CA2582737A1 - Out-of-round rotation disc for a timing drive - Google Patents
Out-of-round rotation disc for a timing drive Download PDFInfo
- Publication number
- CA2582737A1 CA2582737A1 CA002582737A CA2582737A CA2582737A1 CA 2582737 A1 CA2582737 A1 CA 2582737A1 CA 002582737 A CA002582737 A CA 002582737A CA 2582737 A CA2582737 A CA 2582737A CA 2582737 A1 CA2582737 A1 CA 2582737A1
- Authority
- CA
- Canada
- Prior art keywords
- rotation disk
- teeth
- rotation
- disk
- looping
- 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.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/024—Belt drive
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
-
- 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
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Pulleys (AREA)
Abstract
The invention relates to a rotating disc, which may be rotated about a rotation axis by a rotational angle and a rotating disc profile with has at least one elevation, a given number of teeth, arranged around the rotating disc profile, each with a mid-point, whereby the mid-points of adjacent teeth have a given separation, a rotating disc radius, which is a function of the rotational angle and a mean radius and a resulting rotating disc contact curve, the mean radius being selected such that a rotating arc length for the rotating disc contact curve is the same as the product of the given separation of the mid-points of adjacent teeth and the number of teeth. The invention further relates to a corresponding method for embodiment of at least one rotating disc, rotating about a rotational axis by a rotation angle, for a timing drive.
Description
Title of the invention Out-of-round rotation disk for a timing drive S
Description Field of the invention The invention relates to an out-of-round or noncircular rotation disk for a timing drive and to a method for constructing and designing a rotation disk of this type.
The present invention relates, furthermore, to a computer system for designing a rotation disk of this type.
Background of the invention Synchronous drive systems, such as, for example, systems based on control belts, are in widespread use in motor vehicles and in industrial applications.
In motor vehicles, for example, control belts or control chains are used for driving camshafts which open and close engine inlet and outlet valves. Other devices, too, such as, for example, water and fuel pumps, may likewise be driven by means of a belt of this type or a chain of this type.
Strand oscillations, as they may be referred to, constitute system-specific ef-fects on wrap-around gears of this type. In principle, a tension means, such as, for example, a chain or a belt, used in wrap-around gears may be excited into transverse, longitudinal and torsional oscillations. Such oscillations of the ten-sion means may appreciably disturb the operation of an overall drive system.
Their occurrence leads to noises and increased structural loads on components of the drive system due to dynamic force peaks which shorten the useful life of the overall system. Furthermore, for example, in the event of an impact of the belt strand against adjacent parts which is brought about by transverse oscilla-tions, both these parts and the belt itself, too, may be damaged. Even after a short time, a failure of the overall drive system may therefore occur. Such strand oscillations are excited by a drive torque of the internal combustion en-gine which takes place nonuniformly. In this case, moreover, fluctuations in the belt or chain stresses may arise, which may likewise cause higher wear and a shorter useful life of the belt or chain.
It is known, in drive systems of this type, to provide noncircular or out-of-round belt disks, in order to attempt to avoid or rule out such oscillations.
DE-A 195 20 508 discloses a rotating belt drive system for an internal combus-tion engine, in which a control belt runs around two driven belt disks coupled to a camshaft of an engine and around a drive belt disk which is coupled to a crankshaft of the engine. In this case, it is proposed to reduce torsional oscilla-tions by means of an out-of-round belt disk which is illustrated as a camshaft belt disk.
Utility model publication DE 203 19 172 discloses a noncircular rotation compo-nent which consists of a rotor having a plurality of teeth arranged on the circum-circle of the rotor, each tooth possessing a crown and a depression being lo-cated between each pair of teeth lying next to one another, and the crowns of the teeth lying on a curved circumference which forms the circumcircle of the rotor. In this case, the circumcircle of the rotor has a noncircular profile with at least two projecting regions which alternate with drawn-back regions. The spac-ing between the centerpoints of the crowns of each pair of teeth lying next to one another and, furthermore, the profile of the depressions between each pair of teeth lying next to one another are essentially identical. The spacing between the centerpoint of each crown and the axis of the rotor on the circumcircle var-ies, in order to achieve said noncircular profile.
Description Field of the invention The invention relates to an out-of-round or noncircular rotation disk for a timing drive and to a method for constructing and designing a rotation disk of this type.
The present invention relates, furthermore, to a computer system for designing a rotation disk of this type.
Background of the invention Synchronous drive systems, such as, for example, systems based on control belts, are in widespread use in motor vehicles and in industrial applications.
In motor vehicles, for example, control belts or control chains are used for driving camshafts which open and close engine inlet and outlet valves. Other devices, too, such as, for example, water and fuel pumps, may likewise be driven by means of a belt of this type or a chain of this type.
Strand oscillations, as they may be referred to, constitute system-specific ef-fects on wrap-around gears of this type. In principle, a tension means, such as, for example, a chain or a belt, used in wrap-around gears may be excited into transverse, longitudinal and torsional oscillations. Such oscillations of the ten-sion means may appreciably disturb the operation of an overall drive system.
Their occurrence leads to noises and increased structural loads on components of the drive system due to dynamic force peaks which shorten the useful life of the overall system. Furthermore, for example, in the event of an impact of the belt strand against adjacent parts which is brought about by transverse oscilla-tions, both these parts and the belt itself, too, may be damaged. Even after a short time, a failure of the overall drive system may therefore occur. Such strand oscillations are excited by a drive torque of the internal combustion en-gine which takes place nonuniformly. In this case, moreover, fluctuations in the belt or chain stresses may arise, which may likewise cause higher wear and a shorter useful life of the belt or chain.
It is known, in drive systems of this type, to provide noncircular or out-of-round belt disks, in order to attempt to avoid or rule out such oscillations.
DE-A 195 20 508 discloses a rotating belt drive system for an internal combus-tion engine, in which a control belt runs around two driven belt disks coupled to a camshaft of an engine and around a drive belt disk which is coupled to a crankshaft of the engine. In this case, it is proposed to reduce torsional oscilla-tions by means of an out-of-round belt disk which is illustrated as a camshaft belt disk.
Utility model publication DE 203 19 172 discloses a noncircular rotation compo-nent which consists of a rotor having a plurality of teeth arranged on the circum-circle of the rotor, each tooth possessing a crown and a depression being lo-cated between each pair of teeth lying next to one another, and the crowns of the teeth lying on a curved circumference which forms the circumcircle of the rotor. In this case, the circumcircle of the rotor has a noncircular profile with at least two projecting regions which alternate with drawn-back regions. The spac-ing between the centerpoints of the crowns of each pair of teeth lying next to one another and, furthermore, the profile of the depressions between each pair of teeth lying next to one another are essentially identical. The spacing between the centerpoint of each crown and the axis of the rotor on the circumcircle var-ies, in order to achieve said noncircular profile.
In this case, although the design of out-of-round disks of positive tension gears is described, the approach described nevertheless contains weaknesses in terms of methodology. Thus, the utility model publication mentioned assumes a basic contour in the form of a polygon. This means that an out-of-round disk provided with teeth has an enveloping line which is approximated by a polygon.
On account of this approach, in the further design of the disk, a chord length is used for chain drives and an arc length for toothed belt drives. Furthermore, a highly deformed tooth contour arises due to the oblique position of the teeth arranged on the disk.
Object of the invention An object of the present invention, then, was to provide, against the background of the prior art mentioned, a rotation disk and a corresponding method for de-signing a rotation disk of this type, in order to eliminate the abovementioned disadvantages.
Summary of the invention Proceeding from the prior art mentioned and from the considerations to be de-rived from this, the present invention provides an out-of-round rotation disk hav-ing the features of patent claim 1, a method for designing a rotation disk of this type, having the features of patent claim 6, a computer program having the fea-tures of patent claim 10 and a computer system having the features of patent claim 13.
According to patent claim 1, a rotation disk rotatable over an angle of rotation about an axis of rotation is provided, the rotation disk having a rotation disk con-tour possessing at least one elevation, a predetermined number of teeth ar-ranged on the rotation disk contour and having a respective centerpoint, the centerpoints of teeth in each case adjacent being at a predetermined spacing, a rotation disk radius which depends functionally on the angle of rotation and on a mean radius and a rotation disk looping curve resulting from this, the mean ra-dius being selected such that a continuous arc length of the rotation disk loop-ing curve is equal to the product of the predetermined spacing of the center-points of adjacent teeth and the nuniber of teeth.
Out-of-round means, within the scope of the present invention, that the radius of the disk is not constant, and this may be accompanied by a nonuniform trans-mission ratio. By means of an out-of-round rotation disk, a timing drive may experience an excitation, that is to say an excitation to oscillation, which results from the disk shape, that is to say the not ideally round shape. As already men-tioned initially, rotation disks which are out-of-round in this way may be used for the absorption of torsional oscillations in timing drive systems. Causes of tor-sional oscillations of this type may be, inter alia, in a combustion process of an engine or in nonuniform drive torques of other assemblies, such as, for exam-ple, pumps. In systems of this type, a correct positioning and profiling of teeth of a corresponding rotation disk assume major importance, so as to avoid unnec-essary loads on a tension means used, such as, for example, a belt or a chain, in contact with the rotation disk or with the wheel. On the other hand, the con-sequence would be a shortened useful life of the tension means.
By a rotation disk according to the invention being used, the oscillation behavior of wrap-around gears designed as nonuniformly transmitting gears can be calmed. Examples of this are found, for example, in the timing and assembly drives used in automobile construction. However, the rotation disks according to the invention can be employed independently of any particular application, for example also in sectors of textile or office machines.
In the rotation disk according to the invention, the length, covered during a rotation, of the rotation disk looping curve arising from the rotation disk contour is equal to the circumference of a round disk which is obtained as a product of the predetermined number of teeth and of the predetermined respective spacing of adjacent teeth, the rotation disk radius dependent on the angle of rotation and on the mean radius being used to calculate the length of the rotation disk looping curve. In this case, a specific mean radius is obtained, which, however, may vary, depending on the functional formulation for the rotation disk radius.
On account of this approach, in the further design of the disk, a chord length is used for chain drives and an arc length for toothed belt drives. Furthermore, a highly deformed tooth contour arises due to the oblique position of the teeth arranged on the disk.
Object of the invention An object of the present invention, then, was to provide, against the background of the prior art mentioned, a rotation disk and a corresponding method for de-signing a rotation disk of this type, in order to eliminate the abovementioned disadvantages.
Summary of the invention Proceeding from the prior art mentioned and from the considerations to be de-rived from this, the present invention provides an out-of-round rotation disk hav-ing the features of patent claim 1, a method for designing a rotation disk of this type, having the features of patent claim 6, a computer program having the fea-tures of patent claim 10 and a computer system having the features of patent claim 13.
According to patent claim 1, a rotation disk rotatable over an angle of rotation about an axis of rotation is provided, the rotation disk having a rotation disk con-tour possessing at least one elevation, a predetermined number of teeth ar-ranged on the rotation disk contour and having a respective centerpoint, the centerpoints of teeth in each case adjacent being at a predetermined spacing, a rotation disk radius which depends functionally on the angle of rotation and on a mean radius and a rotation disk looping curve resulting from this, the mean ra-dius being selected such that a continuous arc length of the rotation disk loop-ing curve is equal to the product of the predetermined spacing of the center-points of adjacent teeth and the nuniber of teeth.
Out-of-round means, within the scope of the present invention, that the radius of the disk is not constant, and this may be accompanied by a nonuniform trans-mission ratio. By means of an out-of-round rotation disk, a timing drive may experience an excitation, that is to say an excitation to oscillation, which results from the disk shape, that is to say the not ideally round shape. As already men-tioned initially, rotation disks which are out-of-round in this way may be used for the absorption of torsional oscillations in timing drive systems. Causes of tor-sional oscillations of this type may be, inter alia, in a combustion process of an engine or in nonuniform drive torques of other assemblies, such as, for exam-ple, pumps. In systems of this type, a correct positioning and profiling of teeth of a corresponding rotation disk assume major importance, so as to avoid unnec-essary loads on a tension means used, such as, for example, a belt or a chain, in contact with the rotation disk or with the wheel. On the other hand, the con-sequence would be a shortened useful life of the tension means.
By a rotation disk according to the invention being used, the oscillation behavior of wrap-around gears designed as nonuniformly transmitting gears can be calmed. Examples of this are found, for example, in the timing and assembly drives used in automobile construction. However, the rotation disks according to the invention can be employed independently of any particular application, for example also in sectors of textile or office machines.
In the rotation disk according to the invention, the length, covered during a rotation, of the rotation disk looping curve arising from the rotation disk contour is equal to the circumference of a round disk which is obtained as a product of the predetermined number of teeth and of the predetermined respective spacing of adjacent teeth, the rotation disk radius dependent on the angle of rotation and on the mean radius being used to calculate the length of the rotation disk looping curve. In this case, a specific mean radius is obtained, which, however, may vary, depending on the functional formulation for the rotation disk radius.
5 What is achieved thereby is that ttie circumference of ttie out-of-round rotation disk exactly corresponds, in the effective plane, to that of a round disk. The ex-act determination of the circumference or of the length, covered during a 360 rotation, of the rotation disk looping curve is important, since a transmission ratio is thereby determined directly, and, to that extent, this is functionally rele-vant. Thus, for example, in a timing drive of a passenger car, the transmission ratio between a crankshaft used and a camshaft correspondingly used must be exactly 2:1.
In a further possible embodiment of the rotation disk according to the invention, the rotation disk radius can be expressed by a harmonic development of the following form:
r(r) = rõKaõ + 8n cos(ntt + yx) in this case rmeaõ being the mean radius, Sr; being an out-of-roundness ampli-tude, n; being the number of elevations of the rotation disk contour, 4z being a phase position and t being a running parameter composed of an interval from 0 to 2rr. As already mentioned, the mean radius is in this case not constant, but variable. The mean radius may vary, for example, as a function of the selected number of elevations n,, also designated below as order, of ttie phase positions ep or else of the out-of-roundness amplitudes Sri. The rotation looping curve as a three-dimensional curve can be given in coordinate form by means of the an-gle-dependent radius as follows:
(x(t), y(t))=(r(t)cos(t), r(t)sin(t)) The mean radius can then be determined in that an arc length, covered during a 360 rotation, of the rotation looping curve given in parameter form (x(t), y(t)) is calculated, to be precise by carrying out an integration of the arc lerigth differen-tial over an interval of 0 to 2r, and the resulting arc length is equated to the product of the predetermined number Z of teeth and the predetermined spacing D of teeth in each case adjacent:
,T
ZDz~ f x'2(t)+ y'(r)dt In this case, therefore, an arc length between two teeth in the form of the rota-tion disk looping curve segment is used instead of the chord length or the spac-ing of two centerpoints of adjacent teeth. This approach is more complicated in terms of methodology, but leads to correct results in the case of increasing out-of-roundnesses. It may be noted, in this context, that, in chain drives, a chord length must be used instead of the arc length, since a polygon effect, as it is known, comes into effect here on account of the rigidity of the individual chain links.
In a further conceivable embodiment of the rotation disk according to the inven-tion, the teeth of the rotation disk are oriented such that their respective center line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rotation disk looping curve. Such an orientation of the teeth may considerably reduce a load, wherever it may occur, on a tension means used. In an orientation of tooth spaces occurring between the teeth over a poly-gon, the profile of the teeth is distorted. Such distortion, in turn, .stresses a ten-sion means used. A residual deformation which nevertheless remains may be remedied, if appropriate, by a position-dependent and therefore radius-deperiderit variation in the tooth profile.
In another embodiment of the rotation disk according to the invention, a looping arc formed by a tension means at least partially looping around the rotation disk always follows the rotation disk looping curve. This means that the looping arc formed by the tension rneans has the greatest possible bearing contact with the rotation disk. This means, furthermore, that the rotation disk looping curve al-ways possesses a nonnegative curvature.
The present invention relates, furthermore, to a method for designing at least one rotation disk rotatable over an angle of rotation about an axis of rotation for a timing drive, the at least one rotation disk having a rotation disk contour pos-sessing at least one elevation, a predetermined number of teeth arranged on the rotation disk contour and having centerpoints, the centerpoints of teeth in each case adjacent being at a predetermined spacing, a rotation disk radius dependent functionally on the angle of rotation and on a mean radius and a rotation disk looping curve resulting from this. In the method, in this case, the mean radius is determined such that a continuous arc length of the rotation disk looping curve is equal to the product of the predetermined spacing of ttie cen-terpoints of adjacent teeth and the predetermined number of teeth.
In a possible embodiment of the method according to the invention, the rotation disk radius is determined by a harmonic development of the following form:
r(t)=rõK,,,,+~gr;cos(rtrt+p) in this case r,,,ean corresponding to the mean radius, Sr, to an out-of-roundness amplitude, n; to the number of elevations, ~% a phase position and t a running parameter composed of an interval from 0 to 2n. The mean radius rn,o~n is in this case variable and is determined separately in each case for a specific formula-tion, that is to say for a specific selection of the number of elevations, that is to say the order, the phase positions or the out-of-roundness amplitudes.
Furthermore, it is conceivable to orient the teeth such that their respective cen-ter line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rotation disk looping curve.
In a further possible embodiment of the rotation disk according to the invention, the rotation disk radius can be expressed by a harmonic development of the following form:
r(r) = rõKaõ + 8n cos(ntt + yx) in this case rmeaõ being the mean radius, Sr; being an out-of-roundness ampli-tude, n; being the number of elevations of the rotation disk contour, 4z being a phase position and t being a running parameter composed of an interval from 0 to 2rr. As already mentioned, the mean radius is in this case not constant, but variable. The mean radius may vary, for example, as a function of the selected number of elevations n,, also designated below as order, of ttie phase positions ep or else of the out-of-roundness amplitudes Sri. The rotation looping curve as a three-dimensional curve can be given in coordinate form by means of the an-gle-dependent radius as follows:
(x(t), y(t))=(r(t)cos(t), r(t)sin(t)) The mean radius can then be determined in that an arc length, covered during a 360 rotation, of the rotation looping curve given in parameter form (x(t), y(t)) is calculated, to be precise by carrying out an integration of the arc lerigth differen-tial over an interval of 0 to 2r, and the resulting arc length is equated to the product of the predetermined number Z of teeth and the predetermined spacing D of teeth in each case adjacent:
,T
ZDz~ f x'2(t)+ y'(r)dt In this case, therefore, an arc length between two teeth in the form of the rota-tion disk looping curve segment is used instead of the chord length or the spac-ing of two centerpoints of adjacent teeth. This approach is more complicated in terms of methodology, but leads to correct results in the case of increasing out-of-roundnesses. It may be noted, in this context, that, in chain drives, a chord length must be used instead of the arc length, since a polygon effect, as it is known, comes into effect here on account of the rigidity of the individual chain links.
In a further conceivable embodiment of the rotation disk according to the inven-tion, the teeth of the rotation disk are oriented such that their respective center line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rotation disk looping curve. Such an orientation of the teeth may considerably reduce a load, wherever it may occur, on a tension means used. In an orientation of tooth spaces occurring between the teeth over a poly-gon, the profile of the teeth is distorted. Such distortion, in turn, .stresses a ten-sion means used. A residual deformation which nevertheless remains may be remedied, if appropriate, by a position-dependent and therefore radius-deperiderit variation in the tooth profile.
In another embodiment of the rotation disk according to the invention, a looping arc formed by a tension means at least partially looping around the rotation disk always follows the rotation disk looping curve. This means that the looping arc formed by the tension rneans has the greatest possible bearing contact with the rotation disk. This means, furthermore, that the rotation disk looping curve al-ways possesses a nonnegative curvature.
The present invention relates, furthermore, to a method for designing at least one rotation disk rotatable over an angle of rotation about an axis of rotation for a timing drive, the at least one rotation disk having a rotation disk contour pos-sessing at least one elevation, a predetermined number of teeth arranged on the rotation disk contour and having centerpoints, the centerpoints of teeth in each case adjacent being at a predetermined spacing, a rotation disk radius dependent functionally on the angle of rotation and on a mean radius and a rotation disk looping curve resulting from this. In the method, in this case, the mean radius is determined such that a continuous arc length of the rotation disk looping curve is equal to the product of the predetermined spacing of ttie cen-terpoints of adjacent teeth and the predetermined number of teeth.
In a possible embodiment of the method according to the invention, the rotation disk radius is determined by a harmonic development of the following form:
r(t)=rõK,,,,+~gr;cos(rtrt+p) in this case r,,,ean corresponding to the mean radius, Sr, to an out-of-roundness amplitude, n; to the number of elevations, ~% a phase position and t a running parameter composed of an interval from 0 to 2n. The mean radius rn,o~n is in this case variable and is determined separately in each case for a specific formula-tion, that is to say for a specific selection of the number of elevations, that is to say the order, the phase positions or the out-of-roundness amplitudes.
Furthermore, it is conceivable to orient the teeth such that their respective cen-ter line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rotation disk looping curve.
Moreover, it is conceivable to select the rotation disk contour in such a way that the rotation disk looping curve resulting from this always possesses a nonnega-tive curvature. What is achieved thereby is that a tension means looping around the rotation disk has the greatest possible bearing contact with the rotation disk.
The present invention relates, furthermore, to a product for carrying out a method according to the invention, the product being a computer program with a program code which, when the computer program is run on a computer, is suitable for carrying out a method according to the invention. The computer program may in this case be stored on a computer-readable medium.
Furthermore, a computer-readable data carrier with a computer program stored on it is provided, comprising a program code which, when the computer pro-gram is run on a computer, is suitable for carrying out a method according to the invention.
Moreover, a computer system with a storage means is proposed, in which a computer program with a program code is stored, which, when the computer program is run on a computer, is suitable for carrying out a method according to the invention.
It will be appreciated that the features mentioned above and those yet to be explained below may be used not only in the combination specified in each case, but also in other combinations or alone, without departing from the scope of the present invention.
Brief description of the drawings The invention is described in detail by means of an exemplary embodiment, with reference to the drawing in which:
The present invention relates, furthermore, to a product for carrying out a method according to the invention, the product being a computer program with a program code which, when the computer program is run on a computer, is suitable for carrying out a method according to the invention. The computer program may in this case be stored on a computer-readable medium.
Furthermore, a computer-readable data carrier with a computer program stored on it is provided, comprising a program code which, when the computer pro-gram is run on a computer, is suitable for carrying out a method according to the invention.
Moreover, a computer system with a storage means is proposed, in which a computer program with a program code is stored, which, when the computer program is run on a computer, is suitable for carrying out a method according to the invention.
It will be appreciated that the features mentioned above and those yet to be explained below may be used not only in the combination specified in each case, but also in other combinations or alone, without departing from the scope of the present invention.
Brief description of the drawings The invention is described in detail by means of an exemplary embodiment, with reference to the drawing in which:
figure 1 shows a diagrammatic illustration of an embodiment of a rotation disk according to the invention.
Detailed description of the drawings Figure 1 shows an out-of-round rotation disk 1. The rotation disk 1 has four ele-vations 2. Furthermore, a predetermined number Z of teeth 4 are arranged on the rotation disk contour 3. In the case illustrated here, 21 teeth are provided on the rotation disk contour 3. In this case, a minimum diameter dmin and a maxi-mum diameter dmax can be determined, and, from these, a diameter difference Ad. In the present case, the diameter difference Ad is predetermined at 5 mm.
The number n of elevations 2 corresponds to the order which therefore amounts to 4 here. By means of these particuiars, then, a rotation disk looping curve can be specified, in a first approximation, as a three-dimensional curve in the form of (x(t), y(t)), as follows:
x(r) = r(t) cos(t) _(r,.~õ +A~/
4 cos(nt)) cos(t) y(t) = r(t) sin(t) _ (n,w.õ + 6 ~/4 cos(nr)) sin(t) a phase position rpr of 0 being assumed. The out-of-roundness amplitude sr is obtained as od/4. Furthermore, a spacing D in each case between two center-points of adjacent teeth, what is known as a division, was predetermined at 9.525 mm.
By integrating the differential of the arc length of the rotation disk looping curve over ari interval of 0 to 271:
2&
x'(t)+y'(t)dr and by equating with the product of the predetermined number Z of teeth and the predetermined division D:
,1 5 ZD= f x7(t) + y'(r)dt , a mean radius is obtained as:
rn, - = 31.6383 this then resulting in the disk contour of:
x(t) = (31.6383 + 1.25cos(4r)) cos(t ) for t E [0.2n[
y(r) _ (31.6383 + 1?5 cos(4t)) sin(t) It can be seen in this case that, depending on the selected or suitable functionaf formulation of the angle-dependent radius, a different mean radius is obtained.
Thus, the mean radius and, coupled to this, the angle-dependent radius are always adapted to the basic system. The rotation disk looping curve occurring in each case is therefore adapted highly flexibly to existing stipulations. The exact determination of the mean radius or the length of the rotation disk looping curve as an image of the out-of-round contour of the rotation disk is highly relevant in functional terms and is in direct relation to a transmission ratio of the rotation disk. Thus, for example, a transmission ratio between a camshaft and a crank-shaft in the timing drive of a passenger car must be exactly 2:1. Only by an ex-act determination of the mean radius or of the rotation disk looping curve can such stipulations be fulfilled.
Furthermore, an orientation of teeth takes place such that the center line of a tooth is perpendicular to the tangent to the rotation disk looping curve. A
slight residual deformation nevertheless possibly remains and could be remedied by a position-dependent and therefore radius-dependent variation in the tooth profile.
Moreover, a tension means, in the overall run of its looping arc, is as far as pos-sible always to lie on the disk. This means that a looping arc formed by a ten-sion means at least partially looping around the rotatiori disk always follows the rotation disk looping curve. This is equivalent to the requirement that the rota-tion disk looping curve is always to possess a nonnegative curvature.
This requirement must always be taken into account in selecting the parameters in the harmonic formulation made.
The present invention, in all aspects, has many applications in devices which require a noncircular rotation disk, and it is used especially in synchronous drive devices. These may be, for example, an internal combustion engine. The inven-tion, however, may also be used in devices other than synchronous drive de-vices. The out-of-round or noncircular shape of the rotation disk may be pro-vided at many different locations in a drive device. The selection of the rotation disk contour depends on other components of a drive device, In this case, a uniform noncircular profile or a nonuniform profile or contour for the rotation disk may arise. In these circumstances, for reasons of performance and useful life, a tension means and the rotation disk must fit with one another as well as possi-ble.
Detailed description of the drawings Figure 1 shows an out-of-round rotation disk 1. The rotation disk 1 has four ele-vations 2. Furthermore, a predetermined number Z of teeth 4 are arranged on the rotation disk contour 3. In the case illustrated here, 21 teeth are provided on the rotation disk contour 3. In this case, a minimum diameter dmin and a maxi-mum diameter dmax can be determined, and, from these, a diameter difference Ad. In the present case, the diameter difference Ad is predetermined at 5 mm.
The number n of elevations 2 corresponds to the order which therefore amounts to 4 here. By means of these particuiars, then, a rotation disk looping curve can be specified, in a first approximation, as a three-dimensional curve in the form of (x(t), y(t)), as follows:
x(r) = r(t) cos(t) _(r,.~õ +A~/
4 cos(nt)) cos(t) y(t) = r(t) sin(t) _ (n,w.õ + 6 ~/4 cos(nr)) sin(t) a phase position rpr of 0 being assumed. The out-of-roundness amplitude sr is obtained as od/4. Furthermore, a spacing D in each case between two center-points of adjacent teeth, what is known as a division, was predetermined at 9.525 mm.
By integrating the differential of the arc length of the rotation disk looping curve over ari interval of 0 to 271:
2&
x'(t)+y'(t)dr and by equating with the product of the predetermined number Z of teeth and the predetermined division D:
,1 5 ZD= f x7(t) + y'(r)dt , a mean radius is obtained as:
rn, - = 31.6383 this then resulting in the disk contour of:
x(t) = (31.6383 + 1.25cos(4r)) cos(t ) for t E [0.2n[
y(r) _ (31.6383 + 1?5 cos(4t)) sin(t) It can be seen in this case that, depending on the selected or suitable functionaf formulation of the angle-dependent radius, a different mean radius is obtained.
Thus, the mean radius and, coupled to this, the angle-dependent radius are always adapted to the basic system. The rotation disk looping curve occurring in each case is therefore adapted highly flexibly to existing stipulations. The exact determination of the mean radius or the length of the rotation disk looping curve as an image of the out-of-round contour of the rotation disk is highly relevant in functional terms and is in direct relation to a transmission ratio of the rotation disk. Thus, for example, a transmission ratio between a camshaft and a crank-shaft in the timing drive of a passenger car must be exactly 2:1. Only by an ex-act determination of the mean radius or of the rotation disk looping curve can such stipulations be fulfilled.
Furthermore, an orientation of teeth takes place such that the center line of a tooth is perpendicular to the tangent to the rotation disk looping curve. A
slight residual deformation nevertheless possibly remains and could be remedied by a position-dependent and therefore radius-dependent variation in the tooth profile.
Moreover, a tension means, in the overall run of its looping arc, is as far as pos-sible always to lie on the disk. This means that a looping arc formed by a ten-sion means at least partially looping around the rotatiori disk always follows the rotation disk looping curve. This is equivalent to the requirement that the rota-tion disk looping curve is always to possess a nonnegative curvature.
This requirement must always be taken into account in selecting the parameters in the harmonic formulation made.
The present invention, in all aspects, has many applications in devices which require a noncircular rotation disk, and it is used especially in synchronous drive devices. These may be, for example, an internal combustion engine. The inven-tion, however, may also be used in devices other than synchronous drive de-vices. The out-of-round or noncircular shape of the rotation disk may be pro-vided at many different locations in a drive device. The selection of the rotation disk contour depends on other components of a drive device, In this case, a uniform noncircular profile or a nonuniform profile or contour for the rotation disk may arise. In these circumstances, for reasons of performance and useful life, a tension means and the rotation disk must fit with one another as well as possi-ble.
Claims (13)
1. A rotation disk rotatable over an angle of rotation about an axis of rota-tion, with a rotation disk contour possessing at least one elevation, with a predetermined number of teeth arranged on the rotation disk contour and having a respective centerpoint, the centerpoints of teeth in each case adjacent being at a predetermined spacing, with a rotation disk radius which depends functionally on the angle of rotation and on a mean ra-dius, and with a rotation disk looping curve resulting from this, the mean radius being selected such that a continuous arc length of the rotation disk looping curve is equal to the product of the predetermined spacing of the centerpoints of adjacent teeth and the number of teeth.
2. The rotation disk as claimed in claim 1, in which the rotation disk radius can be expressed by a harmonic development of the following form:
r(t) = r mean + .SIGMA..DELTA.r i cos(nit + .PHI.), in which:
r mean = mean radius, .DELTA.r i = an out-of-roundness amplitude, n l = number of elevations, .PHI.i = a phase position, and t = a running parameter composed of an interval from 0 to 2.pi..
r(t) = r mean + .SIGMA..DELTA.r i cos(nit + .PHI.), in which:
r mean = mean radius, .DELTA.r i = an out-of-roundness amplitude, n l = number of elevations, .PHI.i = a phase position, and t = a running parameter composed of an interval from 0 to 2.pi..
3. The rotation disk as claimed in either one of claims 1 and 2, in which the teeth are oriented such that their respective center line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rotation disk looping curve.
4. The rotation disk as claimed in one of the preceding claims, in which a looping arc formed by a tension means at least partially looping around the rotation disk always follows the rotation disk looping curve.
5. The rotation disk as claimed in one of the preceding claims, in which the rotation disk looping curve always possesses a nonnegative curvature.
6. A method for designing at least one rotation disk rotatable over an angle of rotation about an axis of rotation for a timing drive, the at least one ro-tation disk having a rotation disk contour possessing at least one eleva-tion, a predetermined number of teeth arranged on the rotation disk con-tour and having centerpoints, the centerpoints of teeth in each case ad-jacent being at a predetermined spacing, a rotation disk radius depend-ent functionally on the angle of rotation and on a mean radius and a rota-tion disk looping curve resulting from this, in which the mean radius is de-termined such that a continuous arc length of the rotation disk looping curve is equal to the product of the predetermined spacing of the center-points of adjacent teeth and the number of teeth.
7. The method as claimed in claim 6, in which the rotation disk radius is de-termined by a harmonic development of the following form:
r(t) = r mean + .SIGMA. .DELTA.r i cos(nit + .PHI.), in which:
r mean = mean radius, .DELTA.r i = an out-of-roundness amplitude, n l = number of elevations, .PHI. = a phase position, and t = a running parameter composed of an interval from 0 to 2.pi..
r(t) = r mean + .SIGMA. .DELTA.r i cos(nit + .PHI.), in which:
r mean = mean radius, .DELTA.r i = an out-of-roundness amplitude, n l = number of elevations, .PHI. = a phase position, and t = a running parameter composed of an interval from 0 to 2.pi..
8. The method as claimed in either one of claims 6 and 7, in which the teeth are oriented such that their respective center line is perpendicular to the tangent, contiguous to the respective centerpoint of the teeth, of the rota-tion disk looping curve.
9. The method as claimed in one of claims 6 to 8, in which the rotation disk contour is selected in such a way that the rotation disk looping curve re-sulting from this always possesses a nonnegative curvature.
10. A product for carrying out the method as claimed in one of claims 6 to 9, the product being a computer program with a program code which, when the computer program is run on a computer, is suitable for carrying out a method as claimed in one of claims 6 to 9.
11. The computer program as claimed in claim 10, which is stored on a com-puter-readable medium.
12. A computer-readable data carrier with a computer program which is stored on it and comprises a program code which, when the computer program is run on a computer, is suitable for carrying out a method as claimed in one of claims 6 to 9.
13. A computer system with a storage means in which a computer program with a program code is stored, which, when the computer program is run on a computer, is suitable for carrying out a method as claimed in one of claims 6 to 9.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004048629.8 | 2004-10-06 | ||
| DE102004048629A DE102004048629A1 (en) | 2004-10-06 | 2004-10-06 | Non-circular rotary disk for a timing drive |
| US11/029,577 | 2005-01-05 | ||
| US11/029,577 US20060073926A1 (en) | 2004-10-06 | 2005-01-05 | Non-circular rotary disk for a timing control drive |
| PCT/EP2005/009764 WO2006037427A1 (en) | 2004-10-06 | 2005-09-10 | Out-of-round rotation disc for a timing drive |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2582737A1 true CA2582737A1 (en) | 2006-04-13 |
Family
ID=35445735
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002582737A Abandoned CA2582737A1 (en) | 2004-10-06 | 2005-09-10 | Out-of-round rotation disc for a timing drive |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1797351B1 (en) |
| KR (1) | KR20070097020A (en) |
| CA (1) | CA2582737A1 (en) |
| WO (1) | WO2006037427A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11729929B2 (en) | 2020-10-15 | 2023-08-15 | Boe Technology Group Co., Ltd. | Mid-frame assembly and display device |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006049987A1 (en) * | 2006-10-24 | 2008-04-30 | Schaeffler Kg | Continuously variable transmission for transmitting torque, involves introducing torque by input shaft and transmission to other shaft, where rotary disk provides non positive connection between force transmitting endless element and shaft |
| US9341243B2 (en) | 2012-03-29 | 2016-05-17 | Litens Automotive Partnership | Tensioner and endless drive arrangement |
| EP3513097B1 (en) | 2016-09-13 | 2022-03-23 | Litens Automotive Partnership | V tensioner and endless drive arrangement |
| KR102333467B1 (en) * | 2019-12-27 | 2021-12-03 | 주식회사 유라코퍼레이션 | Many sides worktabel |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2303453A1 (en) * | 1973-01-25 | 1974-11-21 | Hallden Machine Co | GEAR TRANSMISSION |
| DE10009808A1 (en) * | 2000-03-01 | 2001-09-06 | Schumag Ag | Tube drawbench drive train has off-round wheels at driving and driven ends traveled by endless chain powered by multi-tooth drawing sprocket. |
| EP1227056B1 (en) * | 2001-01-26 | 2003-10-15 | Univ.-Prof. Dipl.-Ing. Dr. techn. Jörg Oser O. | Chain drive with a polygonal chain wheel |
| DE20319172U1 (en) * | 2003-09-18 | 2004-04-22 | Litens Automotive Partnership, Woodbridge | Non-circular rotation component |
-
2005
- 2005-09-10 WO PCT/EP2005/009764 patent/WO2006037427A1/en active IP Right Grant
- 2005-09-10 KR KR1020077007769A patent/KR20070097020A/en not_active Application Discontinuation
- 2005-09-10 CA CA002582737A patent/CA2582737A1/en not_active Abandoned
- 2005-09-10 EP EP05789880A patent/EP1797351B1/en not_active Not-in-force
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11729929B2 (en) | 2020-10-15 | 2023-08-15 | Boe Technology Group Co., Ltd. | Mid-frame assembly and display device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1797351A1 (en) | 2007-06-20 |
| WO2006037427A1 (en) | 2006-04-13 |
| EP1797351B1 (en) | 2008-09-17 |
| KR20070097020A (en) | 2007-10-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5554131B2 (en) | Synchronous drive device having non-circular drive element | |
| US5921879A (en) | Random engagement roller chain sprocket with staged meshing and flank relief to provide improved noise characteristics | |
| JP5205387B2 (en) | Synchronous belt drive system | |
| CA2468973C (en) | Roller chain sprocket with added chordal pitch reduction | |
| US7074147B2 (en) | Roller chain sprocket with symmetric cushion rings | |
| CA2339729C (en) | A roller chain sprocket with cushion rings | |
| CA1306623C (en) | Camshaft damper | |
| US8113975B2 (en) | Chain wheel and timing chain drive for the compensation of dynamic loads | |
| CA2582737A1 (en) | Out-of-round rotation disc for a timing drive | |
| KR101074821B1 (en) | Sprocket with alternating pitch spacings | |
| CN106468340A (en) | Twisting vibration absorption system | |
| EP1812733B1 (en) | Sprocket with 1.5 order, and multiples thereof, vibration canceling profile and synchronous drive employing such a sprocket | |
| CN101036005B (en) | Out-of-round rotation disc for controlling driving mechanism | |
| US8342993B2 (en) | Synchronous drive apparatus | |
| US4998906A (en) | Tooth belt drive, especially for internal combustion engines | |
| US20080176689A1 (en) | Rotating disk with a periodically changing tooth-space geometry | |
| JPH0718349B2 (en) | Winding transmission device for internal combustion engine | |
| US20090253542A1 (en) | Rotary disc | |
| US20090191997A1 (en) | Rotating disc | |
| EP1893888B1 (en) | Drive having a toothed belt for damping torsional vibrations | |
| EP0870131A1 (en) | Roller chain drive system having improved noise characteristics |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |
Effective date: 20130910 |