CN108133110A - A kind of dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field - Google Patents
A kind of dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field Download PDFInfo
- Publication number
- CN108133110A CN108133110A CN201711464808.5A CN201711464808A CN108133110A CN 108133110 A CN108133110 A CN 108133110A CN 201711464808 A CN201711464808 A CN 201711464808A CN 108133110 A CN108133110 A CN 108133110A
- Authority
- CN
- China
- Prior art keywords
- value
- unit
- lubrication
- bearing
- calculated
- 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.)
- Granted
Links
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Lubricants (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention discloses a kind of dry measuring methods for cutting gear hobbing process intermediate slide portion group temperature field, include the following steps：1) heat source strength during gear hobbing is calculated, including calculating the cutting heat generated between hobboing cutter and workpiece by friction and metal plastic deformation, spindle motor heat production, bearing heating；2) thermal boundary condition is calculated, including determining qualitative temperature, the convection transfer rate on hobboing cutter surface being calculated according to qualitative temperature；3) according to the heat source strength and the result of calculation of thermal boundary condition during gear hobbing, knife rest portion group temperature field can be calculated using finite element emulation software.The invention using air cross grazing single-tube when convection transfer rate computational methods, the dry forced-convection heat transfer coefficient cut during gear hobbing between hobboing cutter and compressed air is calculated, can accurately calculate and dry cut gear hobbing process intermediate slide portion group temperature field.Structure optimization of heat error compensation, knife rest portion group for gear-hobbing machine etc. provides required theoretical foundation.
Description
Technical field
The present invention relates to a kind of measuring methods in temperature field, and gear hobbing process intermediate slide portion group temperature is cut more particularly to one kind is dry
Spend the measuring method of field.
Background technology
Dry to cut in chain digital control gear hobbing machine process, people often ignore the heated situation of knife rest portion group, first, because knife rest
The temperature field of portion's group is difficult to calculate, and comes even if calculating, error is also larger；Second is that the calorific value for being mistakenly considered knife rest portion group is low, no
It influences to use, therefore often result in knife rest portion group and deform, influences precision.
Therefore those skilled in the art are dedicated to developing a kind of high dry of accuracy and cut gear hobbing process intermediate slide portion group temperature
The measuring method of field.
Invention content
In view of the drawbacks described above of the prior art, it is high that the technical problems to be solved by the invention are to provide a kind of accuracy
The dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field.
To achieve the above object, the present invention provides a kind of dry measuring and calculating sides for cutting gear hobbing process intermediate slide portion group temperature field
Method includes the following steps：
1) heat source strength during gear hobbing is calculated：
A1. the cutting heat generated between hobboing cutter and workpiece by friction and metal plastic deformation is calculated：
Q1=Fv1
Q1＇=k1Q1
Wherein Q1To cut thermal power, unit W；
F is main cutting force, herein value be gear hobbing tangential force, unit N；
v1For cutting speed, unit m/s；
D be hobboing cutter outer diameter, unit m；
N be the hobboing cutter speed of mainshaft, unit r/min；
Q1＇ is under actual condition, is input to the cutting heat of knife rest, unit W；
k1For cutting heat heat transfer ratio, value is 1%~10%；
B1. spindle motor heat production is calculated:
Q2＇=k2Q2
Wherein, Q2For spindle motor heat production, unit W；
N is power input to machine, unit W；
MtFor motor output torque, unit Nm；
Z is motor speed, unit r/min；
η is electric efficiency；
D be hobboing cutter outer diameter, unit m；
FtFor gear hobbing tangential force, unit N；
Q2＇ is input to the cutting heat of knife rest, unit W for motor；
k2For motor heat production heat transfer ratio, value is 8%~12%；
C1. bearing heating is calculated：
Q3=1.047 × 10-4Mn
M=M0+M1
In formula, Q3For bearing heating amount, unit W；
N be the hobboing cutter speed of mainshaft, unit r/min；
Total frictional force squares of the M for bearing, unit Nmm；
M0For the torque related with bearing type, rotating speed and lubricating oil property, unit Nmm；
M1For with bearing suffered by the related moment of friction of load, unit Nmm；
Wherein：
M1=f1P1Dm
Wherein, DmFor bearing average diameter, unit mm；
foFor the coefficient related with bearing type and lubricating system；
Q be bearing rotating speed, unit r/min；
P be the kinematic viscosity of lubricant at the working temperature, unit mm2/s；
f1For with bearing type and related coefficient loaded；
P1To determine the calculated load of bearing frictional torque, unit N；
f1And P1Value determine that method is as follows：
1. single-row radial ball bearing f10.0009 (P of value0/C0)0.55, P1Value 3Fa-0.1Fr；
2. double-row spherical ball bearing f10.0003 (P of value0/C0)0.4, P1Value 1.4YFa-0.1Fr；
3. single-row angular contact ball bearing f10.0013 (P of value0/C0)0.33, P1Value Fa-0.1Fr；
4. double-row angular contact bal bearing f10.001 (P of value0/C0)0.33, P1Value 1.4Fa-0.1Fr；
5. band retainer radial short cylindrical roller bearing f1Value 0.00025~0.0003, P1Value Fr；
6. double row self aligning spherical roller bearing f1Value 0.0004~0.0005, P1Value 1.2YFa；
7. taper roll bearing f1Value 0.0004~0.0005, P1Value 2YFa；
8. spherical roller thrust bearing f1Value 0.0005~0.0006, P1Value Fa(Frmax≤0.55Fa)；
Wherein, P0For bearing Equivalent static load, unit N；
C0For bearing rated static load, unit N；
FaFor axial force suffered by bearing, unit N；
FrFor bearing force in radial, unit N；
Y is works as Fa/FrAxial load factor during ＞ e；
Wherein, if P1＜ Fr, then P is taken1=Fr；
P0Obtaining value method it is as follows；
Wherein X0For radial direction static load coefficient；
Y0Axial static load coefficient；
2) thermal boundary condition is calculated：
A2. qualitative temperature is determined：
Wherein, t is qualitative temperature, twFor surface of solids temperature, t∞For fluid temperature (F.T.)；
B2. the convection transfer rate on hobboing cutter surface is calculated according to qualitative temperature
Nu=CRe bPr 1/3
Wherein, convection transfer rates of the α between main shaft surface and air, unit are W/ (m2℃)；
NuFor nusselt number；
λ is air conduction coefficient, and unit is W/ (mk)；
L is characterized length, is taken as hobboing cutter outer diameter, unit m herein；
Re is Reynolds number；
Pr is Prandtl number；
ρ is atmospheric density, unit kg/m3；
v2For air velocity, unit m/s；
d1For equivalent diameter, hobboing cutter outer diameter, unit m are taken herein；
G is air force viscosity, and unit is kg/ (ms) or Pas；
C, b is constant, and obtaining value method is as follows：When Re is 0.4~4, C values 0.989, b values 0.330, Re are 4~40
When, C values 0.911, b values 0.385, when Re is 40~4000, C values 0.683, b values 0.466, Re are 4000~40000
When, C values 0.193, b values 0.618, when Re is 40000~400000, C values 0.0266, b values 0.805；
3) according to the heat source strength and the result of calculation of thermal boundary condition during gear hobbing, it is using finite element emulation software
Knife rest portion group temperature field can be calculated.
Preferably, knife rest portion group use lubricating grease when, p be the kinematic viscosity of lubricating grease at the working temperature, value
For base oil viscosity, unit mm2/s。
Preferably, foValue determine that method is as follows：
1. single-row radial ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, vertical shaft oil
Bath lubrication or oil jet lubrication take 3~4；
2. double-row spherical ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, stand
Axis bath lubrication or oil jet lubrication take 3~4；
3. single-row angular contact ball bearing fog lubrication takes 1, horizontal axis bath lubrication or grease lubrication take 2, vertical shaft bath lubrication or
Oil jet lubrication takes 4；
4. double-row angular contact bal bearing fog lubrication takes 2, horizontal axis bath lubrication or grease lubrication take 4, vertical shaft bath lubrication or
Oil jet lubrication takes 8；
5. band retainer radial short cylindrical roller bearing fog lubrication takes 1~1.5, horizontal axis bath lubrication or grease lubrication take 2
~3, vertical shaft bath lubrication or oil jet lubrication take 4~6；
6. double row self aligning spherical roller bearing fog lubrication takes 2~3, horizontal axis bath lubrication or grease lubrication take 4~6, vertical shaft
Bath lubrication or oil jet lubrication take 8~12；
7. taper roll bearing fog lubrication takes 1.5~2, horizontal axis bath lubrication or grease lubrication take 3~4, vertical shaft oil bath profit
Sliding or oil jet lubrication takes 6~8；
8. thrust ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, vertical shaft oil bath profit
Sliding or oil jet lubrication takes 3~4.
Preferably, X0And Y0Obtaining value method it is as follows：In the case of single-row, parallel combinations, when contact angle is 15 °, X0Value
For 0.5, Y0Value is 0.46, when contact angle is 18 °, X0Value is 0.5, Y0Value is 0.42, when contact angle is 25 °, X0Value
For 0.5, Y0Value is 0.38, when contact angle is 30 °, X0Value is 0.5, Y0Value is 0.33, when contact angle is 40 °, X0Value
For 0.5, Y0Value is 0.26；In the case of back-to-back combination, face-to-face combination, when contact angle is 15 °, X0Value is 1, Y0It takes
It is 0.92 to be worth, when contact angle is 18 °, X0Value is 1, Y0Value is 0.84, when contact angle is 25 °, X0Value is 1, Y0Value is
0.76, when contact angle is 30 °, X0Value is 1, Y0Value is 0.66, when contact angle is 40 °, X0Value is 1, Y0Value is
0.52。
The beneficial effects of the invention are as follows：The invention using air cross grazing single-tube when convection transfer rate calculate
Method calculates the dry forced-convection heat transfer coefficient cut during gear hobbing between hobboing cutter and compressed air, can accurately calculate
It is dry to cut gear hobbing process intermediate slide portion group temperature field.Structure optimization of heat error compensation, knife rest portion group for gear-hobbing machine etc. provides institute
The theoretical foundation needed.
Description of the drawings
Fig. 1 is the temperature field results of measuring structure diagram of the embodiment of the invention.
Specific embodiment
The invention will be further described with reference to the accompanying drawings and examples：
By taking certain numerical control dry cutting gear-hobbing machine knife rest portion group as an example, machined parameters are as shown in table 1：
Certain the numerical control dry cutting gear-hobbing machine knife rest portion group parameter list of table 1
According to 1 parameter of table, calculated according to the method for the present invention as follows：
1) heat source strength during gear hobbing is calculated：
A1. the cutting heat generated between hobboing cutter and workpiece by friction and metal plastic deformation is calculated：
Q1=Fv1
Q1＇=k1Q1
Wherein Q1To cut thermal power, unit W；
F is main cutting force, herein value be gear hobbing tangential force, unit N；
v1For cutting speed, unit m/s；
D be hobboing cutter outer diameter, unit m；
N be the hobboing cutter speed of mainshaft, unit r/min；
Q1＇ is under actual condition, is input to the cutting heat of knife rest, unit W；
k1For cutting heat heat transfer ratio, value is 1%~10%, value 5% in the present embodiment；
Q1＇=k1Q1=5% × 1498.1=74.905W
B1. spindle motor heat production is calculated:
Q2＇=k2Q2
Wherein, Q2For spindle motor heat production, unit W；
N is power input to machine, unit W；
MtFor motor output torque, unit Nm；
Z is motor speed, unit r/min；
η is electric efficiency；
D be hobboing cutter outer diameter, unit m；
FtFor gear hobbing tangential force, unit N；
Q2＇ is input to the cutting heat of knife rest, unit W for motor；
k2For motor heat production heat transfer ratio, value is 8%~12%；Value 10% in the present embodiment；
With reference to the technological parameter in the present embodiment, calculate as follows：
Q2＇=k2Q2=10% × 0.264KW=26.4W
C1. bearing heating is calculated：
Q3=1.047 × 10-4Mn
M=M0+M1
In formula, Q3For bearing heating amount, unit W；
N be the hobboing cutter speed of mainshaft, unit r/min；
Total frictional force squares of the M for bearing, unit Nmm；
M0For the torque related with bearing type, rotating speed and lubricating oil property, unit Nmm；
M1For with bearing suffered by the related moment of friction of load, unit Nmm；
Wherein：
M0The fluid dynamic loss of lubricant is reflected, can be calculated as follows：
M1The frictional dissipation of bearing elastic hysteresis and local differential sliding is reflected, can be calculated as follows：
M1=f1P1Dm
Wherein, DmFor bearing average diameter (dminFor internal diameter, DmaxFor outer diameter), unit mm；
foFor the coefficient related with bearing type and lubricating system；
Q be bearing rotating speed, unit r/min；
P be the kinematic viscosity of lubricant at the working temperature, unit mm2/s；
f1For with bearing type and related coefficient loaded；
P1To determine the calculated load of bearing frictional torque, unit N；
Wherein, foObtaining value method such as table 2：
2 f of tableoValue table
Wherein, f1And P1Value determine method such as table 3：
3 f of table1And P1Exploitation formula table
| Bearing type | f1 | P1 |
| Single-row radial ball bearing | 0.0009(P0/C0)0.55 | 3Fa-0.1Fr |
| Double-row spherical ball bearing | 0.0003(P0/C0)0.4 | 1.4YFa-0.1Fr |
| Single-row angular contact ball bearing | 0.0013(P0/C0)0.33 | Fa-0.1Fr |
| Double-row angular contact bal bearing | 0.001(P0/C0)0.33 | 1.4Fa-0.1Fr |
| Band retainer radial short cylindrical roller bearing | 0.00025~0.0003 | Fr |
| Double row self aligning spherical roller bearing | 0.0004~0.0005 | 1.2YFa |
| Taper roll bearing | 0.0004~0.0005 | 2YFa |
| Spherical roller thrust bearing | 0.0005~0.0006 | Fa(Frmax≤0.55Fa) |
In table 3, P0For bearing Equivalent static load, unit N；
C0For bearing rated static load, unit N；
FaFor axial force suffered by bearing, unit N；
FrFor bearing force in radial, unit N；
Y is works as Fa/FrAxial load factor during ＞ e；
Wherein, if P1＜ Fr, then P is taken1=Fr；
In table 3, bearing Equivalent static load P0It is a kind of imaginary load, i.e., under bearing static position, is bearing maximum load
Contact portion between the rolling element and raceway of lotus, this imaginary load generate Max.contact stress and real load under the conditions of produce
Raw Max.contact stress size is identical.
For radial bearing, Equivalent static load P0It can be calculated by following formula, and the maximum value of result of calculation is taken to be used as and is most terminated
Fruit.P0Obtaining value method it is as follows；
Wherein X0For radial direction static load coefficient；
Y0Axial static load coefficient；
X0And Y0Value such as table 4：
4 static load coefficient X of table0And Y0Value table
In the present embodiment, blade holder part selects 9 single-row angular contact ball bearings altogether, wherein 4 are mounted on bracket, 4
Mounted on tool spindle front end, 1 is mounted on tool spindle tail end, selected bearing designation and parameter such as table 5：
5 bearing designation of table and parameter list
According to above-mentioned parameter and computational methods, the heating power result of calculation of each bearing group of the present embodiment intermediate slide portion group is such as
Table 6：
The heating power of 6 each bearing group of the present embodiment intermediate slide portion group of table
| Bearing group position | Calorific value (W) |
| Bracket | 24 |
| Tool spindle front end | 52.92 |
| Tool spindle tail end | 7.76 |
2) thermal boundary condition is calculated：
A2. qualitative temperature is determined：
Wherein, t is qualitative temperature, twFor surface of solids temperature, t∞For fluid temperature (F.T.)；
It it is 33 DEG C, air velocity v2=3.335m/s, pressure P=0.4MPa through calculating qualitative temperature t in the present embodiment.
B2. thermal boundary condition only considers the cross-ventilation coefficient of heat transfer.The heat convection on knife rest portion group surface, which is divided into, to force pair
Stream heat exchange and two class of heat transfer free convection.Wherein, knife rest outer surface and the heat convection of other stationary parts and air are nature
Heat convection, rule of thumb, NATURAL CONVECTION COEFFICIENT OF HEAT are taken as 10W/ (m2℃).And during gear hobbing, tool spindle is with certain
Rotating speed rotates, and compressed air skips over hobboing cutter surface with constant speed, this is similar with the situation of air cross grazing single-tube, this convection current
Heat exchange is referred to as forced-convection heat transfer.According to the convection transfer rate computational methods of air cross grazing single-tube, the convection current on hobboing cutter surface
The coefficient of heat transfer can be calculated by following formula：The convection transfer rate on hobboing cutter surface is calculated according to qualitative temperature
Nu=CRe bPr 1/3
Wherein, convection transfer rates of the α between main shaft surface and air, unit are W/ (m2℃)；
NuFor nusselt number；
λ is air conduction coefficient, and unit is W/ (mk)；
L is characterized length, is taken as hobboing cutter outer diameter, unit m herein；
Re is Reynolds number；
Pr is Prandtl number；
ρ is atmospheric density, unit kg/m3；
v2For air velocity, unit m/s；
d1For equivalent diameter, hobboing cutter outer diameter, unit m are taken herein；
G is air force viscosity, and unit is kg/ (ms) or Pas；
C, b be constant, obtaining value method such as table 7：
7 C and b value tables of table
| Re | C | n |
| 0.4~4 | 0.989 | 0.330 |
| 4~40 | 0.911 | 0.385 |
| 40~4000 | 0.683 | 0.466 |
| 4000~40000 | 0.193 | 0.618 |
| 40000~400000 | 0.0266 | 0.805 |
Above-mentioned each air physical characterisitic parameter is shown in Table 8：
8 normal atmosphere of table depresses the thermal properties table of dry air
In upper table parameter, only atmospheric density is related to pressure.Tabling look-up can obtain, and during pressure P=0.4MPa, atmospheric density is about
4.558kg/m3, therefore
Because of 40000 ＜ Re, C values 0.0266, b values 0.805,
Nu=CRe bPr 1/3=0.0266Re 0.805Pr 1/3
3) thermal boundary condition is calculated：According to the heat source strength and the result of calculation of thermal boundary condition during gear hobbing, utilize
Finite element emulation software can calculate knife rest portion group temperature field.Temperature is 47.916 DEG C at 1 signal of hobboing cutter, temperature at 2 signal of knife bar
It is 41.192 DEG C to spend, and temperature is 32.235 DEG C at 3 signals at the top of bracket, and temperature is 30.003 DEG C at 4 signal of bracket end cap, back plate
Temperature is 26.575 DEG C at 5 signals, and temperature is 29.711 DEG C at 6 signal of bracket bottom, and temperature is at 7 signal of motor cover bottom
26.847 DEG C, temperature is 29.767 DEG C at 8 signal of motor cover, and temperature is 26.371 DEG C at 9 signal of motor cover, and motor cover 10 is illustrated
It is 26.646 DEG C to locate temperature.
The preferred embodiment of the present invention described in detail above.It should be appreciated that those of ordinary skill in the art without
Creative work is needed according to the present invention can to conceive and makes many modifications and variations.Therefore, all technologies in the art
Personnel are available by logical analysis, reasoning, or a limited experiment on the basis of existing technology under this invention's idea
Technical solution, all should be in the protection domain being defined in the patent claims.
Claims (4)
1. a kind of dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field, it is characterized in that：Include the following steps：
1) heat source strength during gear hobbing is calculated：
A1. the cutting heat generated between hobboing cutter and workpiece by friction and metal plastic deformation is calculated：
Q1=Fv1
Q1＇=k1Q1
Wherein Q1To cut thermal power, unit W；
F is main cutting force, herein value be gear hobbing tangential force, unit N；
v1For cutting speed, unit m/s；
D be hobboing cutter outer diameter, unit m；
N be the hobboing cutter speed of mainshaft, unit r/min；
Q1＇ is under actual condition, is input to the cutting heat of knife rest, unit W；
k1For cutting heat heat transfer ratio, value is 1%~10%；
B1. spindle motor heat production is calculated:
Q2＇=k2Q2
Wherein, Q2For spindle motor heat production, unit W；
N is power input to machine, unit W；
MtFor motor output torque, unit Nm；
Z is motor speed, unit r/min；
η is electric efficiency；
D be hobboing cutter outer diameter, unit m；
FtFor gear hobbing tangential force, unit N；
Q2＇ is input to the cutting heat of knife rest, unit W for motor；
k2For motor heat production heat transfer ratio, value is 8%~12%；
C1. bearing heating is calculated：
Q3=1.047 × 10-4Mn
M=M0+M1
In formula, Q3For bearing heating amount, unit W；
N be the hobboing cutter speed of mainshaft, unit r/min；
Total frictional force squares of the M for bearing, unit Nmm；
M0For the torque related with bearing type, rotating speed and lubricating oil property, unit Nmm；
M1For with bearing suffered by the related moment of friction of load, unit Nmm；
Wherein：
M1=f1P1Dm
Wherein, DmFor bearing average diameter, unit mm；
foFor the coefficient related with bearing type and lubricating system；
Q be bearing rotating speed, unit r/min；
P be the kinematic viscosity of lubricant at the working temperature, unit mm2/s；
f1For with bearing type and related coefficient loaded；
P1To determine the calculated load of bearing frictional torque, unit N；
f1And P1Value determine that method is as follows：
1. single-row radial ball bearing f10.0009 (P of value0/C0)0.55, P1Value 3Fa-0.1Fr；
2. double-row spherical ball bearing f10.0003 (P of value0/C0)0.4, P1Value 1.4YFa-0.1Fr；
3. single-row angular contact ball bearing f10.0013 (P of value0/C0)0.33, P1Value Fa-0.1Fr；
4. double-row angular contact bal bearing f10.001 (P of value0/C0)0.33, P1Value 1.4Fa-0.1Fr；
5. band retainer radial short cylindrical roller bearing f1Value 0.00025~0.0003, P1Value Fr；
6. double row self aligning spherical roller bearing f1Value 0.0004~0.0005, P1Value 1.2YFa；
7. taper roll bearing f1Value 0.0004~0.0005, P1Value 2YFa；
8. spherical roller thrust bearing f1Value 0.0005~0.0006, P1Value Fa(Frmax≤0.55Fa)；
Wherein, P0For bearing Equivalent static load, unit N；
C0For bearing rated static load, unit N；
FaFor axial force suffered by bearing, unit N；
FrFor bearing force in radial, unit N；
Y is works as Fa/FrAxial load factor during ＞ e, e are judgement factor, can be checked in bearing handbook；
Wherein, if P1＜ Fr, then P is taken1=Fr；
P0Obtaining value method it is as follows；
Wherein X0For radial direction static load coefficient；
Y0Axial static load coefficient；
2) thermal boundary condition is calculated：
A2. qualitative temperature is determined：
Wherein, t is qualitative temperature, twFor surface of solids temperature, t∞For fluid temperature (F.T.)；
B2. the convection transfer rate on hobboing cutter surface is calculated according to qualitative temperature
Nu=CRe bPr 1/3
Wherein, convection transfer rates of the α between main shaft surface and air, unit are W/ (m2℃)；
NuFor nusselt number；
λ is air conduction coefficient, and unit is W/ (mk)；
L is characterized length, is taken as hobboing cutter outer diameter, unit m herein；
Re is Reynolds number；
Pr is Prandtl number；
ρ is atmospheric density, unit kg/m3；
v2For air velocity, unit m/s；
d1For equivalent diameter, hobboing cutter outer diameter, unit m are taken herein；
G is air force viscosity, and unit is kg/ (ms) or Pas；
C, b is constant, and obtaining value method is as follows：When Re is 0.4~4, C values 0.989, b values 0.330, when Re is 4~40, C takes
Value 0.911, b values 0.385, when Re is 40~4000, C values 0.683, b values 0.466, when Re is 4000~40000, C takes
Value 0.193, b values 0.618, when Re is 40000~400000, C values 0.0266, b values 0.805；
3) it according to the heat source strength and the result of calculation of thermal boundary condition during gear hobbing, can be calculated using finite element emulation software
Go out knife rest portion group temperature field.
2. the dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field as described in claim 1, it is characterized in that：The knife
When frame portion group uses lubricating grease, p is the kinematic viscosity of lubricating grease at the working temperature, and value is base oil viscosity, unit mm2/
s。
3. the dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field as described in claim 1, it is characterized in that：foTake
Value determines that method is as follows：
1. single-row radial ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, vertical shaft oil bath profit
Sliding or oil jet lubrication takes 3~4；
2. double-row spherical ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, vertical shaft oil
Bath lubrication or oil jet lubrication take 3~4；
3. single-row angular contact ball bearing fog lubrication takes 1, horizontal axis bath lubrication or grease lubrication take 2, vertical shaft bath lubrication or oil spout
Lubrication takes 4；
4. double-row angular contact bal bearing fog lubrication takes 2, horizontal axis bath lubrication or grease lubrication take 4, vertical shaft bath lubrication or oil spout
Lubrication takes 8；
5. band retainer radial short cylindrical roller bearing fog lubrication takes 1~1.5, horizontal axis bath lubrication or grease lubrication take 2~3,
Vertical shaft bath lubrication or oil jet lubrication take 4~6；
6. double row self aligning spherical roller bearing fog lubrication takes 2~3, horizontal axis bath lubrication or grease lubrication take 4~6, vertical shaft oil bath
Lubrication or oil jet lubrication take 8~12；
7. taper roll bearing fog lubrication takes 1.5~2, horizontal axis bath lubrication or grease lubrication take 3~4, vertical shaft bath lubrication or
Oil jet lubrication takes 6~8；
8. thrust ball bearing fog lubrication takes 0.7~1, horizontal axis bath lubrication or grease lubrication take 1.5~2, vertical shaft bath lubrication or
Oil jet lubrication takes 3~4.
4. the dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field as described in claim 1, it is characterized in that：X0And Y0
Obtaining value method it is as follows：In the case of single-row, parallel combinations, when contact angle is 15 °, X0Value is 0.5, Y0Value is 0.46, is connect
When feeler is 18 °, X0Value is 0.5, Y0Value is 0.42, when contact angle is 25 °, X0Value is 0.5, Y0Value is 0.38, is connect
When feeler is 30 °, X0Value is 0.5, Y0Value is 0.33, when contact angle is 40 °, X0Value is 0.5, Y0Value is 0.26；The back of the body
In the case of back of the body combination, combining face-to-face, when contact angle is 15 °, X0Value is 1, Y0Value is 0.92, and contact angle is 18 °
When, X0Value is 1, Y0Value is 0.84, when contact angle is 25 °, X0Value is 1, Y0Value is 0.76, when contact angle is 30 °, X0
Value is 1, Y0Value is 0.66, when contact angle is 40 °, X0Value is 1, Y0Value is 0.52.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711464808.5A CN108133110B (en) | 2017-12-28 | 2017-12-28 | Method for measuring and calculating temperature field of tool rest unit in dry cutting and hobbing process |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711464808.5A CN108133110B (en) | 2017-12-28 | 2017-12-28 | Method for measuring and calculating temperature field of tool rest unit in dry cutting and hobbing process |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108133110A true CN108133110A (en) | 2018-06-08 |
| CN108133110B CN108133110B (en) | 2021-07-02 |
Family
ID=62393855
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711464808.5A Expired - Fee Related CN108133110B (en) | 2017-12-28 | 2017-12-28 | Method for measuring and calculating temperature field of tool rest unit in dry cutting and hobbing process |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108133110B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109164852A (en) * | 2018-07-27 | 2019-01-08 | 同济大学 | A kind of mass concrete self-adaptive temperature and stress control method |
| CN112118050A (en) * | 2020-08-20 | 2020-12-22 | 广州创利宝科技有限公司 | Suspension type optical transmitter and receiver communication equipment |
| CN112446153A (en) * | 2020-12-02 | 2021-03-05 | 山东大学 | Calculation method and system for storage energy field of first deformation region in steady-state cutting |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070053778A1 (en) * | 2004-02-09 | 2007-03-08 | Dube Bryan P | Shroud honeycomb cutter |
| CN103302751A (en) * | 2013-05-27 | 2013-09-18 | 湖南大学 | Device for cutting ceramic with laser-assisted heating |
| CN103438234A (en) * | 2013-08-01 | 2013-12-11 | 常熟市迅达粉末冶金有限公司 | Valve plate |
| CN103862843A (en) * | 2014-03-27 | 2014-06-18 | 深圳市广晟德科技发展有限公司 | Closed-loop control high-precision positioning lifting system of full-automatic solder paste printer |
| CN104216334A (en) * | 2014-09-16 | 2014-12-17 | 北京工业大学 | Selection optimization method of temperature measurement point combination for positioning errors of numerically-controlled machine tool under thermal effect |
| CN104963959A (en) * | 2015-07-13 | 2015-10-07 | 柯晓贤 | Piston-cylinder-fixed type air pressure multi-disc friction clutch |
| CN106001613A (en) * | 2016-07-28 | 2016-10-12 | 哈尔滨工业大学 | Laser heating assisted turning device and method |
-
2017
- 2017-12-28 CN CN201711464808.5A patent/CN108133110B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070053778A1 (en) * | 2004-02-09 | 2007-03-08 | Dube Bryan P | Shroud honeycomb cutter |
| CN103302751A (en) * | 2013-05-27 | 2013-09-18 | 湖南大学 | Device for cutting ceramic with laser-assisted heating |
| CN103438234A (en) * | 2013-08-01 | 2013-12-11 | 常熟市迅达粉末冶金有限公司 | Valve plate |
| CN103862843A (en) * | 2014-03-27 | 2014-06-18 | 深圳市广晟德科技发展有限公司 | Closed-loop control high-precision positioning lifting system of full-automatic solder paste printer |
| CN104216334A (en) * | 2014-09-16 | 2014-12-17 | 北京工业大学 | Selection optimization method of temperature measurement point combination for positioning errors of numerically-controlled machine tool under thermal effect |
| CN104963959A (en) * | 2015-07-13 | 2015-10-07 | 柯晓贤 | Piston-cylinder-fixed type air pressure multi-disc friction clutch |
| CN106001613A (en) * | 2016-07-28 | 2016-10-12 | 哈尔滨工业大学 | Laser heating assisted turning device and method |
Non-Patent Citations (3)
| Title |
|---|
| 唐倩: "盘形凸轮共轭淬火机构设计及感应加热数值模拟", 《机械传动》 * |
| 李文化: "平面二次包络环面蜗杆加工专用机床结构设计及性能分析", 《中国优秀硕士学位论文全文数据库 工程科技Ⅰ辑》 * |
| 韩江 等: "数控滚齿机刀架温度场及热误差仿真分析", 《合肥工业大学学报》 * |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109164852A (en) * | 2018-07-27 | 2019-01-08 | 同济大学 | A kind of mass concrete self-adaptive temperature and stress control method |
| CN112118050A (en) * | 2020-08-20 | 2020-12-22 | 广州创利宝科技有限公司 | Suspension type optical transmitter and receiver communication equipment |
| CN112446153A (en) * | 2020-12-02 | 2021-03-05 | 山东大学 | Calculation method and system for storage energy field of first deformation region in steady-state cutting |
| CN112446153B (en) * | 2020-12-02 | 2023-01-06 | 山东大学 | Calculation method and system for storage energy field of first deformation region in steady-state cutting |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108133110B (en) | 2021-07-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108133110A (en) | A kind of dry measuring method for cutting gear hobbing process intermediate slide portion group temperature field | |
| CN106649982B (en) | Method for calculating friction torque of large-cone-angle conical main bearing of wind driven generator | |
| Kim et al. | A numerical approach to determine the frictional torque and temperature of an angular contact ball bearing in a spindle system | |
| Nguyen-Schäfer | Computational design of rolling bearings | |
| Sarangi et al. | Stiffness and damping characteristics of lubricated ball bearings considering the surface roughness effect. Part 1: theoretical formulation | |
| Yan et al. | Study on thermal induced preload of ball bearing with temperature compensation based on state observer approach | |
| Yu et al. | Reliability analysis of rolling bearings considering internal clearance | |
| Kaczor et al. | The influence of preload on the work of angular contact ball bearings | |
| US20140363112A1 (en) | Rolling bearing | |
| Brewe et al. | Film-transfer studies of seven ball-bearing retainer materials in 60 R (33 K) hydrogen gas at 0.8 million DN value | |
| Majdoub et al. | Kinematic equilibrium of rollers in tapered roller bearings | |
| CN110399670B (en) | Method for establishing fluid dynamic and static ball bearing oil film pressure calculation model | |
| Pham et al. | A method to evaluate wear and vibration characteristics of CNC lathe spindle | |
| Shaw et al. | The hydrosphere—a new hydrodynamic bearing | |
| Antunović et al. | Mathematical model for temperature change of a journal bearing | |
| CN111881523B (en) | Correction method for rolling bearing temperature analysis related empirical formula | |
| Han et al. | Thermal Elastohydrodynamic Lubrication Analysis of High-Speed and Light-Load Rolling Bearing with Double Rings Rotation | |
| Chen et al. | A thermal analyzing model for high speed motorized spindles—thermal properties | |
| Martin | Paper 16: Minimum Allowable Oil Film Thickness in Steadily Loaded Journal Bearings | |
| Zhang et al. | Experimental comparison of the seizure loads of gray iron journal bearing and aluminum alloy journal bearing under aligned and misaligned conditions | |
| Wen et al. | Analysis of cage slip in angular contact ball bearing considering non-Newtonian behavior of elastohydrodynamic lubrication | |
| BRECHER et al. | New bearing steel for high-speed applications | |
| Jiaming et al. | Test and analysis of skidding characteristics of high-speed and light-load cylindrical roller bearings | |
| Bamberger et al. | Effect of speed and load on ultra-high-speed ball bearings | |
| Mathur et al. | System and Component level Design Procedure for High Reduction Ratio Pericyclic Drive |
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 | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20210702 Termination date: 20211228 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |