0000
no help text available ..
5050:MEASURE2
The diametral two-sphere mass is obtained from the measurement of the gear by means of two opposing ball and pin diameters.
If you enter 0, the program recommends an appropriate diameter that you can use or reject.
5060
The extent of the upper and lower deviations is identical and can either be selected from
5061
the ISO tolerance series or entered manually.
5080:DIMEN
Enter pressure angle in degrees. The default is the normal pressure angle of 20 degrees.
See DIN 3960, paras 3.3.3 and 3.3.4.
Exact results can only be expected for load carrying capacity proof according to DIN 3990 when alpha = 20 degrees.
5090:DIMEN
The skew angle (beta) = 90 degrees - pitch angle; for straight toothed spur gears is alpha = 0.
See also DIN 3960, para 3.5.1.
5100:DIMEN
Enter normal module.
5110:DIMEN
Gear 1 is always the pinion, that is, the smaller gear.
5120:DIMEN
Enter a negative number for the number of teeth for ring gears.
5130:DIMEN
If the gear and pinion have different face widths, enter the smaller value.
For different tooth widths ZAR1 calculates with overlapping tooth widths, while the individual tooth widths are
relevant for the tooth root stability.
5140:DIMEN
The center distance can be modified by approx. ñ5% compared to the reference center distance
5141
by means of addendum modification.
5142
If you enter 0, the program recommends adopting the center distance without addendum modification.
5150:PROFILV1
The addendum modification affects the center distance and tooth thickness.
5151
The center distance is recalculated if you choose a different addendum modification.
5160:CLEARANC
The total clearance must be approx. 0.12*mn.
Total clearance, reduction and reduced outer diameter are directly dependent on each other.
Therefore, you need only input one of these values.
5170:CLEARANC
If you input addendum reduction, outside diameter and total clearance will be calculated
5180:CLEARANC
Clearance, addendum reduction, and reduced outside diameter dak are directly dependent on each other.
5181
For this reason, you need enter only one of the following 3 values.
5200
Input of gear quality, tolerances, machining allowance and measurement.
5210
Input gear quality according to DIN
Quality 1 & 2:  Master gears.
Quality 3:  Master gears for measuring area.
Quality 4:  Master gears for gearing.
Quality 5:  Gears for tool machines, turbines, etc.
Quality 6:  As for 5, as well as car gears.
Quality 7:  Gears for lorries, trucks, rail vehicles, etc.
Quality 8 & 9:  Heavy vehicles, low gears.
Quality 10 - 12:  Agricultural machinery and mechanical engineering.
5220:DIMEN
The tolerance of flank clearance is defined by Tsn.
The manufacture addendum modification, tooth shape, df, tooth width and sphere
mass are also influenced.
5230:DIMEN
The minimum backlash is defined by the tolerance field.
The manufacture addendum modification, tooth shape, df, toothe width and sphere
mass are also influenced.
Upper and lower values can also be entered manually.
If you type Asne=0 and Asni=0, you will get a gear without flank clearance
5240:DIMEN
Pay attention to the negative sign for ring gears
5250:Z1-E-067
Input 0 if the gear is finished by the cutting-tool
CAD always presents the finished gear.
To see the end result enter 0 here.
5260:MEASURE1
ZAR1 calculates the measurement width for the gear from the entered number of teeth.
The toothe measurement number entered for ring gears must be negative.
If you enter 0, an appropriate value will be suggested.
5270
For Rad1=Rad2 (same material) the values for wheel and pinion are accepted.
With ZAR1+ you can choose a material from the data base.
5280
Choose the appropriate material group.
With ZAR1+ you can choose a material from the data base.
5290
The material description is only for information purposes and will also be printed out.
With ZAR1+ you can choose a material from the data base.
5300:SH
The warm treatment influences the stability opposed to tooth root permanent break and pit appearance.
If the safety margin is less than 1, the time until tooth root permanent break and pit appearance will be calculated.
If the safety margin SH is less than 1/ZNTmax, pitting will occur immediately.
With SF < 1/YNTmax tooth break occurs immediately.  With 1/SH (SF) between 1.0 and ZNTmax (YNTmax) the life expectancy is calculated.
5310
The tooth root permanent stability Sigma FE must not be confused with tooth root permanent stability Sigma F lim of the test wheel.
With ZAR1 you can choose a material from the data base.
5320
Acceptable flank shot.
With ZAR1+ you can choose a material from the data base.
5330
With the use of HAERTE software you can convert from Vickers, Rockwell or tensile strength to the Brinell strength.
5340
Important for calculation of safeguard against pitting.
5350
The E modulus for steel is approximately 210 000 N/mmý.
With ZAR1+ the value is accepted from the material data base.
5360
The poisson ratio æ for steel is approximately 0.3.
With ZAR1+ the value is accepted from the material data base.
5370
The density of steel is approximately 7.8 kg/dm^3.
With ZAR1+ the value is accepted from the material data base.
5400:PROFILE
You can select a tooth profile to DIN 867 or define the tool yourself.
5410:PROFILE
See help picture "Profile" with the dimensions of the toothing tool.
5420:PROFILE
See help picture "Profile" with the dimensions of the toothing tool.
5430:PROFILE
If you enter 0 or the pressure angle alfa for the transverse pressure angle at a point,
no tip chamfer is taken into account.
The edge break flank profile angle must be greater than the pressure angle
5440:PROFILE
See help picture "Profile" with the dimensions of the toothing tool.
5450:PROFILE
The protuberance angle must be smaller than the pressure angle.
5451
Default is 6 degrees.
See help picture "Profile" with the dimensions of the toothing tool.
5460:PROFILE
The protuberance factor should be about 0.02
See help picture "Profile" with the dimensions of the toothing tool.
5470:PROFILE
If you enter 0, the program recommends the greatest possible tip radius.
See help picture "Profile" with the dimensions of the toothing tool.
5480:PROFILE
You can either select the tool or freely define it on the basis of the tool dimensions.
5490 PROFILE
In default entry, for example, a profile will be choosen directly according to DIN 867.
The on-line entry is suitable when it is necessary to change the individual tool factors.
5500:SPITTING
The rotational speed must not be 0!  Please enter a low speed (e.g. 100 rpm)
5501
for gear trains that are idling.
5510:SF
When you enter a power value (next step), the torque is recalculated.
By entering 0, a possible torque will be recommended.
5520:STOOFRAC
If you enter a power value, the torque is recalculated.
5530
When calculating according to DIN 3990, part 1, you must also define bearing and
tooth bearings.
5540:TBEARING
Please refer to the manual or to DIN 3990 for a table containing the various tooth bearings.
5550:BEARING
Please refer to the manual or to DIN 3990 for a table containing the various options
5551
for bearing arrangements.
5560:BEARING
For distance between bearings "l", see Pinion bearing.
5570:BEARING
For offset "s", see Pinion bearing.
5580:DSH
The inside diameter of cast and welded gears is required for calculating the resonance speed.
5581
For solid gears, di = 0.
5590
The arithmetic mean of the tooth flank peak-to-valley heights of gear 1 and gear 2 should be taken
5591
as the peak-to-valley height.
5595:EINGRIF2
For normal gear steps there is one tooth entry per revolution.
Intermediate gears have two tooth entries per revolution.
Planet gears have two entries per planet gear, sun and ring gears have the
same number of entries as there are planet gears.
5600:KA
The service factor is dependent on the nature of the load on the gearing.
5601
It is entered separately for the tooth root load-bearing capacity and the pitting capacity.
5602
Reference values in DIN 3990 Part 1 and Part 41 (motor vehicle transmission).
5605:EINGRIF2
Input 0 if there is no alternate load. YA is 1.0 in this case.
For intermediate and planet gears a change of load occurs with each revolution.
A revolution is corresponds here to a period.
The number of load changes/periods can be dependent on the application.
5610
If you enter 0 for the shaft diameter of the pinion, the program recommends a value in the range
5611
of the root diameter.
5615
ZL = 1 with a viscosity of 100mmý/s at 50øC.
5620:DOUBLE
Specify herringbone gearing or double helical gearing.
With herringbone gearing or double helical gearing the axial forces balance each other out.
5630
You should expect a supporting effect with open gearing if d1/dsh >= 1.15.
5631
There is no supporting effect when d1/dsh < 1.15, nor when a pinion with featherkey joint
5632
or similar is fitted.
5633
You should also expect practically no supporting effect with conventional shrink fits.
5640
End relief protects the tooth ends against overloading that arises due to alignment deviation.
5641
The extent of relief at the tooth ends is intended to compensate for the expected alignment deviation
5642
caused by generating variations and deformation.
5650
Crowning is intended to compensate for generating variations and deformation under load
5651
and in particular to relieve the load on the tooth end.
5660
Entry with a low load promotes KH beta and KF beta.
5670
Correction of the helix angle is intended to compensate for the deformation that arises due to bending
5671
and torsion under service load.
5680:SF
The dynamic factor includes the inner dynamic additional forces.
The calculation follows according to method B, in order that gears with
revolutions in the upper critical area may also be included.
5690:SH
The width factors take into account the effect of irregular load distribution
on the flank shot (KH beta) and the tooth root stress (KF beta).
5700:SF
The width factors take into account the effect of irregular load distribution
on the flank shot (KH beta) and the tooth root stress (KF beta).
5710:SH
The spur factors take into account the effect of irregular load distribution
on several gear pairs in action at the same time.
5720:SF
The spur factors take into account the effect of irregular load distribution
on several gear pairs engaged at the same time.
5730:SH
The zone factor includes the influence of the tooth flank curvature in the
rolling point of Hertz's compression, and the conversion of the circumferential
force at the part cylinder on the normal force at the rolling cylinder.
5740:SH
The single entry factor is used for conversion of the flank compression in the
rolling point to the flank commpression in the inner single entry point.
5750:SH
The upper limit factor takes into account the influence of profile and jump
upper level on the surface compression.
5760:SH
The skew factor Z beta takes into account the influence of the skew angle on
the flank compression.
5770:SH
ZL takes the influence of the nominal viscosity into account.
5775:SH
ZV takes the influence of the circumferential speed into account.
5785:SH
ZR takes into account the influence of the tooth flank roughness on the
effectivness of the lubricant.
5780:SH
The material pairing factor takes into account the increase of fatigue
strength of a gear made of steel, toughened steel or grey cast iron with
ball graphite, when paired with a toughened cog wheel with smooth tooth
flanks.
5790:SH
The size factor takes into account the static, theoretical and technological
stability size influence on the pitted load-carrying capacity.
5800:SF
The shape factor YF takes into account the influence of the tooth shape on
the actual tooth root stress for force attack in the outer single mesh point.
5810:SF
The stress factor YS takes into account the conversion of the bending-nominal
stress with force attack in the outer single entry point on the local tooth
root stress.
With this YS includes the stress increasing effect of the root curvature
(notch effect), and the fact that a complex stress situation exists in the
critical root cross-section.
5820:SF
The skew factor Y beta takes into account the skew angle of the tooth root
stress.
5850:SF
The size factor YX takes into account the static, theoretical and technological
stability size influence of the construction sizes on the tooth root stability.
5855:SF
The factor YA takes into account the number of meshes and load changes.
5860
Transmission ratio u = revolution gear 1 / revolution gear 2.
The ration for ring gears must be entered as a negative number.
5880:HPD4
Here you can enter text or a number for processing and clearance with short
addendum.
5900:DIMEN
Enter pressure angle in degrees.  Default = 20.
5905:DIMEN
beta = 0 for straight spur gears.
5910:DIMEN
Enter normal module.
Norm I:  0.05  0.06  0.08  0.1  0.12  0.16  0.2  0.25  0.3  0.4  0.5  0.6  0.7  0.8  0.9  1
1.25  1.5  2  2.5  3  4  5  6  8  10  12  16  20  25  32  40  50  60
5915:DIMEN
Gear 1 is always the pinion, that is, the smaller gear.
5920:DIMEN
Enter a negative number for the number of teeth for ring gears.
5925:DIMEN
If the gear and pinion have different facewidths, enter the smaller value.
5930:DIMEN
The addendum modification affects the center distance and tooth thickness.
Take note of the influence of the addendum modification on the specific gliding.
5935:DIMEN
The addendum modification affects the center distance and tooth thickness.
Enter 0 to calculate the Zero axial distance (for x1 = 0 and X2 = 0).
5940:DIMEN
The clearance must be approx. 0.12*mn.
Enter 0 to obtain the ideal addendum.
5945:DIMEN
The clearance must be approx. 0.12*mn.
Enter 0 to obtain the ideal addendum.
6000:PROFILE
The dedendum of tool provides the addendum of the finished toothing.
The dedendum hfPO/mn is 1.0 for toothing accord. DIN 867.
6005:PROFILE
The addendum of tool provides the dedendum of the finished toothing.
The addendum haPO/mn is 1.25 for toothing accord. DIN 867.
6010:PROFILE
The tool chamfer generates involute tip edge breakage on the finished gear,
which reduces the contact impact from the bending deformation of the gears
under load.
Enter chamfer pressure angle (alpha KPO) in degrees.
Alpha KPO must be greater than the entry angle alpha.
As a guide you can enter 45 degrees.
6015:PROFILE
The tool chamfer generates involute tip edge breakage on the finished gear,
which reduces the contact impact from the bending deformation of the gears
under load.
After the angle of chamfer alpha kPO has been defined, then hFfPO/mn can be entered.
If alpha kPO = alpha, then hFfPO/mn will be set = to hfPO/mn.
6020:PROFILE
Enter the protuberance angle alpha prPO in degrees, which must be smaller than alpha.
A standard value is alpha prPO 0 6ø.
A protuberance miller is used when the gear is pre-milled and ground.
6025:PROFILE
A standard value for the protuberence factor is prPO/mn = 0.02.
A protuberance miller is used when the gear is pre-milled and ground.
6030:PROFILE
The fillet radius factor generates the tooth root radius in the finished toothing.
Enter fillet radius factor
6400:LOADKOLL
After input of a collective load, ZAR1 calculates the equivalent torque and application factor KA.
For new input "Enter New Step".  Enter the collecitve load in the correct order, commencing with the greatest
torque area.  Not until "Calculation" will the KA factors be calculated and accepted!
To alter, choose the appropriate step.  If you wish to enter further steps go to -> "Enter New Step".
Important:  Input of collective load must occur AFTER Input/Calculation stability.
6410:LOADKOLL
Using the cursor keys, choose the position where a further torque area should be entered.
6430:LOADKOLL
Enter the proportional torque for the load interval in Nm.
6440:LOADKOLL
Enter number of load changes for the load interval.
If only running times are availabe, these must be converted via the speeds and number of contacts/revolutions into load changes.
In addition it is possible to enter values to the power of ten, e.g. 5.4e6 for 5400000.
6460:LOADKOLL
The application factor KAH (pit) and KAF (tooth root) calculated from the collective load can be accepted in the
stability calculation according to DIN 3990.
6480:LOADKOLL
Enter a multiplication faktor for all load changes.
6490:LOADKOLL
Using the cursor keys, choose the step to be deleted.
6500:LOADKOLL
The collective load can be output as a diagram along with the load line for tooth foot stress or
Hertz's compression.
6600
30 individual pictures are allowed.  Attention:  Very high calculation times for more than 20 steps.
With the Windows version you will have to wait a while until the pictures appears.  However it is
possible to quickly repeat the picture with a double click of the left-hand mouse button.
6610
Push any key to obtain the next picture, with ESC or ENTER you can exit the simulation.
7500
Through EDI files you can setup an interface for data exchange between ZAR1+ and other programs.
The file format is described in the hand book.  The format is oriented on the FVA format.
7520
Enter file name (without .EDI extension).
8220
Gear 1 is always the smaller gear, e.g. pinion.
8230
By generating DXF and IGES files you can export scale drawings and tables to CAD.
8250
The flank direction is output to the table.
8270
Drawings toothing tools, tooth, gear, tooth contact and gear steps can be displayed
on screen, or you can generate DXF or IGES files for CAD.
8272
Under "Config" you can choose different display options and settings.
8275
Here you can choose different display options and settings.
8276
Do not leave Configuration with <ESC>, otherwise the options you have choosen
8277
will not be saved.
8280:EINGRIF1
Collision due to too many planet gears can be determined in the picture "Planetary Gear".
8285:EINGRIF1
You can have either the gear with the larger or smaller number of teeth
as the sun gear in the drawing for outer toothed gear steps.
8300
With a higher value you increase the accuracy, however, the drawing size is then also increased.
8302
Default value is 20.
8303
You can increase the working speed during simulation by reducing the value.
8310
You should work with poly lines if you wish to convert a DXF file to a CNC
8311
file when using the DXF Manager, so that the outline won't be interrupted.
8320
With ring gears you can view the working gears and ring gears in "Gears with
8321
envelopes and involutes".  This enables visual control of contact interference.
8323
Higher values increase resolution, however they also increases drawing time and size.
8324
Default value is 200.
8325:ZA-PROF
The tooth involent is obtained from the envelope of the tooth profile.
8326
Default value for the number of envelopes is 10.
8330:ABMASS
The torsional backlash is obtained from the difference between the nominal and manufacture
8331
addendum modification coeffecient.
8332
You can see how input effects the backlash in the contact picture.
8333
ZAR1 calculates the values for the greatest and smallest factor from the values input
8334
in the tolerance field under "Quality".
8340:ABMASS
The tooths will overlap if the xe value is too large.
Play increases if the xe value is too small (compared with x nominal).
8345
For helical gears the tool head is no radius, but is drawn as polyline.
You can configure the resolution for the number of points.
8350:ABMASS
You can check the influence on torsional backlash by viewing the tooth contact picture
with greatest and smallest axial distances.
8360:ABMESS
Here you can enter the axial distance with upper and lower tolerence in order to
8361
make visible in the tooth contact picture how tolerence effects quality
8365:ABMESS
You can show the toothing pictures with or without transverse circle, composite
8366
circle, root circle, etc.
8370
You can show the tooth contact pictures with the gears in different positions.
8520:EINGRIF1
The calculated gear pair can be used in the planetary gear exposition.
8530
The sun gear/planet gear or ring gear/planet gear pairs can be used
8531
in the full calculation.
8532
When entering geometry, you must still define addendum reduction and tooth play respectively.
8533
The easiest way is to enter 0 for c1 and c2 in the online input.
8534
ZAR1 will then calculate optimal clearance.
8600:DIMEN
Enter pressure angle in degrees
8605
Helix angle á in degress.   á = 0 for spur gearing.
8610:EINGRIF 1
Normal modulas mn.
8615
Number of teeth of the sun gear.
8616
If you enter 0, an appropriate tooth number will be recommended.
8617
By entering "<" or ">", the next smallest or next largest possible tooth number can be choosen.
8620
Number of teeth of the planet gear.
8621
If you enter 0, an appropriate tooth number will be recommended.
8622
By entering "<" or ">", the next smallest or next largest possible tooth number can be choosen.
8625
Number of teeth of the ring gear.
8626
If you enter 0, an appropriate tooth number will be recommended.
8627
By entering "<" or ">", the next smallest or next largest possible tooth number can be choosen.
8630
Enter addendum modification coefficient x of the sun gear.
8635
Enter addendum modification coefficient x of the planet gear.
8640:PROFILV2
The addendum modification coefficient x of the ring gear is determined from the
8641
tooth number ratio as well as by xS and xP.
8645
Transmission ratio zH/zS.  The program calculates a gear pair referenced to zS when you enter this.
8650:EINGRIF 1
Rotating ration = transmission ratio + 1.
8655:EINGRIF 1
Number of planet gears (default = 3)
9010
Fatiguestr. tooth root stress must not be confused with Sigma Flim (differ by a cooeffecient of 2!).
Sigma Hlim:  Fatiguestr. Hertziancont.press.  Example data for 42CrMo4: SigmaFE=500, SigmaHlim.=1000, HB=500, E modulus=210000, mue=0.3, density=7.85.
9020:ZA-MESS1
ZAR1 calculates tooth width and diametral two-ball and roller mass for the entered number of teeth
measurment and ball and roller diameters respectively.  You can first, if you wish have the
recommended values calculated and then adjust the ball and roller diameters to your company's norm.
9025:ZA-MESS2
9030
The inner diameter for cast and welded gears is required for calculation of the resonance speed. For solid gears di = 0. Tooth meshing: For normal gear steps ther is one tooth contact per revolution. Intermediate gears have two tooth contacts per
revolution. For planetary gears, the planet gears have two tooth contacts, for sun and ring gears the number is identical to the number of planet gears. Load change number = 0. The coefficient YA is then 1. For intermediate gears and planet gears
a load change occurs for every revolution. A revolution is equal to a period. The number of load changes/periods is dependent on the application. The roughness depth is the arithmetic mean of the flank roughness depth between gear 1 and gear 2.
The application coefficient is dependent upon the gear strain type. It is entered separately for tooth root load-bearing capacity and flank load-bearing capacity. With a viscosity of 100 mmý/s at 50øC then ZL = 1. For double-helical toothing the
axial forces cancel each other out. In addition, there are effects when calculating KH beta and KF beta according to DIN 3990.
9040
The total of the addendum modification coefficient is calculated from the axial distance, which you must now distribute between x1 and x2.  With "recommendation" the factors
are distributed according to equal flexural load of the tooth root.  Another method is to distribute according to equal specific sliding.  You can obtain additional information
about the distribution of addendum modification.
9050
By entering 0 for the shaft diameter of the pinion a root diameter value will used. You should reckon on support effect when d1/dsh >= 1.15. No support effect will occur when d1/dsh < 1.15, or with added pinion with sliding key connection or
similar. Even with normal pressed fits practically no support effect is to be expected. Shrinkage due to low loads promotes the factors KH beta and KF beta. Skew angle correction should compensate for the bending and torsional deformation occuring
from operating loads. Crowning should compensate for manufacturer differences and deformation under pressure, and above all, take the strain off of the tooth ends. End withdrawal protects the tooth ends from over-load resulting from angular
alignment deviation. End-with drawal protects the tooth ends from overload resulting from alignment deviation. The amount of withdrawal at tooth end should compensate for the expected alignment deviation (due to manufacturer differences and
deformation).
9500
The abbreviations stand for: WST_NR=mat.number (max.9 chars), WST_NAME=mat.name (max.12 chars), W=mat.type (1=Structural steel, 2=Case-hardened steel, 3=Heat treated steel, 4=Speroidal-graphite cast iron, pearlitic or bainitic,
5=Spheroidal-graphite cast iron, ferritic 6=Gray-cast iron, 7=All-black malleable cast iron, 8=others), WST_ART=mat.type, B=heat treatment (0=none, 1=heat-treated, 2=case-hardened, 3=induction-hardened, 4=flame-hardened, 5=gas-nitrided,
6=bath-nitrided, 7=nitro-carb. BEHANDLUNG=heat treatment HB_FLANKE=Brinel hardness flank, SIGMA_H=max.Hertzian stress(N/mmý), SIGMA_F=max.tooth root stress [N/mmý], E_MODUL=modulus of elast.[N/mmý], MUE=Youngs coeff., DENSITY= kg/dm3
INFO=Add.Information (max.60 chars).
0000
