Tsubakimoto Chain Company

Masatoshi Sonoda

Kenshi Suzuki

Shunji Sakura

Hiroshi Horie

Aizoh Kubo

Takayuki Morimoto

Hiroki Ishida

Yoshiki Motoshima

Takashi Nakagawa

Makoto Kanehira

Shigekazu Fukuda

Hitoshi Ohara

Takayuki Funamoto

Kazumasa Matsuno

Nobuto Kozakura

Akira Hirai

Toyonaga Saitoh

Tatsuya Hirai

Yoshinori Iwasaki

Tomoyuki Saji

Yudai Takagi

Tsutomu Haginoya

Toyonaga Saito

Takeshi Kondo

Kouichi Ichikawa

Toshihiko Takashima

Naoki Okada

Hiroko Ishida

Yoshinori Tsujino

Takaaki Tsuda

Eiji Ishimoto

Provided is a chain tensioner that can always provide a suitable reaction force and damping force to various tension fluctuations of the chain, has a simple structure, is easy to produce, and also enables a reduction in the production cost. The chain tensionerhas a plungerinserted in a plunger bore, and biasing meansfor biasing the plunger in a protruding direction of the plunger. A plurality of biasing meansare accommodated so as to freely expand and contract inside a high pressure chamberand arranged in series along the protruding direction of the plunger, with a separator plateinterposed therebetween. The separator platehas one or more oil passages that adjust oil flow.

Chain tensioner

A silent chain includes guide plates each of which has a cut-away portion on its inner side and a cut-away portion on its outer side for allowing elastic deformation of the guide plate in the longitudinal direction of the chain so that bowing of the connecting pins of the chain is reduced, and galling of the connecting pins and unbalance of the loads on the link plates of the chain are suppressed. The deepest parts of the respective cut-away portions are longitudinally offset from each other so that longitudinal elastic deformation can occur without impairing the tensile strength of the guide plate.

Silent chain

There is provided a chain comprising guide link rows and non-guide link rows disposed alternately along the length of the chain with each plate of each row overlapping each plate of each of two adjacent rows. For each guide link row, a pair of pins is provided for connecting the guide link rows and non-guide link rows in articulating relationship. The first connecting pin extends into a first hole of each of the guide plates of its guide link row and into and through the second hole of each link plate of an adjacent non-guide link row. The second connecting pin extends into a second hole of each of the guide plates extends into and through a first hole of each link plate of an adjacent non-guide link row. The connecting pins fit tightly into each first hole into which it extends and fits loosely in each second hole into which it extends.

Chain

In a silent chain transmission, the distance between the centers of front and rear pin holes of each of the inner link plates of the chain is smaller than the length of the smallest chord obtained by dividing, by the number of sprocket teeth, the circumference of a circle having a radius extending from the center of the sprocket to the center of a pin hole of a link plate of the chain when the last-mentioned link plate is fully engaged with the sprocket.

Silent chain transmission

In a chain transmission using a hybrid chain having inner and outer links with bushings, or with bushings and rollers, the rollers mesh with a central sprocket, and the link plates have teeth that function as a silent chain, meshing with side sprockets fixed to the central sprocket. The teeth of the link plates of the inner links have a shape different from that of the teeth of the link plates of the outer links. The outer flanks of the teeth can all have the same shape, and the shape difference can be in the shapes of the inner flanks.

Chain transmission device

A hoisting and lowering driving engagement multi-row chain is disclosed, in which bending of the connecting pins in the chain is suppressed to avoid fatigue failure. Additionally, the load carrying balance in the chain width direction is improved, and contact vibrations and contact noises generated between the chain and the hoisting and lowering sprockets are suppressed. Endurance of the bush in the chain is thereby improved. Bending of connecting pins is avoided by press-fitting bushes, through which connecting pins pass, into intermediate tooth plates. This also improves load carrying balance widthwise. Contact noises and vibrations between the bushes and sprockets are suppressed by providing bushes with a separate sprocket engagement portion having a larger diameter than the press-fitting portion of the bushes.

Hoisting and lowering driving engagement multi-row chain

In a silent chain having interleaved guide rows and joint rows, guide plates at the outer sides of the guide rows are connected by engagement pins which extend through overlapping recesses formed on the outer flanks of the guide row plates, and on the inner flanks of the joint row plates. The engagement pins contact sprocket teeth before the outer flanks of the guide row plates contact the sprocket teeth. Cutouts formed in the guide plates adjacent the engagement pins allow the guide plates to deform and thereby absorb the impact imparted to the engagement pins by the sprocket teeth.

In a roller or bushing chain transmission a standard roller or bushing chain having a uniform chain pitch meshes with a sprocket having at least two different tooth form pitches.

In a chain transmission in which a roller chain transmits power from a driving sprocket to one or more driven sprockets, the sprocket teeth are shaped so that at a location radially outward from the sprocket pitch circle, the distance between the front surface of each sprocket tooth to a radial reference line from the sprocket center through the center of the tooth root, is at least as great as the distance from the centerline to the front tooth surface at the pitch circle. The tooth faces merge smoothly with the tooth gap bottom, the sprocket root diameter is smaller than the root diameter according to ISO standards, and the radius of the arcuate tooth gap bottom is greater than the radius of the chain roller.

Chain transmission

In a sprocket for a chain transmission, teeth are disposed around the circumference of the sprocket at intervals. Arc-shaped tooth gap bottoms are formed between adjacent teeth, and each tooth gap bottom is continuous with the facing tooth surfaces of its adjacent teeth. Each tooth is formed so that its thickness is greater than the thickness of an ISO tooth form and gradually becomes thinner from the pitch line toward the tooth head. At engagement of the chain with the sprocket, a roller first comes into contact with a back tooth surface so that polygonal movement is suppressed.

Sprocket for chain

In a slat conveyor, slats for supporting conveyed articles and personnel extend between two side-by-side, spaced, endless roller chains engaged with driving sprockets at one end of the conveying path and driven sprockets at the other end. At a location radially outward from the pitch circle, the distance between the front surface of the sprocket teeth to the tooth center line is at least as great as the distance from the centerline to the front surface at the pitch circle. The tooth faces merge smoothly with the tooth gap bottom, and the root diameter is smaller than the root diameter according to ISO standards.

Conveyance system

A transfer guide for a high-speed power transmission, which can cancel a change in a transmission chain speed so that smooth transmission timing can be realized and a driving power and vibration noises of the transmission chain can be significantly reduced. A curve track T for a transfer guidefor a high-speed power transmission disposed in a transfer position Xjust before a transmission chain, which is traveled at a fixed speed by pressing the chain on the inner circumferential side of the chain with a travel limiting guide R, is meshed with a sprocket S, is defined along an movement passage of the roller Cin the transfer position X. Thus, the change in the transmission chain speed is canceled so that smooth transmission timing can be reliably realized and the driving power and vibration noise of the transmission chain can be significantly reduced.

Transfer guide for high-speed power transmission

In a sprocket for a roller chain, the tooth form is such that the distance between the tooth center line and a part of the front tooth surface, at a location on the tooth head side of the pitch line, is greater than the distance between the tooth center line and the front surface of the tooth along the pitch line. The diameter of the tooth gap bottom circle is smaller than the diameter of a tooth gap bottom circle in a sprocket having an ISO tooth form for the same chain.

A conveying chain guide, in which the stick slip phenomenon of a conveying chain, which meshes with a driving sprocket, and a seasickness phenomenon are removed whereby stable conveying of articles can be smoothly realized and the driving force and vibration noise of a conveying chain can be remarkably reduced. When continuous three rollers C, C, Cin the conveying chain C is to be meshed with the sprocket while gradually descending from the linear rail R for supporting the conveying surface toward the driving sprocket S, in such an arrangement traveling state that always corresponds to the linear rail R for supporting the conveying surface, a transfer position Xand a meshing position X, the guide track T is defined along an movement passage of the roller Cin the transfer position X

Conveying chain guide

In a transmission comprising an endless silent chain and a sprocket the inside tooth faces of the link plates of the chain are identical to tooth profiles, arranged axially, of a hob cutter for forming teeth of the sprocket. The inside and outside tooth faces also satisfy Hi&equals;Ho&plus;Hs, where Hi is the distance from a pin center line Lp to a pitch line Li of the inside tooth faces, Ho is a distance from the pin center line to a pitch line Lo of the outside tooth faces, and Hs is the amplitude of polygonal motion of the chain. Each link plate also has a concave bottom surface between its teeth to avoid interference with edges of the involute teeth arising due to the chain polygonal motion amplitude when the outside tooth faces are brought into meshing engagement with the involute teeth and become seated thereon.

Growing community of inventors

Osaka, Japan

Masatoshi Sonoda