JPH04160258A - Straight motion mechanism - Google Patents

Straight motion mechanism

Info

Publication number
JPH04160258A
JPH04160258A JP2286260A JP28626090A JPH04160258A JP H04160258 A JPH04160258 A JP H04160258A JP 2286260 A JP2286260 A JP 2286260A JP 28626090 A JP28626090 A JP 28626090A JP H04160258 A JPH04160258 A JP H04160258A
Authority
JP
Japan
Prior art keywords
tooth
rack
active
passive rack
racks
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2286260A
Other languages
Japanese (ja)
Other versions
JPH0751979B2 (en
Inventor
Mikiaki Hirai
幹了 平井
Hiroyuki Takenaka
竹中　浩之
Hidekazu Yokoi
横井　秀和
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nabtesco Corp
Original Assignee
Teijin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Teijin Seiki Co Ltd filed Critical Teijin Seiki Co Ltd
Priority to JP2286260A priority Critical patent/JPH0751979B2/en
Priority to DE69102392T priority patent/DE69102392T2/en
Priority to EP91309602A priority patent/EP0482827B1/en
Priority to US07/777,717 priority patent/US5187994A/en
Publication of JPH04160258A publication Critical patent/JPH04160258A/en
Priority to SG128694A priority patent/SG128694G/en
Priority claimed from SG128694A external-priority patent/SG128694G/en
Priority to HK5895A priority patent/HK5895A/en
Publication of JPH0751979B2 publication Critical patent/JPH0751979B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/02—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms the movements of two or more independently moving members being combined into a single movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
    • F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

PURPOSE:To obtain a straight motion mechanism of a large thrust in a small size by making plural active racks carry out a fluctuation crank operation while maintaining a specific phase difference by the rotation of crankshafts, and forming a corrugated tooth form at one side either a passive rack or an active rack, while forming a circular arc tooth form at the other side. CONSTITUTION:The tooth T1 of a passive rack 11 is formed in a cycloidal curve form corrugated tooth profile, while the tooth T2 of active racks 12A to 12C is in a circular arc form tooth profile which has the radius same as a circle to be the base of the tooth profile. The active racks 12A to 12C are supported by the respective eccentric cams 15a, 15b, and 15c of a pair of crankshafts 15A and 15B to make each tooth T2 oppose to the passive rack 11, and when the gears 16A and 16B linked to one end sides of the crankshafts 15A and 15B are rotated, the plural active racks 12A to 12C can carry out a fluctuation crank operation while maintaining a specific phase difference. Since the active racks 12A to 12C push the passive rack 11 through plural teeth T2, the pressure applied to each tooth T2 can be reduced, and a large thrust of straight motion mechanism can be realized.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、回転運動を直線運動に変換する直進運動機構
に関し、詳しくは揺動型ラックによりその変換を行うよ
うにした直進運動機構に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a linear motion mechanism that converts rotational motion into linear motion, and more particularly to a linear motion mechanism in which the conversion is performed by a swinging rack.

〔従来の技術〕[Conventional technology]

従来、工作機械の送り機構等には、回転運動を直線運動
に変換する直進運動機構が設けられており、この直進運
動機構には、機械全体の小型化の要求に応えるべく構成
の簡素なものが用いられている。Conventionally, the feed mechanism of machine tools has been equipped with a linear motion mechanism that converts rotational motion into linear motion. is used.

この種の直進運動機構としては、例えば第６図に示すラ
ックピニオン機構が知られている。この機構では、ピニ
オン１の回転によりこのピニオン１に噛み合うラック２
を軸方向に移動させる。また、第７図に示すビンラック
機構も知られており、この機構では、ラック３とこのラ
ック３に噛み合うビン歯車４との間で運動方向の変換が
なされるようになっている。As this type of linear movement mechanism, for example, a rack and pinion mechanism shown in FIG. 6 is known. In this mechanism, a rack 2 is engaged with the pinion 1 by rotation of the pinion 1.
move in the axial direction. A bin rack mechanism shown in FIG. 7 is also known, and in this mechanism, the direction of motion is changed between the rack 3 and the bin gear 4 that meshes with the rack 3.

〔発明が解決しようとする課題］ しかしながら、このような従来の直進運動機構にあって
は、入力側部材、例えばピニオン１やビン歯車４の回転
を別設の減速機によって減速する構成となっていたため
、直進運動機構が大型化してしまうという問題があった
。[Problems to be Solved by the Invention] However, in such conventional linear motion mechanisms, the rotation of the input side members, such as the pinion 1 and the pin gear 4, is decelerated by a separate speed reducer. Therefore, there was a problem in that the linear movement mechanism became large.

また、ビニオンｌとラック２の噛み合い歯数、又は、ラ
ック３とピン歯車４の噛み合い歯数が１又は２程度と少
ないため、所定のラック推力を発揮させるためには、そ
れぞれの歯幅を大きくして一定の歯面圧に耐え得るよう
にしなければならず、やはり、直進運動機構の大型化を
招いていた。In addition, since the number of meshing teeth between the binion l and the rack 2, or the number of meshing teeth between the rack 3 and the pin gear 4 is small at about 1 or 2, in order to exert a predetermined rack thrust, the width of each tooth must be increased. It had to be able to withstand a certain level of tooth surface pressure, which also led to an increase in the size of the linear movement mechanism.

そこで、本発明は、小型で推力の大きい直進運動機構を
提供することを目的とする。Therefore, an object of the present invention is to provide a linear movement mechanism that is small and has a large thrust.

〔課題を解決するための手段〕[Means to solve the problem]

本発明は、上記目的達成のため、複数の歯を有する受動
ラックと、受動ラックの歯と同一ピッチの複数の歯が形
成され、各々が該歯を受動ラックに当接させた複数の能
動ラックと、複数の能動ラックを所定の位相差を保って
支持するとともに、該位相差で複数の能動ラックを揺動
クランク運動させるクランク軸と、を備え、受動ラック
および能動ラックのうち一方に波形の歯形を形成し、他
方に円弧状の歯形を形成したことを特徴とするものであ
る。To achieve the above object, the present invention provides a passive rack having a plurality of teeth, and a plurality of active racks in which a plurality of teeth are formed with the same pitch as the teeth of the passive rack, and each tooth is brought into contact with the passive rack. and a crankshaft that supports the plurality of active racks while maintaining a predetermined phase difference and causes the plurality of active racks to perform rocking crank motion using the phase difference. It is characterized by forming a tooth profile and forming an arcuate tooth profile on the other side.

〔作用〕[Effect]

本発明では、受動ラックの歯と同一ピンチの歯を有する
複数の能動ラックが、該歯を受動ラックに当接させた状
態でクランク軸に支持され、該クランク軸の回転により
複数の能動ラックが所定の位相差を保って揺動クランク
運動する。したがって、クランク軸が一回転すると、少
なくとも何れか１つの能動ラックによって受動ラックが
常に推進方向に押動され、受動ラックの直線運動が得ら
れる。また、このとき、受動ラックと能動ラックが多数
の歯を当接させているから、両ラックを小型にしても歯
面圧があまり高くならず、小型でも推力の大きな直進運
動機構が実現可能となる。In the present invention, a plurality of active racks having teeth of the same pinch as the teeth of a passive rack are supported by a crankshaft with the teeth in contact with the passive rack, and rotation of the crankshaft causes the plurality of active racks to rotate. The oscillating crank moves while maintaining a predetermined phase difference. Therefore, when the crankshaft makes one rotation, the passive rack is always pushed in the propulsion direction by at least one of the active racks, and linear movement of the passive rack is obtained. In addition, since the passive rack and active rack have many teeth in contact with each other, the tooth surface pressure does not increase too much even if both racks are made small, making it possible to realize a linear motion mechanism with a large thrust despite its small size. Become.

〔実施例〕〔Example〕

以下、本発明を図面に基づいて説明する。 Hereinafter, the present invention will be explained based on the drawings.

第１〜５図は本発明の一実施例を示す図である。1 to 5 are diagrams showing one embodiment of the present invention.

まず、構成を説明する。First, the configuration will be explained.

第１〜３図において、１１は複数の歯Ｔ１を有する受動
ラック、１２Ａ、１２Ｂ、１２Ｃは受動ラック１１の歯
Ｔ１のピッチＰと同一ピッチの複数の歯Ｔ２が形成され
た複数の（本実施例では３つの）能動ラックである。受
動ラック１１の歯Ｔ１は、第４図に示すようなトロコイ
ド曲線又はサイクロイド曲線状（波形）の歯形に形成さ
れており、能動ラック１２Ａ〜１２Ｃの歯Ｔ２はこの歯
形の基準となる円と同一の半径Ｒを有する円弧状の歯形
に形成されている。また、受動ラック１１は複数個の循
環式のボール１３を介してケース１４に軸方向移動自在
に結合しており、受動ラック１１０両側面にはボール１
３に係合する溝部１１ａが形成され、ケース１４の底部
１４ａ内にはボール循環通路１４ｂが形成されている。In FIGS. 1 to 3, reference numeral 11 denotes a passive rack having a plurality of teeth T1, and 12A, 12B, and 12C refer to a plurality of teeth T2 having the same pitch as the pitch P of the teeth T1 of the passive rack 11 (in this embodiment). In the example there are three) active racks. The teeth T1 of the passive rack 11 are formed in a trochoidal or cycloidal curve (waveform) tooth profile as shown in FIG. It is formed into an arcuate tooth shape with a radius R of . Further, the passive rack 11 is coupled to the case 14 via a plurality of circulating balls 13 so as to be freely movable in the axial direction.
A groove 11a that engages with the case 14 is formed in the bottom 14a of the case 14, and a ball circulation passage 14b is formed in the bottom 14a of the case 14.

能動ラック１２Ａ〜１２Ｃは、それぞれ歯Ｔ２側を受動
ラック１１に対向させるよう一対のクランク軸１５ＡＳ
１５Ｂのそれぞれの偏心カム部１５ａ、１５ｂ、１５Ｃ
に支持されており、クランク軸１５Ａ、１５Ｂが各一対
の軸受１９．２０を介してケース１４に支持されること
により、各能動ラック１２Ａ〜１２Ｃの歯Ｔ２は受動ラ
ック１１に当接している。クランク軸１５Ａ、１５Ｂは
、その偏心カム部１５ａ〜１５ｃが例えば等角度間隔に
形成されており、クランク軸１５Ａ、１５Ｂの一端側に
連結された歯車１６Ａ、１６Ｂが回転するとき、複数の
能動ラック１２Ａ〜１２Ｃを所定の位相差（本実施例で
は能動ラック数に対応する等しい位相差１２０°）を保
って揺動クランク運動させることができる。また、歯車
１６Ａ、１６Ｂには入力歯車１７が噛み合っており、入
力歯車１７は図示しない軸受によりケース１４に軸支さ
れた入力シャフト１８に連結されている。この入力シャ
フト１８の一端部はケース１４から外方に突出し、この
一端部から回転入力を入力するようになっている。The active racks 12A to 12C each have a pair of crankshafts 15AS so that the tooth T2 side faces the passive rack 11.
15B, each eccentric cam part 15a, 15b, 15C
The teeth T2 of each of the active racks 12A to 12C are in contact with the passive rack 11 because the crankshafts 15A and 15B are supported by the case 14 via each pair of bearings 19 and 20. The crankshafts 15A, 15B have eccentric cam portions 15a to 15c formed at equal angular intervals, and when gears 16A, 16B connected to one end of the crankshafts 15A, 15B rotate, a plurality of active racks are formed. 12A to 12C can be subjected to rocking crank motion while maintaining a predetermined phase difference (in this embodiment, an equal phase difference of 120 degrees corresponding to the number of active racks). Further, an input gear 17 meshes with the gears 16A and 16B, and the input gear 17 is connected to an input shaft 18 that is pivotally supported by the case 14 by a bearing (not shown). One end of this input shaft 18 protrudes outward from the case 14, and rotational input is input from this one end.

なお、受動ラック１１と能動ラック１２Ａ〜１２Ｃとの
歯形状を逆にして、能動ラック１２Ａ〜１２Ｃに波形の
歯形を形成し、受動ラック１１に円弧状の歯形を形成す
ることもできる。It is also possible to reverse the tooth shapes of the passive rack 11 and the active racks 12A to 12C so that the active racks 12A to 12C have wave-shaped tooth shapes, and the passive rack 11 has arc-shaped tooth shapes.

また、第１〜３図において、２１．２２．２３は能動ラ
ック１２とクランク軸１５Ａ、１５Ｂの偏心カム部１５
ａ、１５ｂ、１５ｃとの間に介装されたニードル軸受で
あり、２４は歯車１６Ａ、１６Ｂをクランク軸１５Ａ、
１５Ｂに固定するキー、２５はケース１４の底部１４ａ
を固定するボルト、２６はケース１４の蓋部１４ｃを固
定するピン、２７．２８は軸受１９．２０を介してケー
ス１４とクランク軸１５Ａ、１５Ｂの軸方向のずれを規
制するそれぞれ複数の止め輪、２９は受動ラック１１の
移動端を決定するストッパである。In addition, in FIGS. 1 to 3, 21, 22, and 23 are the active rack 12 and the eccentric cam portions 15 of the crankshafts 15A and 15B.
a, 15b, 15c, and 24 is a needle bearing interposed between the gears 16A, 16B and the crankshaft 15A,
Key fixed to 15B, 25 is the bottom 14a of the case 14
26 is a pin that fixes the lid part 14c of the case 14, and 27 and 28 are a plurality of retaining rings that restrict axial deviation between the case 14 and the crankshafts 15A and 15B via bearings 19 and 20. , 29 are stoppers that determine the moving end of the passive rack 11.

次に、作用を説明する。Next, the effect will be explained.

外部からの動力により入力シャフト１８が回転されると
、入力歯車１７が回転し、この入力歯車１７と噛み合う
歯車１６Ａ、１６Ｂが同一回転方向に回転することによ
って、クランク軸１５Ａ、１５Ｂが駆動され、複数の能
動ラック１２Ａ〜１２Ｃが所定の位相差を保って揺動ク
ランク運動する。When the input shaft 18 is rotated by external power, the input gear 17 rotates, and the gears 16A and 16B that mesh with the input gear 17 rotate in the same rotational direction, thereby driving the crankshafts 15A and 15B. The plurality of active racks 12A to 12C perform rocking crank motion while maintaining a predetermined phase difference.

このとき、クランク軸１５Ａ、１５Ｂの回転に伴って、
能動ラック１２Ａ〜１２Ｃが例えば第５図（ａ）〜（Ｃ
）に示すように偏心揺動し、歯Ｔ２に歯Ｔ１の一面側を
押された受動ラック１１が第５図の矢印Ｘ方向へ移動す
る。また、能動ラック１２Ａ〜１２Ｃはその数に応じた
所定の位相差を保って揺動クランク運動するから、クラ
ンク軸１５Ａ、１５Ｂの一回中に複数の能動ラック１２
Ａ〜１２Ｃのうち少なくとも何れか１つが歯Ｔ１の前記
−面側で受動ラック１１に当接することになり、その能
動ラックの揺動により受動ラック１１が矢印Ｘ方向に押
動される。At this time, as the crankshafts 15A and 15B rotate,
For example, the active racks 12A to 12C are shown in FIGS.
), the passive rack 11 swings eccentrically, and one side of the tooth T1 is pushed by the tooth T2, and the passive rack 11 moves in the direction of the arrow X in FIG. In addition, since the active racks 12A to 12C perform rocking crank motion while maintaining a predetermined phase difference corresponding to the number of active racks 12A to 12C, a plurality of active racks 12
At least one of A to 12C comes into contact with the passive rack 11 on the negative surface side of the tooth T1, and the swinging of the active rack pushes the passive rack 11 in the direction of the arrow X.

したがって、クランク軸１５Ａ、１５Ｂが一回転すると
、受動ラック１１は歯Ｔｌ　、Ｔ２の１歯分（ピッチ分
）移動する。Therefore, when the crankshafts 15A and 15B rotate once, the passive rack 11 moves by one tooth (pitch) of the teeth Tl and T2.

一方、入力シャフト１８への回転入力を逆向きにすると
、クランク軸１５Ａ、１５Ｂが逆転し２、受動ラック１
１は矢印Ｘ方向と反対の方向へ移動する。On the other hand, when the rotational input to the input shaft 18 is reversed, the crankshafts 15A and 15B are reversed 2 and the passive rack 1
1 moves in the direction opposite to the arrow X direction.

ここで、受動ラック１１の移動中における受動ラック１
１と能動ラック１２Ａ〜１２Ｃの歯Ｔ１、Ｔ２の噛み合
いについて考察すると、受動ラック１１に推力を与える
能動ラック１２Ａ〜１２Ｃは、受動ラック１１に沿って
適宜数配列された複数の歯Ｔ２で受動ラック１１を押圧
するため、各歯Ｔ２に加わる圧力は小さ（て済む。従っ
て、推力の大きな直進運動機構を実現できる。また、能
動ラック１２Ａ〜１２Ｃのクランク運動により、クラン
ク軸１５Ａ、１５Ｂの一回転に対して受動ラック１１の
歯Ｔ１の１歯分の減速出力が得られるから、減速機を別
設する必要がなく、前記歯面圧が小さいことと相俟って
非常に小型の直進運動機構が実現可能となる。さらに、
ラック同志を組合せた構成から角形にでき、受動ラック
１１を案内する構造としてボール１３等を利用した簡素
で信顛性の高いものにできる。Here, the passive rack 1 while the passive rack 11 is moving
1 and the teeth T1 and T2 of the active racks 12A to 12C, the active racks 12A to 12C that provide thrust to the passive rack 11 have a plurality of teeth T2 arranged in an appropriate number along the passive rack 11. 11, the pressure applied to each tooth T2 is small. Therefore, a linear movement mechanism with large thrust can be realized. Also, by the crank movement of the active racks 12A to 12C, one revolution of the crankshafts 15A and 15B is Since the deceleration output corresponding to one tooth T1 of the passive rack 11 can be obtained, there is no need to separately install a decelerator, and together with the low tooth surface pressure, a very small linear motion mechanism can be achieved. becomes possible.Furthermore,
It can be made into a rectangular configuration by combining racks, and it can be made simple and highly reliable by using balls 13 or the like as a structure for guiding the passive rack 11.

〔効果〕〔effect〕

本発明によれば、受動ラックの歯と同一ピッチの歯を有
する複数の能動ラックを、クランク軸の回転により所定
の位相差を保って揺動クランク運動させ、クランク軸の
回転中常に少なくとも何れか１つの能動ラックによって
受動ラックを推進方向に押動するようにしているので、
受動ラックの安定した直線運動を得る゛ことができ、受
動ラックと能動ラックを多数の歯で当接させて歯面圧を
小さくし、小型で推力の大きな直進運動機構を実現する
ことができる。According to the present invention, a plurality of active racks having teeth having the same pitch as the teeth of a passive rack are caused to undergo rocking crank motion while maintaining a predetermined phase difference by rotation of the crankshaft, and at least one of the active racks is always rotated during rotation of the crankshaft. Since one active rack pushes the passive rack in the propulsion direction,
Stable linear motion of the passive rack can be obtained, the passive rack and active rack are brought into contact with each other with a large number of teeth, the tooth surface pressure is reduced, and a compact linear motion mechanism with large thrust can be realized.

【図面の簡単な説明】[Brief explanation of drawings]

第１〜５図は本発明に係る直進運動機構の一実施例を示
す図であり、 第１図はその概略構成を示す斜視図、 第２図はその外観正面図、 第３図は第２図のＡ−Ａ矢視断面図、 第４図はそのラック形状の説明図、 第５図はその作用説明図である。 第６．７図はそれぞれ従来例を示す図であり、第６図は
ラックピニオン機構の構成図、第７図はピンラック機構
の構成図である。 １１・・・・・・受動ラック、 １２Ａ、１２Ｂ、１２Ｃ・・・・・・能動ラック、１５
Ａ、１５Ｂ・・・・・・クランク軸、１６Ａ、１６Ｂ・
・・・・・歯車、 １７・・・・・・入力歯車、 Ｔ１・・・・・・受動ラックの歯、 Ｔ２・・・・・・能動ラックの歯。1 to 5 are diagrams showing one embodiment of the linear motion mechanism according to the present invention, FIG. 1 is a perspective view showing its schematic configuration, FIG. 2 is an external front view thereof, and FIG. FIG. 4 is an explanatory diagram of the rack shape, and FIG. 5 is an explanatory diagram of its operation. 6 and 7 are diagrams showing conventional examples, respectively. FIG. 6 is a configuration diagram of a rack and pinion mechanism, and FIG. 7 is a configuration diagram of a pin rack mechanism. 11... Passive rack, 12A, 12B, 12C... Active rack, 15
A, 15B... Crankshaft, 16A, 16B.
... Gear, 17 ... Input gear, T1 ... Passive rack tooth, T2 ... Active rack tooth.

Claims (1)

【特許請求の範囲】 複数の歯を有する受動ラックと、 受動ラックの歯と同一ピッチの複数の歯が形成され、各
々が該歯を受動ラックに当接させた複数の能動ラックと
、 複数の能動ラックを所定の位相差を保って支持するとと
もに、該位相差で複数の能動ラックを揺動クランク運動
させるクランク軸と、を備え、受動ラックおよび能動ラ
ックのうち一方に波形の歯形を形成し、他方に円弧状の
歯形を形成したことを特徴とする直進運動機構。[Scope of Claims] A passive rack having a plurality of teeth; a plurality of active racks each having a plurality of teeth having the same pitch as the teeth of the passive rack, each of which abuts the tooth on the passive rack; A crankshaft that supports the active racks while maintaining a predetermined phase difference and causes a plurality of active racks to perform rocking crank motion using the phase difference, and has a wave-shaped tooth profile formed on one of the passive rack and the active rack. , a linear movement mechanism characterized by forming an arcuate tooth profile on the other side.
JP2286260A 1990-10-23 1990-10-23 Linear motion mechanism Expired - Lifetime JPH0751979B2 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2286260A JPH0751979B2 (en) 1990-10-23 1990-10-23 Linear motion mechanism
DE69102392T DE69102392T2 (en) 1990-10-23 1991-10-17 Mechanism for converting a rotational movement into a longitudinal movement.
EP91309602A EP0482827B1 (en) 1990-10-23 1991-10-17 Rotary motion to longitudinal motion converting mechanism
US07/777,717 US5187994A (en) 1990-10-23 1991-10-21 Rotary motion to longitudinal motion converting mechanism
SG128694A SG128694G (en) 1990-10-23 1994-09-01 Rotary motion to longitudinal motion converting mechanism
HK5895A HK5895A (en) 1990-10-23 1995-01-12 Rotary motion to longitudinal motion converting mechanism

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2286260A JPH0751979B2 (en) 1990-10-23 1990-10-23 Linear motion mechanism
SG128694A SG128694G (en) 1990-10-23 1994-09-01 Rotary motion to longitudinal motion converting mechanism

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP5028328A Division JPH0772587B2 (en) 1993-02-18 1993-02-18 Linear motion mechanism

Publications (2)

Publication Number Publication Date
JPH04160258A true JPH04160258A (en) 1992-06-03
JPH0751979B2 JPH0751979B2 (en) 1995-06-05

Family

ID=26556230

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2286260A Expired - Lifetime JPH0751979B2 (en) 1990-10-23 1990-10-23 Linear motion mechanism

Country Status (1)

Country Link
JP (1) JPH0751979B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19512780A1 (en) * 1994-04-06 1995-10-12 Teijin Seiki Co Ltd Rotary to linear motion conversion mechanism

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103032263B (en) * 2011-10-01 2015-04-01 陈伟 Hypocycloid yawing gearbox for wind driven generator

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19512780A1 (en) * 1994-04-06 1995-10-12 Teijin Seiki Co Ltd Rotary to linear motion conversion mechanism
JPH07280057A (en) * 1994-04-06 1995-10-27 Teijin Seiki Co Ltd Rectilinear motional mechanism, its manufacture and working machine to realize manufacture
US5582068A (en) * 1994-04-06 1996-12-10 Teijin Seiki Co., Ltd. Motion transforming mechanism and system for producing same
DE19512780C2 (en) * 1994-04-06 1999-09-02 Teijin Seiki Co Ltd Movement conversion mechanism

Also Published As

Publication number Publication date
JPH0751979B2 (en) 1995-06-05

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