定端として、外筒部１１０（のフロントプレート１１４）とベーンロータ２１０間に介装される。 Further, the spiral coil spring 80C has one fixed end 83a as the vane rotor side fixed end and the other fixed end 182b as the outer cylinder portion side fixed end, and is interposed between the outer cylinder portion 110 (the front plate 114) and the vane rotor 210. Be dressed.

　なお、前記した本発明の第２の実施例（図１２，１３，１４参照）では、外筒部１１０を構成するフロントプレート１１６と、ベーンロータ２１０間に介装された渦巻きコイルばね８０，８０Ａ～８０Ｃ（図３，４，６～１１参照）によって、ベーンロータ２１０が常に遅角側（反時計回り）に付勢されているが、渦巻きコイルばね８０，８０Ａ～８０Ｃを構成するばね線材ｗの旋回方向（線材コイルの旋回方向）を逆向きに構成した渦巻きコイルばねを用いることで、ベーンロータ２１０が常に進角方向（時計回り）に付勢されるように構成してもよい。 In the above-described second embodiment of the present invention (see FIGS. 12, 13, and 14), spiral coil springs 80, 80A to 80A interposed between the front plate 116 constituting the outer cylinder portion 110 and the vane rotor 210 are provided. The vane rotor 210 is always urged to the retard side (counterclockwise) by 80C (see FIGS. 3, 4, 6 to 11), but the swirling of the spring wire w constituting the spiral coil springs 80 and 80A to 80C The vane rotor 210 may be configured to be always urged in the advance direction (clockwise) by using a spiral coil spring having the direction (the turning direction of the wire coil) reversed.

本発明の第１の実施例である自動車用エンジンにおける位相可変装置の縦断面図である。It is a longitudinal cross-sectional view of the phase variable apparatus in the engine for motor vehicles which is the 1st Example of this invention. 同装置の内部構造を示す分解斜視図である。It is a disassembled perspective view which shows the internal structure of the apparatus. 同装置の要部である渦巻きコイルばねの拡大斜視図である。It is an expansion perspective view of the spiral coil spring which is the principal part of the same apparatus. 同渦巻きコイルばねの具体的形態を示す図で、（ａ）は渦巻きコイルばねの平面図、（ｂ）は渦巻きコイルばねの正面図、（ｃ）は渦巻きコイルばねの右側面図、（ｄ）は渦巻きコイルばねの縦断面図（図４（ｂ）の線IV-IVに沿う断面図）、（ｅ）は渦巻きコイルばねの具体的形態を説明する斜視図である。It is a figure which shows the specific form of the spiral coil spring, (a) is a top view of a spiral coil spring, (b) is a front view of a spiral coil spring, (c) is a right view of a spiral coil spring, (d). Fig. 4 is a longitudinal sectional view of the spiral coil spring (cross sectional view taken along line IV-IV in Fig. 4B), and Fig. 4E is a perspective view for explaining a specific form of the spiral coil spring. 同渦巻きコイルばねの捩りトルク特性を示す図である。It is a figure which shows the torsion torque characteristic of the same spiral coil spring. 変形例１の渦巻きコイルばねの具体的形態を説明する斜視図である。It is a perspective view explaining the specific form of the spiral coil spring of the modification 1. FIG. 同渦巻きコイルばねの平面図である。It is a top view of the spiral coil spring. 変形例２の渦巻きコイルばねの具体的形態を説明する斜視図である。It is a perspective view explaining the specific form of the spiral coil spring of the modification 2. 同渦巻きコイルばねの平面図である。It is a top view of the spiral coil spring. 変形例３の渦巻きコイルばねの具体的形態を説明する斜視図である。It is a perspective view explaining the specific form of the spiral coil spring of the modification 3. 同渦巻きコイルばねの平面図である。It is a top view of the spiral coil spring. 本発明の第２の実施例である自動車用エンジンにおける位相可変装置の縦断面図である。It is a longitudinal cross-sectional view of the phase variable apparatus in the engine for motor vehicles which is the 2nd Example of this invention. 同装置の内部構造を示す正面図（図１２に示す線XIII-XIIIに沿う正面図）である。FIG. 13 is a front view showing the internal structure of the apparatus (front view taken along line XIII-XIII shown in FIG. 12). 同装置の油圧回路の構成を示す概略図である。It is the schematic which shows the structure of the hydraulic circuit of the apparatus. 従来の自動車用エンジンにおける位相可変装置（特許文献１）の縦断面図である。It is a longitudinal cross-sectional view of the phase variable apparatus (patent document 1) in the conventional automobile engine. コイルばねの捩りトルク特性を示す図である。It is a figure which shows the torsion torque characteristic of a coil spring. 従来の自動車用エンジンにおける位相可変装置（特許文献２）の縦断面図である。It is a longitudinal cross-sectional view of the phase variable apparatus (patent document 2) in the conventional automobile engine. 渦巻きばねの捩りトルク特性を示す図である。It is a figure which shows the torsion torque characteristic of a spiral spring.

２　カムシャフト
２ｂ　カムシャフト締結ボルト
８　エンジンケース
１０　円環状外筒部
１１　締結ねじ
１２　スプロケット
１６　スプラインケース
１７，３３；２３，３２　ヘリカルスプライン係合部
２０　円環状内筒部
３０　中間部材
３１，４５　角ねじ部
４０　ブレーキ手段である電磁クラッチ
４１　クラッチケース
４２　電磁コイル
４３　摩擦材
４３ａ　摩擦材保持プレート
４４　回転ドラム
４４ａ　回転ドラムの円筒軸
７０　オイル通路
７４　オイル溜まり
ｗ　ばね線材
８０，８０Ａ，８０Ｂ，８０Ｃ　渦巻きコイルばね
８１，８１Ａ，８１Ｂ，８５，８５Ａ，８５Ｂ，８５Ｃ，１８１，１８１Ａ　渦巻きばね部
８３，８７，１８３　最大径コイル
８２，８６，１８２　最小径コイル
８８，８８Ａ，８８Ｂ，８９，８９Ａ　共有旋回領域
８２ａ，８３ａ　外筒部側固定端（ベーンロータ側固定端）
８６ｃ，８７ｂ，１８２ｂ，１８３ｂ　回転ドラム側固定端（外筒部側固定端）
１１０　円環状外筒部
１１２　スプロケット
１１３　外筒部を構成するシューハウジング
１１４　外筒部を構成するフロントプレート
１１５　シュー
１２０　円環状内筒部
１１６　シューハウジングの凹部
１１６ａ　遅角油圧室
１１６ｂ　進角油圧室
１１７，１１７ａ～１１７ｄ　遅角通路
１１８，１１８ａ～１１８ｄ　進角通路
Ｐ　油圧ポンプ
Ｔ　オイルタンク
２００　通路切替弁
２１０　ベーンロータ
２１１　ベーンロータのボス部
２１２　ベーン
２１４　ばね収容室 2 Camshaft 2b Camshaft fastening bolt 8 Engine case 10 Annular outer cylinder part 11 Fastening screw 12 Sprocket 16

Spline cases

17, 33; 23, 32 Helical spline engaging part 20 Annular inner cylinder part 30

Intermediate members

31, 45 Angle Screw part 40 Electromagnetic clutch 41 as brake means Clutch case 42 Electromagnetic coil 43 Friction material 43a Friction material holding plate 44 Rotating drum 44a Cylindrical shaft 70 of rotating drum Oil passage 74 Oil pool

w Spring wire

80, 80A, 80B, 80C

Spiral coil Spring

81, 81A, 81B, 85, 85A, 85B, 85C, 181, 181A

Spiral spring portion

83, 87, 183

Maximum diameter coil

82, 86, 182

Minimum diameter coil

88, 88A, 88B, 89, 89A

Shared turning area

82a , 83a Outer tube side fixed end Vane rotor side fixed end)
86c, 87b, 182b, 183b Rotating drum side fixed end (outer cylinder side fixed end)
110 Annular outer cylinder part 112 Sprocket 113 Shoe housing 114 constituting the outer cylinder part Front plate 115 constituting the outer cylinder part Shoe 120 Annular inner cylinder part 116 Shoe housing recess 116a Retarded hydraulic chamber 116b Advance

hydraulic chamber

117 , 117a to 117d

retarded passage

118, 118a to 118d advanced passage P hydraulic pump T oil tank 200 passage switching valve 210 vane rotor 211 vane rotor boss 212 vane 214 spring accommodating chamber

Claims

　クランクシャフトの駆動力が伝達されるスプロケットを備えた駆動側の円環状外筒部と、前記外筒部に対し同軸状に回動可能に組み付けられ、動弁機構を構成するカムシャフトに延びる従動側の内筒部と、前記外筒部と内筒部にそれぞれヘリカルスプライン係合して外筒部と内筒部間に配設され、軸方向に移動して外筒部に対する内筒部の位相を変える中間部材と、前記内筒部に回転可能に支承された回転ドラムと、前記回転ドラムと軸方向に正対する位置に設けられ、前記回転ドラムに制動力を作用させる円環状の電磁クラッチと、前記回転ドラムと前記外筒部間に介装された復帰ばねと、を備え、
　前記制動力によって、前記回転ドラムに生じる前記外筒部に対する回転遅れに連係して、前記外筒部と前記内筒部間の位相が変わる自動車用エンジンにおける位相可変装置において、
　前記復帰ばねは、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部が軸方向に接近するように並設一体化された渦巻きコイルばねで構成されたことを特徴とする自動車用エンジンにおける位相可変装置。 A drive-side annular outer cylinder portion having a sprocket to which the driving force of the crankshaft is transmitted, and a follower that is rotatably mounted coaxially with respect to the outer cylinder portion and extends to a camshaft constituting the valve mechanism The inner cylinder part on the side, helical spline engagement with the outer cylinder part and the inner cylinder part, respectively, arranged between the outer cylinder part and the inner cylinder part, and moving in the axial direction of the inner cylinder part relative to the outer cylinder part An intermediate member that changes the phase, a rotating drum that is rotatably supported by the inner cylinder portion, and an annular electromagnetic clutch that is provided at a position that faces the rotating drum in the axial direction and applies a braking force to the rotating drum. And a return spring interposed between the rotating drum and the outer cylinder part,
In the phase variable device in the automobile engine, the phase between the outer cylinder part and the inner cylinder part changes in association with the rotation delay with respect to the outer cylinder part generated in the rotary drum by the braking force.
The return spring is composed of a spiral coil spring that is integrated in parallel so that a plurality of spiral spring portions in which the spring wire material spirally swivels on the same plane approaches in the axial direction. Phase variable device in an engine.
　軸方向に互いに接近する前記渦巻きばね部は、各渦巻きばね部をそれぞれ構成する線材コイル同士が線材コイル延在方向に対し僅かに軸方向に傾斜するばね線材の共有旋回領域を介して一体化されたことを特徴とする請求項１に記載の自動車用エンジンにおける位相可変装置。 The spiral spring portions that are close to each other in the axial direction are integrated via a shared swirl region of spring wire rods in which the wire coils constituting the spiral spring portions are slightly inclined in the axial direction with respect to the wire coil extending direction. The phase varying device for an automobile engine according to claim 1.
　前記内筒部の外周には、前記中間部材とヘリカルスプライン係合する前記回転ドラムの円筒軸が配設され、前記円筒軸の外周に、円環状に形成された前記電磁クラッチが配設されたことを特徴とする請求項１または２に記載の自動車用エンジンにおける位相可変装置。 A cylindrical shaft of the rotating drum that engages with the intermediate member in a helical spline is disposed on the outer periphery of the inner cylinder portion, and the electromagnetic clutch formed in an annular shape is disposed on the outer periphery of the cylindrical shaft. The phase varying device for an automobile engine according to claim 1 or 2.
　前記渦巻きコイルばねは、外筒部側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第１の渦巻きばね部と、回転ドラム側固定端が設けられ前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第２の渦巻きばね部とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項２に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring has a first spiral spring portion in which a spring wire is swirled around a minimum diameter coil provided with an outer tube side fixed end and swirling in a direction opposite to the rotation direction of the outer tube portion; A second spiral spring portion in which a spring wire is swirled around a minimum diameter coil provided with a rotating drum side fixed end and swirling in the rotation direction of the outer cylinder portion is separated by a minute distance in the axial direction. 3. The phase varying device for an automobile engine according to claim 2, wherein the phase variable device is disposed and the maximum-diameter coils of the first and second spiral spring portions are continuous with each other via a shared turning region of the spring wire. .
　前記渦巻きコイルばねは、外筒部側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第１の渦巻きばね部と、回転ドラム側固定端が設けられ前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第２の渦巻きばね部とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項２に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring includes a first spiral spring portion in which a spring wire is swirled in a spiral shape inside a maximum diameter coil provided with an outer tube portion side fixed end and swirling in a direction opposite to the rotation direction of the outer tube portion; The second spiral spring part in which the spring wire is swirled inside the maximum diameter coil provided with the rotating drum side fixed end and swirling in the rotation direction of the outer cylinder part is separated by a minute distance in the axial direction. 3. The phase varying device for an automobile engine according to claim 2, wherein the phase variable device is disposed and the minimum diameter coils of the first and second spiral spring portions are continuous with each other via a shared turning region of the spring wire. .
　前記渦巻きコイルばねは、外筒部側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第１の渦巻きばね部と、前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第２の渦巻きばね部と、回転ドラム側固定端が設けられ前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第３の渦巻きばね部とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続し、前記第２，第３の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項２に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring has a first spiral spring portion in which a spring wire is swirled around a minimum diameter coil provided with an outer tube side fixed end and swirling in a direction opposite to the rotation direction of the outer tube portion; A second spiral spring part in which a spring wire turns in a spiral shape around a minimum-diameter coil that turns in the rotation direction of the outer cylinder part, and a rotating drum side fixed end are provided to rotate in the rotation direction of the outer cylinder part A third spiral spring part, in which the spring wire turns in a spiral shape, is arranged inside the maximum diameter coil in a form spaced apart by a minute distance in the axial direction, and the maximum of the first and second spiral spring parts The radial coils are continuous through a shared swirl region of the spring wire, and the minimum diameter coils of the second and third spiral spring portions are continuous through the shared swirl region of the spring wire. The position in the automobile engine described in 2 Varying device.
　前記渦巻きコイルばねは、外筒部側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第１の渦巻きばね部と、前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第２の渦巻きばね部と、回転ドラム側固定端が設けられ前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第３の渦巻きばね部とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続し、前記第２，第３の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項２に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring includes a first spiral spring portion in which a spring wire is swirled in a spiral shape inside a maximum diameter coil provided with an outer tube portion side fixed end and swirling in a direction opposite to the rotation direction of the outer tube portion; A second spiral spring part in which a spring wire turns in a spiral shape and a rotating drum side fixed end are provided inside a maximum diameter coil that turns in the rotation direction of the outer cylinder part, and turns in the rotation direction of the outer cylinder part. A third spiral spring portion in which the spring wire turns in a spiral shape around the minimum diameter coil is arranged in a form spaced apart by a small distance in the axial direction, and the outermost of the first and second spiral spring portions. The small-diameter coils are continuous through a shared swirl region of the spring wire, and the maximum-diameter coils of the second and third spiral spring portions are continuous through the shared swirl region of the spring wire. The position in the automobile engine described in 2 Varying device.
　クランクシャフトの駆動力が伝達されるスプロケットを備えた駆動側の円環状外筒部と、前記外筒部に対し同軸状に回動可能に組み付けられ、動弁機構を構成するカムシャフトに延びる従動側の内筒部と、前記外筒部の内側に形成された凹部と、前記内筒部に一体化されて前記凹部を周方向に遅角油圧室と進角油圧室に区画するとともに、周方向に回動して外筒部に対する内筒部の位相を変えるベーンロータと、前記油圧室に作動油を供給する油圧ポンプと、前記ベーンロータと前記外筒部間に介装された復帰ばねと、を備え、
　前記遅角油圧室と進角油圧室の圧力差によって、前記ベーンロータに生じる前記外筒部に対する回転遅れに連係して、前記外筒部と前記内筒部間の位相が変わる自動車用エンジンにおける位相可変装置において、
　前記復帰ばねは、ばね線材が同一平面上を渦巻状に旋回する複数の渦巻きばね部が軸方向に接近するように並設一体化された渦巻きコイルばねで構成されたことを特徴とする自動車用エンジンにおける位相可変装置。 A drive-side annular outer cylinder portion having a sprocket to which the driving force of the crankshaft is transmitted, and a follower that is rotatably mounted coaxially with respect to the outer cylinder portion and extends to a camshaft constituting the valve mechanism A side inner cylinder part, a recess formed inside the outer cylinder part, and an integral part of the inner cylinder part to divide the recess into a retarded hydraulic chamber and an advanced hydraulic chamber in the circumferential direction. A vane rotor that rotates in a direction to change the phase of the inner cylinder part relative to the outer cylinder part, a hydraulic pump that supplies hydraulic oil to the hydraulic chamber, a return spring interposed between the vane rotor and the outer cylinder part, With
The phase in the automobile engine in which the phase between the outer cylinder part and the inner cylinder part changes due to the rotation delay with respect to the outer cylinder part generated in the vane rotor due to the pressure difference between the retard hydraulic chamber and the advance hydraulic chamber. In the variable device,
The return spring is composed of a spiral coil spring that is integrated in parallel so that a plurality of spiral spring portions in which the spring wire material spirally swivels on the same plane approaches in the axial direction. Phase variable device in an engine.
　互いに接近する前記渦巻きばね部は、各渦巻きばね部をそれぞれ構成する線材コイル同士が線材コイル延在方向に対し僅かに軸方向に傾斜するばね線材の共有旋回領域を介して一体化されたことを特徴とする請求項８に記載の自動車用エンジンにおける位相可変装置。 The spiral spring portions that are close to each other are integrated via a common swirl region of spring wire rods in which the wire coils constituting each spiral spring portion are slightly inclined in the axial direction with respect to the wire coil extending direction. The phase varying device for an automobile engine according to claim 8.
　前記渦巻きコイルばねは、ベーンロータ側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第１の渦巻きばね部と、外筒部側固定端が設けられ前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第２の渦巻きばね部とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項９に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring includes a first spiral spring portion provided with a vane rotor-side fixed end and a spiral wire spring spirally wound around a minimum diameter coil that rotates in a direction opposite to the rotation direction of the outer cylinder portion, and an outer cylinder The second spiral spring part in which the spring wire turns in a spiral shape around the smallest diameter coil that is provided with a part-side fixed end and turns in the rotation direction of the outer cylinder part is arranged in a form that is separated by a minute distance in the axial direction. The phase variable device for an automobile engine according to claim 9, wherein the maximum diameter coils of the first and second spiral spring portions are continuous through a shared turning region of the spring wire.
　前記渦巻きコイルばねは、ベーンロータ側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第１の渦巻きばね部と、外筒部側固定端が設けられ前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第２の渦巻きばね部とが、軸方向に微小距離離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項９に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring includes a first spiral spring portion provided with a vane rotor side fixed end and a spiral wire spring spirally wound inside a maximum diameter coil that rotates in a direction opposite to the rotation direction of the outer cylinder portion, and an outer cylinder The second spiral spring part in which the spring wire turns in a spiral shape is arranged inside the maximum diameter coil that is provided with a part-side fixed end and turns in the rotation direction of the outer cylinder part, and is arranged in a form spaced apart by a small distance in the axial direction. The phase variable device for an automobile engine according to claim 9, wherein the minimum-diameter coils of the first and second spiral spring portions are continuous with each other via a shared turning region of the spring wire.
　前記渦巻きコイルばねは、ベーンロータ側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第１の渦巻きばね部と、前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第２の渦巻きばね部と、外筒部側固定端が設けられ前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第３の渦巻きばね部とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続し、前記第２，第３の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項９に記載の自動車用エンジンにおける位相可変装置。 The spiral coil spring includes a first spiral spring portion provided with a vane rotor side fixed end and having a spring wire that spirally rotates around a minimum diameter coil that rotates in a direction opposite to the rotation direction of the outer cylinder portion, A second spiral spring part in which a spring wire turns in a spiral shape around a minimum diameter coil that turns in the rotation direction of the cylinder part, and a maximum that turns in the rotation direction of the outer cylinder part provided with a fixed end on the outer cylinder side A third spiral spring part in which the spring wire turns in a spiral shape is arranged inside the radial coil in a form that is separated by a minute distance in the axial direction, and the maximum diameter of the first and second spiral spring parts The coils are continuous through a shared swirl region of the spring wire, and the minimum diameter coils of the second and third spiral spring portions are continuous through the shared swirl region of the spring wire. In the automotive engine described in Phase varying device.
　前記渦巻きコイルばねは、ベーンロータ側固定端が設けられ前記外筒部の回転方向と逆方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第１の渦巻きばね部と、前記外筒部の回転方向に旋回する最大径コイルの内側に渦巻状にばね線材が旋回する第２の渦巻きばね部と、外筒部側固定端が設けられ前記外筒部の回転方向に旋回する最小径コイルの周りに渦巻状にばね線材が旋回する第３の渦巻きばね部とが、軸方向に微小距離ずつ離間する形態に配置されるとともに、前記第１，第２の渦巻きばね部の最小径コイル同士がばね線材の共有旋回領域を介して連続し、前記第２，第３の渦巻きばね部の最大径コイル同士がばね線材の共有旋回領域を介して連続することを特徴とする請求項９に記載の自動車用エンジンにおける位相可変装置。
The spiral coil spring includes a first spiral spring portion provided with a vane rotor side fixed end and a spiral wire spring spirally wound inside a maximum diameter coil that pivots in a direction opposite to the rotation direction of the outer cylinder portion, and the outer spiral spring portion. A second spiral spring part in which the spring wire turns in a spiral shape inside the maximum diameter coil that turns in the rotation direction of the cylindrical part, and an outer cylinder part side fixed end are provided, and the outermost part rotates in the rotation direction of the outer cylindrical part. A third spiral spring portion in which a spring wire turns in a spiral shape around the small-diameter coil is disposed in a form spaced apart by a minute distance in the axial direction, and the minimum diameter of the first and second spiral spring portions The coils are continuous through a shared swirl region of the spring wire, and the maximum diameter coils of the second and third spiral spring portions are continuous through the shared swirl region of the spring wire. In the automotive engine described in Varying device.