Showing papers on "Pressure angle published in 1989"

Determination of settings of a tilted head cutter for generation of hypoid and spiral bevel gears

Abstract: Kinematics of Gleason mechanisms of hypoid and spiral bevel cutting machines are considered. These mechanisms are designated to install the position and tilt of the head cutter. The tilt of the head cutter with standard blades provides the required pressure angle. The authors have developed the matrix presentation of kinematics of these meachanisms and basic equations for the required settings. An example is presented based on the developed computation procedure.

Gear type flexible coupling

Abstract: A hob or shaper cutter for making a hub for a misalignment gear coupling having a hub and a sleeve. The hob or shaper cutter has cutting edges. Each cutting edge being inclined at a different angle to the center line of the tooth. The cutting edges are adapted to cut tooth flank surfaces having three adjacent involute shaped areas. Each involute shaped area having a different pressure angle than the involute area adjacent it. The involute areas of each tooth result in teeth with flanks that are generally cylindrical shaped, whereby hub treeth operate with a minimum of interferfence with sleeve teeth when operating with the hub misaligned with the sleeve.

Wildhaber-Novikov Circular Arc Gears: Some Properties of Relevance to Their Design

Abstract: This paper follows an earlier one by Dyson et al. (Proc. R. Soc. Lond . A 403, 313 (1986)) in which a rigorous basic theory of the geometry and kinematics of Wildhaber–Novikov circular arc gears was developed. It was then applied to a pair of helicopter rotor final drive gears, operating in the conditions for which they were designed. The present paper extends this treatment by considering the effect of some variations on the same basic design, and of operating in conditions different from those for which the gears were designed. Aspects considered include the sensitivity of the pressure angle to changes in centres distance, the compromise between this sensitivity and reduction in contact stress, the relation between pressure angle and centres distance over the entire range theoretically possible, the avoidance of interference, the extent of the contact area in terms of position on the teeth, backlash and internal gears.

Process cartridge and image forming apparatus using same

Abstract: The present invention relates to a process cartridge removably mountable on an image forming apparatus comprising a support, a rotary member having an image bearing surface and rotatably supported by the support, and a rotatable developing roller supported by the support, for carrying developer thereon and supplying the developer to the image bearing surface to develop a latent image formed on the image bearing surface A first gear is arranged coaxial with the rotary member, a second gear is arranged coaxial with the developing roller and meshed with the first gear, and a guide means is provided for guiding the developing roller in a direction toward and away from the rotary member The direction in which the developing roller is guided by the guide means is inclined with respect to a straight line connecting the center of rotation of the rotary member to the center of rotation of the developing roller, by an angle between 07×Θ (Θ is a pressure angle of the second gear) and 13×Θ The cartridge further includes a bias means for biasing the developing roller toward the image bearing surface

Gear with circum-scribed teeth

Abstract: The utility model discloses a gear with circum-scribed teeth, belonging to a novel gear of the gear drive in the mechanical drive. The geometric structure is that a centre point on the graduation line of a graduated circle circum-scribes an excircle in the graduation line by a circle with a gear-form radius 4 as the tooth form line, ascertaining a tooth width 5, and forming the circum-scribed teeth; the gear with circum-scribed teeth is formed by the circum-scribed teeth equidistantly distributed on the graduation line. The utility model has small friction angle of the teeth, big contact face, big abrasive resistance, fine drive cooperation and almost no impact between the teeth; the pressure angle is reduced when the number of the teeth is increased, making the radial force of the gear tend to zero; the drive noise is small; the gear form is thick and difficult to undercut or beat the teeth. The application of the gear with circum-scribed teeth can effectively increase the gear drive performance and prolong the service life.

A Procedure Using Manufacturing Variance to Design Gears With Minimum Transmission Error

Abstract: This paper deals with the design of spur gears that have minimum transmission error and are insensitive to manufacturing variance. We address two stages of design: (1) generation of candidate designs (selection of number of teeth, pressure angle, etc.), and (2) tooth profile modification. The first stage involves a search of discrete combinations of design variables, while the second stage utilizes numerical optimization techniques. The key research issue is finding a candidate design and its profile modification that not only has low transmission error, but is insensitive to variations in the design values caused by the manufacturing process. To achieve this goal, the procedure applies Taguchi’s concept of parameter design. In this paper, we consider a design problem with a set specification: fixed center distance, speed ratio, and transmission torque. We seek to find a limited number of candidate designs by applying conventional design generation techniques and some design heuristics. For each candidate design, the procedure determines the optimum profile modification (linear tip relief) by linking the Load Distribution Program (LDP) for gears with an optimization program package (OPTPAK). From the resulting peak optimum, we further seek the statistical optimum using an algorithm developed in this paper. The statistical optimum shows a nominal increase in the transmission error, but is quite insensitive to typical process error associated with gear manufacturing. The developed algorithm readily applies to other gear designs as well as other types of machine elements. In particular, we foresee our procedure to be particularly effective for helical gears. We hope to further our method by developing a means to add statistical heuristics to the discrete design generation stage.

Four-wheel locking system for a motor vehicle

Abstract: In the drive line of a motor vehicle, a planetary transmission is arranged as four-wheel locking system, a braking device acting upon the planet carrier of this planetary transmission. The planetary transmission includes an input sun gear, an output sun gear disposed coaxially next to it, and planet wheels mating simultaneously with both sun gears. In order to keep friction losses low and avoid a self-locking in the planetary transmission, the real pitch module of all gear wheels is as small as possible and proportional to the driving torque to be transmitted, and the operational pressure angle is as large as possible.

Finishing method for tooth surface of toothed wheel

Abstract: PURPOSE:To finish uniformly and precisely the tooth surface of a processed toothed wheel by rotating in mesh the processed toothed wheel and a master toothed wheel for finish-grinding by putting on a load, and at the same time, moving both toothed wheels reciprocatably and relatively against an axis connecting the rotation center shafts of both toothed wheels. CONSTITUTION:A processed toothed wheel 1 and a master toothed wheel 2 for finish- grinding are in mesh at a slide-contacting portion 3, and the standard toothed wheel 2 is rotated by means of the drive rotation of the processed toothed wheel 1. Such brake force as generates a suitable surface load at the sliding portion 3 is put on the rotational shaft of the master toothed wheel 2. The rotational center shaft 6 of the standard toothed wheel 2 is moved reciprocatably in a pressure angle direction 5 against an axis 7 connecting the rotational center shaft 5, 6, of both toothed wheels 1, 2. Accordingly, the master toothed wheel 2 is rotated by the drive rotation of the processed toothed wheel 1 as the surface load is added on the slide-contacting portion 3. And at the same time, being moved reciprocatably is done in the direction of a meshing pressure angle, so the tooth surface of the processed toothed wheel 1 is processed in slide-contact at the slide-contacting portion 3 while in mesh, and being finished uniformly without a tooth form being put into disorder can be done.

Process cartridge driving mechanism for image forming device

Abstract: PURPOSE:To stabilize the fitting position of a process cartridge to a main body by specifying the position relation between the driven gear on the side of the process cartridge and the driving gear on the side of a main body CONSTITUTION:The position relation between the driven gear (drum gear) 23 and the driving gear 3 is so set that a driving force operates on the process cartridge 20 in its fitting direction Namely, the rotation of a driving shaft is transmitted to the drum gear 23 on the side of the process cartridge 20 through the driving gear 3 to drive and rotate a photosensitive drum, etc, on the side of the process cartridge 20, thereby carrying out necessary image formation In the case, the direction of a force F that a tooth flank of the drum gear 23 receives deviates by a gear pressure angle alpha from the perpendicular (l) to the straight line connecting the centers of the drum gear 23 and driving gear 3 and this direction is in the fitting direction of a process unit 20 Consequently, the process cartridge 20 is pressed in this fitting direction at the time of the image formation wherein a driving motor is driven, and its fitting position becomes stable

A Study of Spur Gear Geometry Factor Through Complex Potential Analysis

Abstract: Bending stresses in spur gears have been obtained analytically using the Complex Potential Method of the two-dimensional theory of elasticity and conformal mapping of the tooth profile. Effects of profile shift and sliding friction on geometry factor have been studied for 20 deg pressure angle and numbers of teeth ranging from 20 to 150. It has been shown how these results can be applied to obtain a geometry factor corrected to include either the profile or the coefficient of friction effect in a given gear pair

Optical serial printed head

Abstract: PURPOSE:To maintain a constant developing gap and obtain a favorable print free of ununiformity of development, by a construction comprising an idle gear so disposed that the direction of a contact load between it and a sleeve gear coincides with the direction of pressing a developing sleeve against a photosensitive drum. CONSTITUTION:Where a pressure angle alpha of a gear is 20 deg., an idle gear 31b is so disposed that the position of contact of a sleeve gear 34 with the idle gear 31b is deviated rightward by the pressure angle alpha of 20 deg. from a direction perpendicular to the direction in which a developing sleeve 25 is pressed against a photosensitive drum 11. With a drum gear 30 rotated clockwise, the photosensitive drum 11 is also rotated clockwise, whereas an idle gear 31a is rotated counterclockwise, and the idle gear 31b is rotated clockwise. The idle gear 31b exerts a contact load (f) on the sleeve gear 34 in a direction parallel to the direction of pressing the developing sleeve 25 against the photosensitive drum 11, from the contact position of teeth of the idle gear 31b and the sleeve gear 34.

Method for controlling blade coater

Abstract: PURPOSE:To permit compliance with a wide range of specifications with each of established factors under control for maintenance of a constantly high quality coating, by theoretically calculating the action force of the end of a blade based on deflection theory and the action force of the fluid pressure exerted by a liquid coating material to be applied CONSTITUTION:A liquid coating material is applied to the surface of paper stock by bringing the end of a blade 3 into widthwise contact with the surface of the paper stock 2 which, guided by partially rolling a backing roll 1, is traveling in accordance with the circumferential speed of the roll 1 and by controlling the scrape-off amount of the liquid coating material at a contact point between the paper stock and the blade The action force of fluid pressure of the liquid coating material is calculated considering the traveling speed of the paper stock and, based on the deflecting conditions of the blade determined by the action force of the fluid pressure so calculated and the specifications and wear amount of the blade, the action force of the blade end is theoretically calculated, thereby controlling the set angle theta and pressure angle (i) of the blade with respect to the paper stock, the reactive force of a fulcrum pressing the blade and the position of a stopper 5 regulating the blade end of a coater head 8 held by a swing arm 11

Comments on "Pressure Angle in Loom Shedding Cam Design"

Abstract: situation, there is one principal direction of relative motion, determined by the resultant applied force, and there is no relative motion in the perpendicular direction. But any small additional sideways force will change the direction of slip and give rise to a perpendicular component of motion. 1~undamentally, there is thus only one general slipping mode, and this cannot be associated with rotational or longitudinal grip. What Jang et al. refer to as partial grip modes are really the particular solutions of the process dynamics that cause the motion of the yarn over the surface to be either purely a)~ial (for their &dquo;rotational grip mode&dquo;) or purely rotational (for their &dquo;longitudinal grip mode&dquo;). In mathematical terms, such exact solutions can be found, but in practice, the precise conditions could never be exactly maintained, and so there would be some slip in the direction that appears to be forbidden in their terms. There is no physical grip maintaining the state, as there is in the positive grip mode. Nevertheless, the results of their analysis are valid and useful as a way of indicating the process conditions to aim at, if it is necessary to minimize either axial or rotational slip-in other words, to cause the relative motion to be in a preferred direction.

Mechanism for driving planting claw of transplantation machine

Abstract: PURPOSE:To improve the durability of a gear train giving a longitudinally elongated orbit of a claw tip by using a sun gear, intermediate gears and a final gear each having non-circular form an specifying the tooth profile, cutter pressure angle of the profile and addendum of each gear. CONSTITUTION:A final gear 20 is fixed to a supporting shaft of a transplantation claw-supporting case. Intermediate gears 22, 23 are integrally fixed to the intermediate shaft between the final gear 20 and a sun gear 11. The gears 11, 22, 23 and 20 are non-circular gears having the same teeth number and same module and the bottom of each gear is formed in the form of a curve having connectively varying radius of curvature. The cutter pressure angle of the profile and the addendum of the gear are designed in such a manner as to closely approach the engagement action line A of the engaging part of each gear to the curve of the gear bottom or passing through said curve.

Gear tooth surface finishing device

Abstract: PURPOSE:To improve finishing accuracy of the tooth surface of a gear to be worked by engaging the gear to be worked with a finishing master gear and rotating them together while imposing a load, and relatively reciprocating the rotation axes of both the gears in parallel. CONSTITUTION:A gear 1 to be worked and a master gear 2 are engaged with each other at an abutting part 3. The rotation of the gear 1 to be worked is transmitted to the master gear 2, and both the gears are rotated together, while a braking force acts on the axis 4 of rotation of the master gear 2 to produce a suitable face load on the abutting part 3. And the center axis 4 of the master gear 2 is reciprocated in parallel in S direction with pressure angle alpha. Thus, because the master gear 2 is rotated and simultaneously engaged with the gear 1 while imposing the face load on the abutting part 3 and reciprocated along X direction with pressure angle alpha, the finishing accuracy of the abutting part of the gear 1 to be worked is substantially improved.

Planting claw driving mechanism of transplantation machine

Abstract: PURPOSE:To set the orbit of a transplantation claw tip in the form of a longitudinally oblong loop and to enable the transplantation leaving only a small dent of claw, by specifying various dimensions of sun gear, intermediate gears and final gear CONSTITUTION:The sun gear 11, intermediate gears 22, 23 and final gear 20 are non-circular gears having the same teeth number and the same module Each gear has the following dimensions Ratio of (maximum pitch curve radius Rmax/minimum pitch curve radius Rmin)=13-15 (on each gear), module m=(0025-0075)X(distance between shafts), pressure angle of tool alpha=20-28 deg, addendum <=12m (module) The bottom of the gear forms a curve having continuously varying radius of curvature

Four-wheel drive locking device for a motor vehicle

Abstract: Arranged in the power train of a motor vehicle as an all-wheel drive locking system is a planetary gear mechanism, on the planet carriers of which a braking device acts. The planetary gear mechanism comprises an input sun gear, an output sun gear mounted coaxially next to the latter, and the planet gears simultaneously meshing with the two sun gears. In order to keep the frictional losses low and avoid self-locking in the planetary gear mechanism, the normal module of all the gears is as small as possible and proportional to the driving torque to be transmitted and the operating pressure angle is as large as possible.