Showing papers on "Pressure angle published in 1994"

Synthesis of contact surfaces of spherical cam-oscillating roller-follower mechanisms: a general approach

Abstract: A novel method of synthesis of the surface geometry of spherical cam-oscillating roll-follower mechanisms is introduced. The approach aims at zeroing the sliding velocity between the cam and the roller, their respective geometries being thus obtained as conical surfaces. The pressure angle is analyzed in detail. Specific results are presented for the application of this synthesis technique to indexing cam mechanisms.

Roll-forming die for helical gears

Abstract: Four different designs for the teeth of a rolling die are disclosed. A pair of the disclosed dies is used to form helical teeth in a cylindrical rod workpiece. All four of the disclosed die tooth embodiments are variations of a common design feature: Namely, at least one segment of the tooth profile for the first tooth of the start portion of the die is formed with a pressure angle substantially larger than the pressure angle of the final basic profile geometry desired for the teeth, and then the profiles of the successive die teeth for the start portion are formed so that the pressure angle of each successive die tooth progressively and gradually decreases in magnitude from the pressure angle of the first tooth until the pressure angle of the final die tooth of the start section is substantially the same as the pressure angle of the desired workpiece teeth.

Quiet sound gear

Abstract: PURPOSE: To set an engagement factor to 3 or more, to uniformize gear precision, and to reduce the generation of noise by a method wherein a pressure angle is specified, the heights of an addendum and a deddendum are increased to a value being 16 or more times as large as that of an ordinary tooth CONSTITUTION: A gear 11 having the number of teeth being 34, a module being 05, the height of an addendum 08, the height of a deddendum being 09 and a gear 12 having the number of teeth being 66, a module being 05, the height of the addendum being 08, and the height of the deddendum being 09 are provided the heights of the addendums and the deddedums of the gears 11 and 12 are increased to a value being 16 times or more as large as those of an ordinary tooth The engagement factors of the gears 11 and 12 is 31 in case of a pressure angle=145°C In this case, contact parts simultaneously engaged with each other are three or four in a number When the gear 11 is driven in the direction of an arrow mark, contact occurs to the vicinity of the addendum part 11a of the gear 11, the central part 11b and the deddendum part 11c of a tooth Thus, since even a gear having low precision is actually always engaged by using two or more teeth, gear precision is uniformized and any influence is hardly exercised, whereby the generation of engagement noise owing to a fluctuation in rotation is reduced COPYRIGHT: (C)1995,JPO

Developing device and process cartridge using that

Abstract: PURPOSE:To prevent displacement of a developer sleeve from a photosensitive drum by the force in pressure angle direction caused by engagement of gears. CONSTITUTION:The device has a supporting and guiding member 45 and a supporting and guiding member 46. The member 45 guides a bearing 43 which supports the end of the driving side of the sleeve 4 so that the bearing can displace in the direction Q at an angle 0.7Xtheta to 1.3Xtheta (theta is the pressure angle of the gear) from the line L connecting the photosensitive drum 2 and the rotation center of the sleeve 4. The member 46 guides the bearing 44 which supports the non-driving side end of the sleeve 4 in the direction R between -6 and +6 degree from the line L. The magnet is supported in the inside of the sleeve in the driving side and independently supported from the sleeve 4 in the nondriving side.

Paw oscillating type ratchet mechanism

Abstract: The utility model relates to a pawl oscillating type ratchet mechanism, which is composed of ratchet wheels, ratchets and pawls. The utility model is characterized in that the pawl pushes the ratchet wheel to rotate to touch the ratchet; the connecting line of a tooth crest and an oscillating shaft of the pawl forms a closed angle beta with the direction of movement of the pawl; the closed angle beta is greater than or equal to the sum of a ratchet pressure angle alpha and a friction angle; the closed angle beta is smaller than 40 DEG. The utility model can realize high precision transmission with smaller pawls and ratchets and can reduce the movement loss to minimum and the theoretical value can be zero. The utility model is capable of combining with a superposed ratchet wheel mechanism and the flexual and folding working surfaces of the ratchets and the pawls are acceptable.

Truck lock type differential restricting device

Abstract: PURPOSE: To perform a smooth differential restricting action by generating always uniform thrust force as the whole device, by constituting so that phases of meshing points of mutual respective meshing teeth in plural pinion gears and left and right side gears meshing with these become respectively different from each other. CONSTITUTION: A device is constituted so that phases of meshing points of mutual respective meshing teeth in plural pinion gears 3 and 3.and left and right side gears 4 and 5 meshing with these become respectively different from each other. When the phases of the plural meshing points to simultaneously mesh with each other are respectively different from each other, since thrust force to the side gears 4 and 5 generated by reaction of bevel teeth meshing between the pinion gear 3 and the side gear 4 by driving force at a certain time acts as the sum total of one generated in the different size according to a pressure angle at the respective meshing points, left and right multiple disk clutches 6 and 7 are brought into pressure contact with each other by generation of always uniform thrust force as a whole, and stable differential restricting torque is obtained, and a smooth differential restricting action can be performed. COPYRIGHT: (C)1996,JPO

Computer-Aided Thread Grinding without Form Dressing with Monitoring System to Prevent Wheel Interference.

Abstract: A previous report proposed a computer-aided thread grinding method for generating helicoid without form dressing, using a standard-shaped grinding wheel independent of the final helicoid. The method uses a simple conical or plain wheel, without limitations of the diameter and base angle. The wheel axis is set three-dimensionally at the optimum computed angle of inclination. When the wheelthickness is large or the thread pitch is small, there is a risk of interference between the back of the wheel and helical surface opposing the helical surface being ground. When the grinding wheel is fed radially to the thread with a small thread pressure angle, there is also a risk of deformation of the helical surface generated. This report introduces a monitoring system to the original computer-aided thread grinding method, for protection against undesirable wheel interference, considering an axial displacement of the wheel and the maximum allowable displacement. The investigation shows that the monitoring system is effective to determine limits of thread dimensions without undesirable wheelinterference.

Wire rod for wrapping connector driving

Abstract: PURPOSE:To ensure power transmission while being compact by forming teeth at equal pitches around the whole periphery of a wire rod of circular cross section. CONSTITUTION:Teeth 2 for preventing a slip with a pulley during the transmission of driving force are formed around a wire rod body 3. The shape of the tooth 2 is not specified if the tooth 2 can be meshed with the tooth of the pulley, but the same shape as the tooth form of a gear is desirable from the viewpoint of transmission efficiency. Power transmission torque can be also controlled by changing the height (h) and pressure angle alpha of the tooth 2. This wire rod F for wrapping connector driving is manufactured by drawing fused synthetic resin material through a die to form the wire rod 3 and forming the tooth part 2 through a toothed metal mold.

Load sharing in~etallic)and~on-metallic gears

Abstract: >> A review of work odooth deformatiohnd load sharing in non-metallic gears is presented. Ahnite element analys;&employing the flexibility method for contacting bodies is used to model tooth deflections and contact patterns ’Betweenheshing geary For metallic gears the change in contact ratio between the theoretical and running values is shown to be small. However, for low modulus, nonYtallic gears the change in contact ratio is large and can give cause for concern. The benefits and disadvantages of this increase in +.Qperating contact ratias stated. Finally, the possibility of characterizing the change in operating contact ratio in a non-dimensional form is discussed. NOTATION elastic modulus force tangential transmitted force final gap between contacting nodes initial gap between contacting nodes ideal contact ratio application factor module number of teeth rotational speed base pitch rigid body displacement base radius radius real contact ratio flexibility matrix torque face width contact ratio factor for bending stress tooth form factor for bending stress actual length of the line of contact roll angle deformation viscosity rigid body rotation coefficient of friction Poisson’s ratio non-dimensional elasticity parameter pressure angle root bending stress