CN110851922B - Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature - Google Patents
Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature Download PDFInfo
- Publication number
- CN110851922B CN110851922B CN201910832096.0A CN201910832096A CN110851922B CN 110851922 B CN110851922 B CN 110851922B CN 201910832096 A CN201910832096 A CN 201910832096A CN 110851922 B CN110851922 B CN 110851922B
- Authority
- CN
- China
- Prior art keywords
- driving wheel
- gear
- angle
- meshing
- worst
- 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.)
- Active
Links
Images
Landscapes
- Gears, Cams (AREA)
Abstract
The invention discloses a method for determining the worst helical angle of a bevel gear based on the lowest tooth surface flash temperature, which comprises the following steps: inputting basic geometric parameters and operating parameters of a bevel gear; step two, inputting the range [ beta 0, beta m ] of the helix angle of the driving wheel and the calculation step length xb; step three, respectively representing the average contact pressure p and the contact half width aH of the wheel set; step four, expressing the friction heat flow Q1 of the driving wheel; step five, expressing total heat convection thermal resistance Rv of the driving wheel; step six, obtaining the maximum instantaneous temperature of the driving wheel; and step seven, loop iteration. The invention discloses a novel method for determining the worst helical angle of a helical gear, which considers the actual meshing process of the helical gear, is closer to the actual working condition of the helical gear, has more accurate prediction result of the worst helical angle, greatly reduces the steps for determining the worst helical angle, saves the calculation resources and improves the efficiency.
Description
The technical field is as follows:
the invention belongs to the field of gear design and processing, and particularly relates to a method for determining the worst helical angle of a bevel gear based on the lowest tooth surface flash temperature.
Background art:
tooth surface flash temperature is one of the main factors causing tooth surface gluing, and the influence of the helical angle of the bevel gear on the tooth surface flash temperature is large. According to research, the maximum tooth surface instantaneous temperature is increased firstly and then reduced along with the increase of the spiral angle, a maximum value exists, and the spiral angle of the bevel gear when the tooth surface instantaneous temperature is maximum is the worst spiral angle. During the design process of the helical gears, gears with various helical angles are designed, so that after the worst helical angle is determined, a reference value can be provided for the design of the gears (helical gear helical angles with larger angle difference from the worst helical angle can generally better prevent tooth surface gluing), and the design is prevented from being selected to be the worst helical angle. However, the existing worst spiral angle determining method has complicated steps, needs long calculation time and wastes calculation resources.
The invention content is as follows:
the invention aims to provide a method for determining the worst helical angle of a helical gear based on the lowest tooth surface flash temperature, and discloses a novel method for determining the worst helical angle of the helical gear.
In order to solve the problems, the technical scheme of the invention is as follows: .
A method for determining the worst helical angle of a bevel gear based on the lowest tooth surface flash temperature comprises the following steps: inputting basic geometric parameters and operating parameters of a bevel gear; the basic geometrical parameter comprises the number Z of gear teethi(ii) a The gear module m; the tooth width B; the gear reference circle pressure angle alpha; poisson ratio mu of gear materialiAnd modulus of elasticity Ei(ii) a Heat transfer coefficient lambda of gear materialiDensity rhoiAnd specific heat capacity ciThe operation parameters comprise the rotating speed n of the gear; gear input torque T; wherein i is 1,2 is respectively indicated as driving wheel and driven wheel;
step two, inputting the range [ beta ] of the helix angle of the driving wheel0，βm]And calculating the step size xb；β0Represents the minimum helix angle, βmRepresents a maximum helix angle;
step three, average contact pressure p and contact half width a of the gear pairHRespectively expressed as:
wherein F is the tooth flank quasi-static load; l isxThe length of a contact line for a single gear tooth in the meshing of the driving wheel; rECAnd EeqRespectively the comprehensive curvature radius and the equivalent elastic modulus of the driving wheel;
the tangential absolute speeds of the driving wheel and the driven wheel at the meshing position are respectively expressed as:
αc1the pressure angle of the engagement point of the driving wheel is shown; alpha is alphac2A pressure angle representing the driven wheel mesh point; n is1Representing the rotation speed of the driving wheel; n is a radical of an alkyl radical2Representing the driven wheel speed; r1And R2Respectively showing the meshing curvature radius of the driving wheel and the driven wheel;
vs＝|v1-v2|；
step four, friction heat flow Q of driving wheel1Expressed as:
wherein, mucIs the coefficient of friction; gamma is a heat energy conversion coefficient; a isHContact half width; delta is the heat flux density distribution coefficient; p represents a contact stress;
ρ1,λ1,c1respectively representing the density, thermal conductivity and specific heat capacity of the material of the driving wheel; ρ is a unit of a gradient2,λ2,c2Are respectively shownThe density, thermal conductivity and specific heat capacity of the driven wheel material; v. of1And v2Respectively, the tangential absolute velocity of the driving wheel and the driven wheel at the meshing position.
Step five, total heat convection thermal resistance R of the driving wheelvExpressed as:
Rv＝Rv1+Rv2+Rv3
wherein R isv1、Rv2、Rv3Respectively expressed as:
b is the number of discrete spur gears, namely the driving wheel is dispersed into the number of a plurality of spur gear sheets which are stacked along the axis and sequentially rotate by a tiny angle; c is the number of discrete spur gears participating in meshing at a certain time in consideration of a change in the length of the meshing line during meshing,
wherein beta represents the helix angle of the driving wheel;
Ri0,Ri1,Ri2,Ri3,Ri4,Ri5,Rt,Rs,Rmare respectively:
wherein, lambda is the heat conduction coefficient of the driving wheel material; h ist,hs,hmThe convective heat transfer coefficients of the tooth crest face, the end face and the meshing face of the driving wheel are respectively; r is a radical of hydrogena,r,rf,r0Respectively showing the addendum circle radius, the reference circle radius, the dedendum circle radius and the shaft hole radius of the driving wheel; wherein S ist,Ss,SmRespectively showing the tooth crest area, the gear end surface area and the meshing surface area of the driving wheel;
step six, obtaining the maximum instantaneous temperature of the driving wheel:
TF＝Q1·Rv；
step seven, iteration is circulated, and the range of the spiral angle is calculated to be [ beta ]0，βm]And calculating the step size as xbThe maximum helix angle corresponding to the maximum instantaneous temperature is the worst helix angle.
The worst spiral angle of the driven wheel is the same as the steps, and only relevant parameters corresponding to the driving wheel are replaced by the driven wheel.
In a further improvement, beta0＝5°，βm＝20°,xb＝0.5°。
The further improvement is that the device is provided with a plurality of grooves,
wherein R is1Showing the meshing curvature radius of the driving wheel; r is2Representing the driven wheel meshing curvature radius; e1The elastic modulus of the driving wheel is shown; e2Representing the modulus of elasticity of the driven wheel.
In the formula, FnIs the tooth surface normal load; l is a radical of an alcoholzIs the total contact line length at any time;
Lz＝∑Lx
Lxthe length of the contact line of a single pair of gear teeth.
In a further improvement, γ is 0.95.
The invention has the following advantages:
the invention has the advantages that:
1. the instantaneous temperature distribution of the tooth surface of the bevel gear is calculated by using a thermal network method, and compared with a Blok flash temperature formula, the method considers the actual meshing process of the bevel gear and is closer to the actual working condition of the bevel gear.
2. The method can obtain the instantaneous temperature distribution of the tooth surface of the bevel gear, and can also obtain the change rule of the instantaneous temperature of the tooth surface along with the change of the helix angle, so that the worst helix angle based on the lowest tooth surface flash temperature is obtained.
Description of the drawings:
FIG. 1 is a schematic flow chart of the present invention.
The specific implementation mode is as follows:
in order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. Reference will now be made in detail to the embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present application and should not be construed as limiting the present application.
Example 1
As shown in fig. 1, in the present invention, it is assumed that, in an ideal state,
(1) it is assumed that the body temperature is the same at each location of each discrete spur gear.
(2) The contact area of the helical gear pair is assumed to be a rectangular area having a contact half width and a tooth width. Firstly, the instantaneous temperature distribution of the tooth surface of the helical gear is predicted by establishing a thermal network model. In the process of establishing a thermal network model, a helical gear is considered as a plurality of spur gear lamellae stacked along an axis and sequentially rotated by a slight angle. The friction heat flow of the bevel gear in the meshing process is analyzed, and the parameters are known as follows: (a) basic geometric parameter, set ZiIs the number of gear teeth; m is a gearModulus; b is the tooth width; alpha is a gear reference circle pressure angle; mu.siAnd EiRespectively the Poisson's ratio and the elastic modulus of the gear material; lambdai、ρi、ciExpressed as the heat transfer coefficient, density and specific heat capacity of the gear material, respectively, (where i ═ 1, and 2 are expressed as the primary and secondary wheels, respectively). (b) Basic operating parameters: n represents the rotational speed of the gear; t represents gear input torque.
Based on the hertz's contact theory, the contact stress and contact half-width of a gear pair can be expressed as:
wherein F is a tooth surface quasi-static load; l iszIs the length of the contact line in the helical gear engagement; rECAnd EeqThe comprehensive curvature radius and the equivalent elastic modulus of the helical gear are obtained;
the combined radius of curvature and equivalent elastic modulus can be expressed as:
the tooth flank quasi-static load can be expressed as:
in the formula, FnNormal load of tooth surface; l is a radical of an alcoholzIs the total contact line length at any instant.
The total contact line length can be expressed as:
Lz＝∑Lx
Lxthe length of the contact line of a single pair of gear teeth. The length of the contact line of a single pair of gear teeth and the total length of the contact lines of multiple pairs of gear teeth are time-varying during the entire meshing process of the helical gears. The idea of solving the variable contact line length of the bevel gear tooth surface is as follows: the length change rule of the first contact line from the engagement process to the engagement process is firstly obtained, then the time-varying lengths of other contact lines are obtained according to the engagement periodicity, and the specific calculation steps refer to reference document 2.
The relative sliding speed at any meshing point can be expressed as:
vs＝|v1-v2|
v1and v2The tangential absolute speeds of the driving wheel and the driven wheel at the meshing position can be respectively expressed as:
in the formula, alphac1The pressure angle of the engagement point of the driving wheel is shown; alpha is alphac2A pressure angle representing the driven wheel mesh point; n is1Representing the rotation speed of the driving wheel; n is2Representing the driven wheel speed; r is1And R2Respectively showing the engaged curvature radius of the driving wheel and the driven wheel.
The friction heat flow of the driving wheel can be expressed as:
in the formula, mucIs the coefficient of friction; gamma is a heat energy conversion coefficient, 0.95; a isHContact half width; δ is the heat flow density distribution coefficient, which can be expressed as:
total heat convection resistance RvCan be expressed as:
Rv＝Rv1+Rv2+Rv3
wherein R isv1、Rv2、Rv3Can be respectively expressed as:
where b is the number of discrete spur gears, the helical gears are discrete into a plurality of spur gear slices stacked along the axis and sequentially rotated by a slight angle. C is the number of discrete spur gears participating in meshing at a certain time in consideration of a change in the length of the meshing line during meshing,
wherein beta represents the gear helix angle
Ri0,Ri1,Ri2,Ri3,Ri4,Ri5,Rt,Rs,RmAre respectively:
wherein λ is the heat conduction coefficient of the gear material; h ist,hs,hmThe convection heat transfer coefficients of the addendum face, the end face and the meshing face of the bevel gear are respectively shown in reference 1; r isa,r,rf,r0Respectively represents the gear tooth top circle radius, the pitch circle radius, the tooth root circle radius and the axle hole radius. Wherein S ist,Ss, SmRespectively showing the tooth crest area, the gear end surface area and the meshing surface area. As shown in fig. 1.
Tooth crest area StCan be expressed as:
b represents the tooth width, saThe tooth thickness representing the tip circle can be expressed as:
invαa＝tanαa-αa；invα＝tanα-α
in the formula, raThe radius of the addendum circle of the gear; r is the pitch circle radius of the gear; alpha is alphaaAnd alpha is respectively the addendum circle pressure angle and the reference circle pressure angle.
The involute equation is known from reference 2 and can be expressed as:
reference is made to reference 2 for basic parameters in the formula
Based on the involute equation, the area of the meshing surface SmCan be expressed as:
the end face area can be expressed as:
in the formula saThe addendum circle thickness; r isa，rbRespectively the gear tooth top circle radius and the base circle radius.
Under the effect of friction heat source and the forced convection cooling of lubricating oil, heat balance can be reached after a certain period of time in the gear meshing process, before heat balance is reached, the internal energy change of the ith discrete straight gear is equal to net flow, and the relation between net flow and temperature increase can be expressed as follows:
in the formula, ci,piRespectively representing the specific heat capacity and the density of the gear material; viRepresenting the volume of the temperature cell.
To simplify the calculation, the time is discretized into:
τk+1＝τk+Δτk
therefore, the temperature variation of the ith discrete spur gear can be expressed by time as:
according to the principle of energy conservation, the expression of the instantaneous temperature of the helical gear can be described as follows:
after thermal equilibrium is reached, the steady state temperature of the helical gear no longer changes over time, and as the moving heat source changes periodically, the instantaneous temperature changes periodically along the meshing line. Thus, the maximum instantaneous temperature of the helical gear can be expressed as:
TF＝Q1·Rv
in the formula, Q1Is the frictional heat flow; rvTotal thermal convective resistance;
the instantaneous temperature of the tooth surface of the helical gear can be obtained by a heat network method, and the helix angle is used as an independent variable, and the instantaneous temperature of the tooth surface is a function of the helix angle of the helical gear. Setting the independent variable interval as [5,20], calculating the step length as 0.5, calculating the maximum instantaneous temperature corresponding to different helix angle values in the interval, comparing the maximum instantaneous temperature corresponding to each helix angle by taking the lowest tooth surface instantaneous temperature rise as a principle, calculating the helix angle corresponding to the highest maximum instantaneous temperature in the interval, and defining the helix angle as the 'worst helix angle' and the calculation process as shown in figure 1.
Reference documents:
1. analysis of influence of high-speed helical gear design parameters on tooth surface temperature (journal paper: Shantou university newspaper)
2. Numerical calculation of herringbone gear adhesion wear under quasi-static and dynamic loads (academic paper: university of Hunan)
The above-mentioned embodiment is only a specific embodiment of the present invention, and is not intended to limit the present invention, and any simple modification and replacement thereof are within the scope of the present invention.
Claims (4)
1. A method for determining the worst helical angle of a bevel gear based on the lowest tooth surface flash temperature is characterized by comprising the following steps: inputting basic geometric parameters and operating parameters of a bevel gear; the basic geometrical parameter comprises the number Z of gear teethi(ii) a The gear module m; the tooth width B; the gear reference circle pressure angle alpha; poisson ratio mu of gear materialiAnd modulus of elasticity Ei(ii) a Heat transfer coefficient lambda of gear materialiDensity rhoiAnd specific heat capacity ciThe operation parameters comprise the rotating speed n of the gear; gear input torque T; wherein i is 1,2 is respectively expressed as a driving wheel and a driven wheel;
step two, inputting the range [ beta ] of the helix angle of the driving wheel0，βm]And calculating the step size xb；β0Denotes the minimum helix angle, βmRepresents a maximum helix angle;
step three, average contact pressure p and contact half width a of the gear pairHRespectively expressed as:
wherein F is the tooth flank quasi-static load; l isxThe length of a contact line of a single gear tooth in the meshing of the driving wheel; rECAnd EeqRespectively is the comprehensive curvature radius and the equivalent elastic modulus of the driving wheel;
the tangential absolute speeds of the driving wheel and the driven wheel at the meshing position are respectively expressed as:
αc1 represents the pressure angle of the engagement point of the driving wheel; alpha is alphac2 denotes the pressure angle of the driven wheel mesh point; n1 represents the driving wheel speed; n2 represents the driven wheel speed; r is1And R2Respectively showing the meshing curvature radius of the driving wheel and the driven wheel;
vs＝|v1-v2|·
step four, friction heat flow Q of driving wheel1Expressed as:
wherein, mucIs the coefficient of friction; gamma is a heat energy conversion coefficient; a isHContact half width; delta is the heat flow density distribution coefficient; p represents a contact stress;
ρ1,λ1,c1respectively showing the density, thermal conductivity and specific heat capacity of the material of the driving wheel; ρ is a unit of a gradient2,λ2,c2Respectively representing the density, the thermal conductivity and the specific heat capacity of a driven wheel material; v1 and v2 respectively represent the tangential absolute speeds of the driving wheel and the driven wheel at the meshing position;
step five, total heat convection thermal resistance R of the driving wheelvExpressed as:
Rv＝Rv1+Rv2+Rv3
wherein R isv1、Rv2、Rv3Respectively expressed as:
b is the number of discrete spur gears, namely the driving wheel is dispersed into the number of a plurality of spur gear sheets which are stacked along the axis and sequentially rotate by a tiny angle; c is the number of discrete spur gears participating in meshing at a certain moment in time taking into account the change in length of the meshing line during meshing,
wherein β represents a helix angle of the drive wheel;
Ri0,Ri1,Ri2,Ri3,Ri4,Ri5,Rt,Rs,Rmare respectively:
wherein, lambda is the heat conduction coefficient of the driving wheel material; h ist,hs,hmRespectively being the tooth crest, end surface and meshing surface of the driving wheelConvective heat transfer coefficient of (a); r isa,r,rf,r0Respectively showing the addendum circle radius, the reference circle radius, the dedendum circle radius and the shaft hole radius of the driving wheel; wherein S ist,Ss,SmRespectively showing the tooth crest area, the gear end surface area and the meshing surface area of the driving wheel;
step six, obtaining the maximum instantaneous temperature of the driving wheel:
TF＝Q1·Rv；
step seven, loop iteration is carried out, and the range of the spiral angle is solved to be [ beta ]0，βm]And calculating the step size as xbThe helix angle corresponding to the maximum instantaneous temperature is the worst helix angle.
2. The method for determining the worst pitch angle of a helical gear based on the lowest tooth flank flashover temperature of claim 1, wherein β is0＝5°，βm＝20°,xb＝0.5°。
3. The method for determining the worst spiral angle of a helical gear based on the lowest tooth flank flashover temperature according to claim 1,
wherein R is1Representing the meshing curvature radius of the driving wheel; r is2Representing the driven wheel meshing curvature radius; e1The elastic modulus of the driving wheel is shown; e2Representing the modulus of elasticity of the driven wheel;
in the formula, FnNormal load of tooth surface; l iszIs the total contact line length at any time;
Lz＝∑Lx
Lxthe length of the contact line of a single pair of gear teeth.
4. The method for determining the worst spiral angle of the helical gear based on the lowest tooth flank flashover temperature as claimed in claim 1, wherein γ is 0.95.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910832096.0A CN110851922B (en) | 2019-09-04 | 2019-09-04 | Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910832096.0A CN110851922B (en) | 2019-09-04 | 2019-09-04 | Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110851922A CN110851922A (en) | 2020-02-28 |
| CN110851922B true CN110851922B (en) | 2022-07-19 |
Family
ID=69594866
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910832096.0A Active CN110851922B (en) | 2019-09-04 | 2019-09-04 | Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110851922B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113722888B (en) * | 2021-08-02 | 2023-04-04 | 北京工业大学 | Single-side meshed cylindrical gear pair meshing line temperature field calculation method based on thermal network |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5108275A (en) * | 1990-12-17 | 1992-04-28 | Sager William F | Rotary pump having helical gear teeth with a small angle of wrap |
| CN106649971A (en) * | 2016-10-25 | 2017-05-10 | 北京航空航天大学 | Evaluation method for spiral bevel gear long-life transmission fatigue reliability based on grinding and heat treatment |
| CN106777459A (en) * | 2016-11-10 | 2017-05-31 | 北京交通大学 | The computational methods in generator shaft radial rotor temperature field |
| CN109187009A (en) * | 2018-09-29 | 2019-01-11 | 济南大学 | A kind of calculation method of herringbone bear flank of tooth heat distortion amount |
-
2019
- 2019-09-04 CN CN201910832096.0A patent/CN110851922B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5108275A (en) * | 1990-12-17 | 1992-04-28 | Sager William F | Rotary pump having helical gear teeth with a small angle of wrap |
| CN106649971A (en) * | 2016-10-25 | 2017-05-10 | 北京航空航天大学 | Evaluation method for spiral bevel gear long-life transmission fatigue reliability based on grinding and heat treatment |
| CN106777459A (en) * | 2016-11-10 | 2017-05-31 | 北京交通大学 | The computational methods in generator shaft radial rotor temperature field |
| CN109187009A (en) * | 2018-09-29 | 2019-01-11 | 济南大学 | A kind of calculation method of herringbone bear flank of tooth heat distortion amount |
Non-Patent Citations (2)
| Title |
|---|
| Parametric studies of lubrication performance of a helical gear pair with non-Newtonian fluids;Liu M 等;《Journal of Mechanical Science and Technology》;20160113;第317-326页 * |
| 基于轮齿载荷分析的斜齿轮最优螺旋角确定方法;唐毅 等;《机械传动》;20101231;第34卷(第12期);第6-9页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110851922A (en) | 2020-02-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110738348B (en) | Prediction method based on thermal network model straight gear temperature field | |
| Mao | A numerical method for polymer composite gear flash temperature prediction | |
| Li et al. | Thermal analysis of helical gear transmission system considering machining and installation error | |
| CN110851922B (en) | Method for determining worst helical angle of bevel gear based on lowest tooth surface flash temperature | |
| CN111767615B (en) | Gear parameter optimization method based on low friction heat loss | |
| CN111059255B (en) | Calculation method for tooth surface abrasion of double-arc harmonic reducer | |
| CN111062103B (en) | Metallurgical crane reducer gear life assessment method for optimizing parameters | |
| Kujawski et al. | Analysis of generation capabilities of noncircular cogbelt pulleys on the example of a gear with an elliptical pitch line | |
| Dong et al. | A semi-analytical method of time-varying mesh stiffness in concentric face gear split-torque transmission system | |
| Pedrero et al. | Calculation of tooth bending strength and surface durability of high transverse contact ratio spur and helical gear drives | |
| CN109271688B (en) | Accurate calculation method for high-speed gear meshing transmission temperature field | |
| Chernets | A method for predicting contact strength and life of Archimedes and involute worm gears, considering the effect of wear and teeth correction | |
| Yin et al. | Thermal elastohydrodynamic lubrication characteristics of double involute gears at the graded position of tooth waist | |
| CN110929350B (en) | Friction heat flow prediction method considering tooth surface abrasion | |
| CN113051682B (en) | Method and device for calculating thermal elastic meshing stiffness of helical gear pair | |
| Ren et al. | Lubrication mechanisms of rubbing interface in internal meshing teeth with small clearance | |
| Delgado et al. | The effectiveness of shrouding on reducing meshed spur gear power loss-test results | |
| Mallesh et al. | Effect of tooth profile modification in asymmetric spur gear tooth bending stress by finite element analysis | |
| CN109372972B (en) | Method for calculating slip friction factor of instantaneous meshing point of tooth surface of herringbone gear | |
| Lin et al. | An optimum design algorithm for gear systems incorporating surface temperature | |
| CN113722888B (en) | Single-side meshed cylindrical gear pair meshing line temperature field calculation method based on thermal network | |
| CN203413092U (en) | Reducer wear-resistant worm wheel provided with oil storage tank | |
| Chen et al. | Contact stress of modified curvilinear gears | |
| Hlebanja et al. | Contribution to the development of cylindrical gears | |
| CN204175916U (en) | A kind of helical gear transverse tooth thickness adjusting apparatus |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |