CN201461897U - Arc spiral cylindrical gear and arc rack - Google Patents
Arc spiral cylindrical gear and arc rack Download PDFInfo
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- CN201461897U CN201461897U CN2009200887147U CN200920088714U CN201461897U CN 201461897 U CN201461897 U CN 201461897U CN 2009200887147 U CN2009200887147 U CN 2009200887147U CN 200920088714 U CN200920088714 U CN 200920088714U CN 201461897 U CN201461897 U CN 201461897U
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Abstract
The utility model discloses an arc spiral cylindrical gear. A contour line (14) and a contour line (13) of a midpoint section of a gear tooth length on a convex tooth surface (1) and a concave tooth surface (2) are spur gear involute tooth-shaped; a section far away from the middle point is helical gear involute tooth-shaped; and the spur gear involute tooth shape is screwed in contour involutes (5, 6, 7 and 8) along a convex surface tooth top arc line (9) and a convex surface tooth root arc line (11) on the convex tooth surface (1) and a concave surface tooth root arc line (11) and a concave surface tooth top arc line (12) on the concave tooth surface (2) from the middle point to the two ends, so that a two-way arc spiral gear tooth is formed by a two-way spiral toothed line with a right-hand arc-shaped helical gear at one end thereof and a left-hand arc-shaped helical gear at the other end. The camber helical toothing track between the gear and a rack reference circle is rigorous and precise, and the top arc of the concave tooth surface is identical to the root arc of the convex tooth surface and is larger than the top arc of the convex tooth surface and the root arc of the concave tooth surface, so that the complete contact surface is formed, and a novel meshing theory is created.
Description
Technical field
The utility model relates to a kind of driving gear, especially a kind of arc spiral tooth trace cylindrical gears and extend the arc rack that theoretical introduction goes out.Same principle, two kinds of original papers intermesh, and its motion mode is changed mutually.
Background technique
Gear transmission is most widely used a kind of type of belt drive, cylindrical gears " tooth trace " has three kinds of forms at present: spur gear (spur wheel), helical gear (spiral gear), the 4th kind of form of herringbone gear (herringbone gear) is " arc tooth cylindrical gear " rarely known by the people, is " bent tooth trace mesh form " research topic of being delivered by the U.S. in 1975.It is involute profile in facewidth central authorities cross section that sample is put on display in international new technology exhibition in 1986, leaves central authorities and becomes approximative value, and " tooth trace " surface of contact part does not produce load, and three precision and ideal form are not inconsistent.So domestic name of patent application that has occurred many these problems from nineteen ninety so far: " cylinder arc gear ", " arc cylindrical gear ", " curved tooth face cylindrical gears ", " arch arc cylindrical gears ", " involute one circular tooth gear " " bidirectional circular-arc gear " or the like, pass through retrieving information, the research back finds that this gear meshing theory also lacks systematic Study, kinematic accuracy, transmission stability, contact precision, and various design parameter shortage is proved foundation.Up to now, all can not obtain excellent popularization uses.Especially " arc rack " do not have both at home and abroad.
Summary of the invention
The purpose of this utility model is to have captured the international research problem---created new principle definition, and proved every design parameter, the check formula, the universal standard, reckoner, the highi degree of accuracy high strength arc helix cylindrical gear and the arc rack that produce the ideal form stable drive, volume are little, in light weight, moment of torsion is big, the life-span is long.
Technological scheme of the present invention is: a kind of arc helix cylindrical gear, the gear teeth are by convex side, the recessed flank of tooth, tooth flank and Topland are formed, the long profile line of Mean section on the convex side and the recessed flank of tooth of gear teeth tooth is the involute profile of spur wheel, the cross section of leaving mid point becomes the helical gear involute profile, this spur wheel involute profile by mid point respectively to two ends along the convex surface tooth top camber line on the convex side, concave surface tooth root camber line on the convex surface tooth root camber line and the recessed flank of tooth, concave surface tooth top camber line spiral is to the profile involute position of oblique gear teeth both ends of the surface, form an end dextrorotation arc helical teeth, the two-way arc helical gear teeth that the bidirectional screw tooth trace of the left-handed arc helical teeth of the other end constitutes, the helixangle of this two-way arc helical gear teeth is a variable, it is gear teeth two ends teeth directional arc tangent line and axial angle, and it is by the long Mean section profile line of gear teeth tooth, zero degree rises to arc helical gear teeth two ends and becomes big gradually.
The involute radius of curvature of two-way arc helical gear teeth is a variable, i.e. end face helical gear involute radius of curvature r
2＞mid point spur wheel involute radius of curvature r
1r
2The involute radius of curvature change the big more r of β with helixangle
2Big more, when supposing that helixangle changes to 90 °, the radius of curvature r of helical gear end face involute
2To twist extension linearly, i.e. r
2=∞.
Two-way arc helical gear teeth is a variable along the transverse tooth thickness c and the wide d of roller seating space of tooth trace normal direction, by the face width of tooth L mid point K of two-way arc helical gear teeth to two ends convergent, R
1, R
2Be two-way arc helical gear teeth tooth trace arc radius of curvature, the shape of tooth flank and Topland is not wait bent crescent moon, tooth trace arc radius of curvature relation: convex surface tooth top arc R=concave surface tooth root arc R＜convex side gear teeth tooth trace arc R
1=recessed flank of tooth gear teeth tooth trace arc R
2＜convex surface tooth root arc R=concave surface tooth top arc R; When the pressure angle α that supposes two-way arc helical gear teeth is zero degree, each tooth trace arc radius of curvature variation relation formula of the gear teeth: R (9)=R (10)=R (11)=R (12)=R
1=R
2Cause L
1With L
2Overlapping, it is identical that wheel Topland, tooth flank and standard pitch circle launch the cross section, bent crescent shape such as is.
Two-way arc helical gear teeth arbitrary end cross section all presents the involute profile of rule, and tooth depth equates everywhere; Should satisfy following three conditions (): the transverse pressure angle α of two-way arc helical tooth
EndBe variable, α
End＞α
Method, transverse pressure angle α
EndChange and change in company with helixangle, helixangle is big more, contrate tooth profile pressure angle α
EndBig more; (2): if pressure angle α is a zero degree, α
EndDo not change, at this moment contrate tooth profile pressure angle α in company with helixangle
EndBe constantly equal to zero degree; (3): two-way arc helical gear teeth is along the Normal pressure angle α of teeth directional
MethodDo not change in company with helixangle.
The standard pitch circle transverse pitch of two-way arc helical gear teeth equals the mid point tooth pitch, i.e. the wide d of the wide b=mid point of transverse tooth thickness a=end face roller seating space transverse tooth thickness c=mid point roller seating space, and the helical teeth transverse module is constantly equal to mid point spur wheel modulus.
A kind of arc rack, teeth are made up of convex side, the recessed flank of tooth, tooth flank, Topland, can mesh with the arc helix cylindrical gear, when above-mentioned arc helix cylindrical gear standard pitch circle launches, have just formed arc rack during the diameter infinity; At this moment, the despiralization on the arc helix cylindrical gear, involute is linearly; Convex-concave tooth trace on Topland on the arc rack and the tooth flank prolongs mutually, and the cross surface shape presents crescent shape.
The relation that the tooth trace arc radius of curvature of each teeth should satisfy: convex surface tooth top camber line radius of curvature R (9-1)=concave surface tooth root camber line radius of curvature R (11-1)＜convex surface tooth root camber line radius of curvature R (10-1)=concave surface tooth top camber line radius of curvature R (12-1).
The tooth trace of described teeth is in bent crescent shape such as the reticule cross section are.
Advantage of the present utility model:
1, bent arc helical toothing track such as this gear and tooth bar standard pitch circle is tightly accurate, and recessed flank of tooth top arc equals convex side root arc, greater than convex side top arc and recessed flank of tooth root arc, has formed 100% surface of contact, has created new mesh theory.Gear arbitrary end cross section all presents the involute profile of rule.Make wheel set can both produce load in the arbitrfary point on the overlap coefficient inner toothed surface of engaging-in and disengaging, area of contact is higher than any gear and the tooth bar of the face width of tooth on year-on-year basis.So are higher than existing gear rack in its bearing capacity and working life.
2, three precision of this gear and tooth bar are higher than similar other products.Face width of tooth mid point is a spur wheel, leaves mid point and becomes helical gear, and helix angle is a variable, prolongs crescent moon arc helix to two ends and becomes gradually greatly, and normal module is a variable, and normal module is prolonged crescent moon arc helix to two ends and diminished gradually.Normal tooth thickness and roller seating space are wide to be variable, by face width of tooth mid point to the two ends convergent.Involute curvature is a variable, and is gradually big to two ends by face width of tooth mid point.Be wrapped on the cylindrical body just as three-dimensional crescent moon, formed the arc helix, the crooked long mid point tooth of tooth is the thickest, it is the peak of full-depth tooth intensity, no matter just change counter-rotating, producing the spiral continuity in the engaging-in process and taken over, keeping stable drive, and (axiom: kinematic accuracy and noise cause owing to back lash and involute error, have a strong impact on the high speed transmission because the tight accurately no gap of movement locus and noise free.The intensity of gear and life-span are except that material, and be all relevant with three precision with shape, and shape is relevant with manufacturing technology with three precision, and manufacturing technology is carried out according to mesh theory.) over more than 30 year, this mesh theory ideal form imperfection is in use because bent flank of tooth physical form is firm and than herringbone gear intensity height, but three precision bound by theory do not have the demonstration foundation of 100% surface of contact, though can use, but do not pass a test at a high speed, low speed is undesirable, the manufacture cost height.Contained the popularization and application of this tooth kind.The present invention has finished the manufacturing of this ideal form on theory and practice, make wheel set in the process of engaging-in and disengaging, and the arbitrfary point in the overlap coefficient on institute's geared surface can both produce load, and force bearing point is evenly distributed.
3, because transverse module is constantly equal to mid point spur wheel modulus, can realize height and angle correcting, widen centre distance and modulus and selected degrees of freedom, for popularization and application provides design and inspection parameter foundation.
4, because teeth directional is an arc tooth line, can prolong a tooth trace angle of rotation (± 2.5 °) so do not influence transmission. wheel set installation parallelism error adaptability is strong, can suffer from one's own actions best contact position, be implemented in 0 °～5 ° with internal burden free axis friendship transmission. that is to say, be not afraid of initiatively and between the driven frame runout takes place. for example: heavily loaded turning round equipment, drive chassis and the partial installation of cylindrical shell follower, operational vibration is very big to straight-tooth or helical gear influence in working life. if adopt the present invention to address the above problem. can cause the design new breakthrough in the gear application area, such as: up and down, about, before and after 0 °～5 ° with interior swing driving mechanism, or be applied in 0 °～5 ° and hand over transmission with interior axle.
5, tooth-shape structure of the present invention is similar to herringbone gear, and no axial force has solved the manufacturing difficult problem of miniature no clearance groov herringbone gear.Alternative herringbone gear has been filled up the blank of miniature no clearance groov herringbone gear in the application in some field.Manufacture cost is lower than herringbone gear, is equivalent to helical gear.Big gear can form automatic production in batches, and cost is equivalent to spur gear.
6, the no clearance groov herringbone tooth bar of the arc rack image curvature among the present invention, no axial force has been filled up the blank of no clearance groov herringbone tooth bar.
7, the present invention is applied on the various speed reducers, under the identical prerequisite of moment of torsion overall volume is dwindled on year-on-year basis, has played the chain effect of energy-conservation joint time material, is that the transmission body ownership is made link and alleviated weight and reduced cost.If heavily loaded bull gear adopts effect of the present invention then more remarkable, can make the gear ring of moment of torsion on year-on-year basis alleviate at double weight, save a large amount of alloy steel products.
It can make the various huge mechanical transmission mechanism reduced volumes and the effect of integrated package invention play the same tune on different musical instruments, and can transmit great moment of torsion in limited space, does not crack a joke.Resist the moment enormous impact power that unexpected stall or counter-rotating cause, than the big several times of herringbone gear of the identical face width of tooth.The clearance groov of herringbone gear disconnects angle steel disjunctor in the most strong tooth, has lost mutual support force, has taken useful space, and Here it is, and why the present invention can make one of argument of mechanical transmission reduced volume.
8, application area of the present invention is boundless, is applied in various industry fields, is the Updated product of straight-tooth, helical teeth, herringbone gear.Because spur gear, helical gear, herringbone gear, stress form is just as straight plate, and arc helix cylindrical gear stress form resembles " Zhao state arch bridge ", and surface of contact is that the arch full-depth tooth is stressed, so can replace hard flank of tooth reduction gear (because helical gear is the spiral points contact, the force bearing point pressure of local overlap coefficient is very big, just adopts hardened face gear).The hardened face gear manufacture cost is very high.
9 because of this strength of gear teeth very high, expanded the gear material scope, nylon aluminum alloy etc. can be made the gear of very light in weight, this gear can be realized mill teeth, roll flute, squeeze tooth, plover tooth process, making the highi degree of accuracy high strength gear that volume is little, in light weight, moment of torsion is big, the life-span is long, is the best driving gears of Aero-Space.Will be if the submarine military project adopts advanced in the world.
10, identify that through mechanical transmission state key test room of University Of Chongqing comparative trial load high speed machine efficiency curve is higher than other gear, temperature rise curve is lower than other gear.(the high-speed overload temperature is very low)
Description of drawings
Fig. 1 is an arc helix cylindrical gear monodentate stereogram;
Fig. 2 is the end face plan view of Fig. 1;
Fig. 3 is that the A-A standard pitch circle of Fig. 2 launches sectional drawing;
Fig. 4 is the arc rack stereogram;
Fig. 5 is the formula definition figure that proves Fig. 1 and Fig. 3;
Fig. 6 is the inference proof diagram;
Fig. 7 such as is at bent crescent moon tooth trace figure.
Embodiment
The present invention is directed to the deficiencies in the prior art, having captured engagement ideal form technology closes, created " arc helix cylindrical gear principle and manufacturing " Systems Theory, various parameter foundations have been proved, cutter standard that R among the figure and L and m ratio relation the applicant have been referred to as " Wanyan Xueming's standard " standard, supporting IWS International Workman Standard has been invented " arc helix cylindrical gear and arc rack " and various gear making machine, has expanded application area.
The arc helix cylindrical gear main structure gear teeth of the present invention are as shown in Figure 1: be made up of convex side 1, the recessed flank of tooth 2, tooth root 3, tooth top 4.The Mean section profile line 13,14 of the long L of tooth is the involute profile of spur wheel, the cross section of leaving mid point becomes the helical gear involute profile, the involute profile of spur wheel is respectively to profile involute 5,6,7,8 positions of two ends along the extremely oblique gear teeth both ends of the surface of 11,12 spirals of the concave surface camber line on the convex surface camber line on the convex side 19,10 and the recessed flank of tooth 2, form an end dextrorotation arc helical teeth, the bidirectional screw tooth that the bidirectional screw tooth trace of the left-handed arc helical teeth of the other end constitutes.The helixangle of this two-way arc helical gear teeth is a variable, and it is two ends teeth directional arc tangent line and axial angle, and it is risen to arc helical gear teeth two ends by long Mean section profile line 13,14 zero degrees of gear teeth tooth and becomes big gradually.The radius of curvature of two ends arc helical teeth 5,6,7,8 involutes is greater than the radius of curvature of long mid point 13, the 14 spur wheel involutes of tooth, r in (as Fig. 2)
2＞r
1, the involute curvature of two-way arc helical gear teeth is variable, r
2The involute radius of curvature change the big more r of β with helixangle
2Big more, when supposing that helixangle changes to 90 °, the radius of curvature r of involute
2To twist extension linearly, i.e. r
2=∞.Standard pitch circle launches section (Fig. 3), and the shape size of tooth and roller seating space is identical, i.e. the wide d of the wide b=mid point of transverse tooth thickness a=end face roller seating space transverse tooth thickness c=mid point roller seating space, R
1=R
2R
nA, b are that L both ends of the surface transverse tooth thickness and roller seating space are wide, and c, d are that L mid point transverse tooth thickness and roller seating space are wide, respectively to two ends along two-way arc helical gear teeth tooth trace arc radius of curvature R convergent, the wide disappearance of two ends transverse tooth thickness and roller seating space is zero when L/R=2.The wheel set meshing condition: standard pitch circle launches musical form R such as section
1=R
2R
n(Fig. 1) radius of curvature of camber line 9,10,11,12 and R value correlation (Fig. 3): R10=R12＞R＞R9=R11.Two-way arc helical tooth arbitrary end cuts the involute profile that section all presents rule, and tooth depth equates everywhere.The long L mid point of tooth spur wheel modulus is constantly equal to the transverse module of two ends arc helical teeth.Two-way arc helical gear teeth is a variable along the transverse tooth thickness c and the wide d of roller seating space of tooth trace normal direction, by the face width of tooth L mid point K of two-way arc helical gear teeth to two ends convergent, R
1, R
2Be two-way arc helical gear teeth tooth trace arc radius of curvature, tooth flank 3 is not wait bent crescent moon with the shape of Topland 4, tooth trace arc radius of curvature relation: convex surface tooth top arc R9=concave surface tooth root arc R11＜convex side gear teeth tooth trace arc R
1=recessed flank of tooth gear teeth tooth trace arc R
2＜convex surface tooth root arc R10=concave surface tooth top arc R12; When the pressure angle α that supposes two-way arc helical gear teeth was zero degree, tooth flank 3 and Topland 4 shapes such as were at bent crescent moon (as Fig. 6), each tooth trace arc radius of curvature variation relation formula: R9=R10=R11=R12=R of the gear teeth
1=R
2Cause L
1With L
2Overlapping, the wheel Topland. tooth flank such as is at bent crescent shape, and launch bent crescent moon such as A-A section with standard pitch circle identical.Face width of tooth L is through the preferred intercepting of practice " crescent moon " intermediate section, " claiming the crescent moon tooth trace ".When launching the gear diameter infinity, standard pitch circle just forms Fig. 3 .5.6---and present the tooth bar shape, Fig. 5 Fig. 6 proves the definition of the separate equations in claims, and Fig. 5 proves following various: the a=b=c=d introduction goes out transverse module m=mid point modulus m.Deng musical form R
1=R
2Rn.Relation at all radius of curvature of Fig. 1 Fig. 3: R9=R11＜R
1=R
2＜R10=R12 is because the teeth directional cross section that the pressure angle α of profile of tooth forms is trapezoidal.The tooth root arc intersects with the radius of curvature convex-concave of tooth top arc and equates, area of lune equal and opposite in direction, and area is less than the bent crescent moon such as grade of Fig. 5 A-A section.Demonstration: suppose that pressure angle α is a zero degree, the teeth directional cross section is rectangular, formation Fig. 6, and convex globoidal prolongs and is exterior circular column, and concave arc surface prolongs and is inner cylinder.Each radius of curvature relation: convex surface tooth top camber line radius of curvature R 9=convex surface tooth root camber line radius of curvature R 10=concave surface tooth root camber line radius of curvature R 11=concave surface tooth top camber line radius of curvature R 12=convex side camber line radius of curvature R
1=recessed flank of tooth camber line radius of curvature R
2Cause L
1With L
2Overlapping, bent crescent moons such as tooth root tooth top crescent moon and A-A section are identical, definition: each radial cross section equal diameters of cylindrical body, label 11,12, R among Fig. 6
1Be the inner cylinder radius, label 9,10, R
2It is the exterior circular column radius.
Just because of pressure angle α relation, the teeth directional cross section is trapezoidal, the convex-concave cambered surface is prolonged be cone, the outer vertebra point of convex side upwards, the vertebra point downwards in the recessed flank of tooth, two toothed rack mesh form form 100% surface of contact by vertebra in entering as outer vertebra. therefore form Fig. 5 convex surface tooth top camber line 9, convex surface tooth root camber line 10, concave surface tooth root camber line 11, the radius of curvature of concave surface tooth top camber line 12 and standard pitch circle launch the correlation of cross section R1: convex surface tooth root arc R10=concave surface tooth top arc R12＞R1＞convex surface tooth top arc R9=concave surface tooth root arc R11. definition: each radial cross section diameter of cone does not wait, the big end section diameter of centrum＞vertebra point diameter of section.
As shown in Figure 7: by the moon cusp chord length formula prove out L
1Less than diameter, convex surface arc R
2Grow up in semicircle concave surface arc R
1Long less than semicircle, the positive negative value of the difference of arc length equates.L
1＝AB＜2R。Month cusp chord length fixed pattern:
(m is a modulus in the formula).c＝00’R1＝R2
Two-way arc helical gear teeth arbitrary end cross section all presents the involute profile of rule, and tooth depth equates everywhere; Should satisfy following three conditions (): the transverse pressure angle α of two-way arc helical tooth
EndBe variable, α
End＞α
Method, transverse pressure angle α
EndChange and change in company with helixangle, helixangle is big more, contrate tooth profile pressure angle α
EndBig more; (2): if pressure angle α is a zero degree, α
EndDo not change, at this moment contrate tooth profile pressure angle α in company with helixangle
EndBe constantly equal to zero degree; (3): two-way arc helical gear teeth is along the Normal pressure angle α of teeth directional
MethodDo not change in company with helixangle.
Arc rack is the secondary tooth bar of joining with the engagement of arc helix cylindrical gear.(as Fig. 4) teeth are made up of convex side 1-1, recessed flank of tooth 2-1, tooth root 3-1, tooth top 4-1.Involute linearly.Standard pitch circle expansion section is this tooth bar reticule section shape in above-mentioned (Fig. 3).The shape size of tooth and roller seating space is identical, alternately.Deng musical form: R
1=R
2=R
3R
n, etc. form a=b=c=d.C, d are that tooth long L mid point transverse tooth thickness and roller seating space are wide, respectively to two ends along R
1, R
2Convergent, two ends transverse tooth thickness and roller seating space are wide when L/R=2 is condensed to zero.
Rack and pinion meshing condition: the radius of curvature of Fig. 4 mean camber line 9-1,12-1,11-1,10-1 and R value correlation (Fig. 3): R12-1=R10-1＞R＞R9-1=R11-1.The helical teeth transverse module is constantly equal to mid point spur wheel modulus.
Arc helix cylindrical gear characteristics:
1, because the helical teeth transverse module is constantly equal to mid point spur gear modulus, can realize height and angle correcting, widen centre-to-centre spacing and modulus and selected the free degree. Spoke is installed depth of parallelism strong adaptability, can hand over transmission with the internal burden free axis at 0 degree-5 degree along tooth trace, be not afraid of in other words initiatively and between the driven pulley frame runout takes place. For example: heavily loaded apparatus for rotating drive chassis and the partial installation of cylindrical shell driven pulley, operational vibration is very big to straight-tooth or helical gear impact in service life. As adopt the present invention just can address the above problem.
2, shape checking: the engagement of two toothed rack is buckled togather, and flank of tooth contact rate 100% meshes entirely. Introduction: when arc helix cylindrical gear diameter is infinitely great, become arc rack. No matter the forward counter-rotating can both contact by 100% flank of tooth this gear with tooth bar. The arbitrary end cross section all presents the involute profile of rule. Make wheel set can both produce load in the arbitrfary point on the overlap coefficient inner toothed surface of engaging-in and disengaging, contact area is higher than on year-on-year basis any gear and the tooth bar of the face width of tooth.
3, crooked flank of tooth mid point tooth is the thickest is full-depth tooth changqiang degree peak, produce the spiral continuity in the engaging-in process in two ends and taken over the maintenance stable drive, and the noiselessness owing to the tight accurately gapless of movement locus, structure of the present invention can make the flank of tooth at engaging-in and detach procedure, arbitrfary point on the contact ratio inner toothed surface can both touch generation load, and stress point is evenly distributed. (the high-speed overload occurrence temperature is very low).
The present invention and prior art Data Comparison such as following table:
The utility model and the contrast of existing tooth trace:
The difference of prior art disclosed uniform thickness curved tooth line gear and present patent application crescent moon tooth trace gear: uniform thickness tooth male and female face tooth trace prolongs non-intersect, must be in the form of a ring. And the male and female face tooth trace of present patent application crescent moon tooth trace prolongs and to intersect at two ends, at the reference circle bent crescent moon (shown in Fig. 3 .5.6.7) such as launch that the section tooth trace is. Such two gear Nie close, the recessed flank of tooth of gear is stressed, another gear is that convex side is stressed, and concave surface tooth top arc 12 Nie are fashionable must to be contacted with convex surface tooth root arc 10, and in like manner convex surface tooth top arc 9 contacts with concave surface tooth root arc 11, it is to wait song that reference circle launches the cross section, only have radius of curvature to equate, contact just can fit together perfectly, again because the curved tooth face is helical arc, therefore the flank of tooth everywhere can both contact in rolling process, guarantees flank of tooth contact 100%; Than the big decades of times of herringbone bear contact area. The undercut of herringbone bear disconnects the most strong part of herringbone disjunctor angle steel, has namely weakened intensity, has occupied again the space, and the present invention that Here it is is the argument of machine driving energy reduced volume.
Claims (8)
1. arc helix cylindrical gear, the gear teeth are by convex side (1), the recessed flank of tooth (2), tooth flank (3) and Topland (4) are formed, it is characterized in that: the profile line (14) of Mean section on the convex side (1) and the recessed flank of tooth (2) that gear teeth tooth is long, (13) be the involute profile of spur wheel, the cross section of leaving mid point becomes the helical gear involute profile, this spur wheel involute profile by mid point respectively to two ends along the convex surface tooth top camber line (9) on the convex side (1), concave surface tooth root camber line (11) on the convex surface tooth root camber line (10) and the recessed flank of tooth (2), concave surface tooth top camber line (12) spiral is to the profile involute (5) of oblique gear teeth both ends of the surface, (6) reach (7), (8) position, form an end dextrorotation arc helical teeth, the two-way arc helical gear teeth that the bidirectional screw tooth trace of the left-handed arc helical teeth of the other end constitutes, the helixangle of this two-way arc helical gear teeth is a variable, it is gear teeth two ends teeth directional arc tangent line and axial angle, and it is by the long Mean section profile line (13) of gear teeth tooth, (14) zero degree rises to arc helical gear teeth two ends and becomes big gradually.
2. arc helix cylindrical gear according to claim 1 is characterized in that: the involute radius of curvature of two-way arc helical gear teeth is a variable, i.e. end face helical gear involute radius of curvature r
2＞mid point spur wheel involute radius of curvature r
1r
2The involute radius of curvature change the big more r of β with helixangle
2Big more, when supposing that helixangle changes to 90 °, the radius of curvature r of helical gear end face involute
2To twist extension linearly, i.e. r
2=∞.
3. arc helix cylindrical gear according to claim 2 is characterized in that: two-way arc helical gear teeth is a variable along the transverse tooth thickness c and the wide d of roller seating space of tooth trace normal direction, by the face width of tooth L mid point K of two-way arc helical gear teeth to two ends convergent, R
1, R
2Be two-way arc helical gear teeth tooth trace arc radius of curvature, tooth flank (3) is not wait bent crescent moon with the shape of Topland (4), tooth trace arc radius of curvature relation: convex surface tooth top arc R (9)=concave surface tooth root arc R (11)＜convex side gear teeth tooth trace arc R
1=recessed flank of tooth gear teeth tooth trace arc R
2＜convex surface tooth root arc R (10)=concave surface tooth top arc R (12); When the pressure angle α that supposes two-way arc helical gear teeth is zero degree, each tooth trace arc radius of curvature variation relation formula of the gear teeth: R (9)=R (10)=R (11)=R (12)=R
1=R
2Cause L
1With L
2Overlapping, it is identical that wheel Topland, tooth flank and standard pitch circle launch the cross section, bent crescent shape such as is.
4. according to claim 1 or 2 or 3 described arc helix cylindrical gears, it is characterized in that: two-way arc helical gear teeth arbitrary end cross section all presents the involute profile of rule, and tooth depth equates everywhere; Should satisfy following three conditions (): the transverse pressure angle α end of two-way arc helical tooth is a variable, α end＞α method, and transverse pressure angle α end changes and changes in company with helixangle, and helixangle is big more, and contrate tooth profile pressure angle α end is big more; (2): if pressure angle α is a zero degree, the α end does not change in company with helixangle, and at this moment contrate tooth profile pressure angle α end is constantly equal to zero degree; (3): two-way arc helical gear teeth does not change in company with helixangle along the Normal pressure angle α method of teeth directional.
5. arc helix cylindrical gear according to claim 4, it is characterized in that: the standard pitch circle transverse pitch of two-way arc helical gear teeth equals the mid point tooth pitch, be the wide d of the wide b=mid point of transverse tooth thickness a=end face roller seating space transverse tooth thickness c=mid point roller seating space, the helical teeth transverse module is constantly equal to mid point spur wheel modulus.
6. arc rack, teeth are made up of convex side (1-1), the recessed flank of tooth (2-1), tooth flank (3-1), Topland (4-1), can mesh with the described arc helix cylindrical gear of claim 1, it is characterized in that:, just formed arc rack during the diameter infinity when above-mentioned arc helix cylindrical gear standard pitch circle launches; At this moment, the despiralization on the arc helix cylindrical gear, involute is linearly; Convex-concave tooth trace on Topland on the arc rack (4-1) and the tooth flank (3-1) prolongs mutually, and the cross surface shape presents crescent shape.
7. arc rack according to claim 6 is characterized in that: the relation that the tooth trace arc radius of curvature of each teeth should satisfy: convex surface tooth top camber line radius of curvature R (9-1)=concave surface tooth root camber line radius of curvature R (11-1)＜convex surface tooth root camber line radius of curvature R (10-1)=concave surface tooth top camber line radius of curvature R (12-1).
8. according to claim 7 a described arc rack, it is characterized in that: the tooth trace of described teeth is in bent crescent shape such as the reticule cross section are.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200887147U CN201461897U (en) | 2009-02-27 | 2009-02-27 | Arc spiral cylindrical gear and arc rack |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2009200887147U CN201461897U (en) | 2009-02-27 | 2009-02-27 | Arc spiral cylindrical gear and arc rack |
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| CN201461897U true CN201461897U (en) | 2010-05-12 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678829A (en) * | 2012-05-28 | 2012-09-19 | 阜新德尔汽车部件股份有限公司 | Spiral gear with circular tooth profile and for hydraulic device |
| CN101818802B (en) * | 2009-02-27 | 2012-10-31 | 完颜学明 | Arc spiral cylindrical gear and arc rack |
| CN103671821A (en) * | 2013-11-12 | 2014-03-26 | 林菁 | Full-tooth-width line-contact helical bevel gear tooth structure |
| CN104819266A (en) * | 2015-05-12 | 2015-08-05 | 西安工业大学 | Arc spiral line mixed herringbone gear without tool withdrawal groove and processing method thereof |
| CN107642592A (en) * | 2016-07-20 | 2018-01-30 | 瑟提马麦肯尼加有限公司 | The herringbone gear with variable helical angle and encapsulation flank profil for mekydro device |
-
2009
- 2009-02-27 CN CN2009200887147U patent/CN201461897U/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101818802B (en) * | 2009-02-27 | 2012-10-31 | 完颜学明 | Arc spiral cylindrical gear and arc rack |
| CN102678829A (en) * | 2012-05-28 | 2012-09-19 | 阜新德尔汽车部件股份有限公司 | Spiral gear with circular tooth profile and for hydraulic device |
| CN102678829B (en) * | 2012-05-28 | 2014-08-20 | 阜新德尔汽车部件股份有限公司 | Spiral gear with circular tooth profile and for hydraulic device |
| CN103671821A (en) * | 2013-11-12 | 2014-03-26 | 林菁 | Full-tooth-width line-contact helical bevel gear tooth structure |
| CN104819266A (en) * | 2015-05-12 | 2015-08-05 | 西安工业大学 | Arc spiral line mixed herringbone gear without tool withdrawal groove and processing method thereof |
| CN107642592A (en) * | 2016-07-20 | 2018-01-30 | 瑟提马麦肯尼加有限公司 | The herringbone gear with variable helical angle and encapsulation flank profil for mekydro device |
| CN107642592B (en) * | 2016-07-20 | 2023-11-07 | 瑟提马麦肯尼加有限公司 | Double helical gear with variable helix angle and non-encapsulated tooth profile for hydraulic gear device |
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