ball/flying valve gear motor

[PIETRO2002]

second agma 2001 - iso - din for external and internal wheels:
x>0 if the tool comes out of the material
x<0 if the tool enters the material

according to jis for external wheels:
x>0 if the tool comes out of the material
x<0 if the tool enters the material
according to jis for external wheels:
x<0 if the tool comes out of the material
x>0 if the tool enters the material
this because jis does not consider difference between internal or external wheel but motion is absolute.

I think positive if the tool moves away from the center, negative if the tool approaches the center.

 

[PIETRO2002]

I tried to make my own variant. What do you think?

I have seen that you can increase the strength of the tooth well by playing with this coefficient. Plus I gave him 0.1mm backlash on satellites.

link for model 3d: https://a360.co/3nkhxe4
View attachment 60355View attachment 60356

but did you see that with correction 1.5 you have a negative addendum? It's not possible!

 

[meccanicamg]

second agma 2001 - iso - din for external and internal wheels:
x>0 if the tool comes out of the material
x<0 if the tool enters the material

according to jis for external wheels:
x>0 if the tool comes out of the material
x<0 if the tool enters the material
according to jis for external wheels:
x<0 if the tool comes out of the material
x>0 if the tool enters the material
this because jis does not consider difference between internal or external wheel but motion is absolute.

What the hell did I say, wrong errata corrige?
second agma 2001 - iso - din for external wheels:
x>0 if the tool comes out of the material
x<0 if the tool enters the material (to the center)
second agma 2001 - iso - din for internal wheels:
x>0 if the tool comes out of the material (to the center)
x<0 if the tool enters the materialaccording to jis for external and internal wheels with absolute radial reference. then comes as follows.
external:
x>0 if the tool comes out of the material (from the center to the outside)
x<0 if the tool enters the material
inside:
x<0 if the tool comes out of the material
x>0 if the tool enters the material (from the center to the outside)this because jis does not consider difference between internal or external wheel but motion is absolute.

I should have written it right now.

 

[meccanicamg]

I think positive if the tool moves away from the center, negative if the tool approaches the center.

but could not use only one reference?

 

[meccanicamg]

but did you see that with correction 1.5 you have a negative addendum? It's not possible!

In fact, the agma chart is below \( \sigma x < -0,6 \)

 

[Mattymecc]

thanks to mechanicsmg and pietro2002 for clarification.

 

[PIETRO2002]

In fact, the agma chart is below \( \sigma x < -0,6 \)

My annotation was adorned! :

 

[Enrico Povolo]

My annotation was adorned! :

As always, don't give me a good one? (I play, of course, better so)

Didn't I notice? I'm trying to do it again tomorrow. . .
to make a "truth" I also tried to animate the design and seemed all appropriate. . .
But I had some doubts about the crown, even if it turned well, visually there was something that didn't come back.
I had corrected this way to strengthen both solar and satellite teeth as they are the most suffering. how and where would you fix it?

feeling my current supplier for sintered as accuracy manages to reach jis6 and khk recommends on all my stages a 0.1mm backlash, but I think you consider jis4... can it be okay anyway?

personally I would not go beyond x1+x2=1 if I do not want to roll on a flat tooth....in fact +0.5+(-1.5)=-1

'
You mean by a couple of wheels? i.e. the sum between xsolar solar e xsatellite must stay between -0.6 and +1 and same thing for the sum between xsatellite e xcrown ? ...or is the sum of all three xes?

then I tried to make a variant even in the third stage on the false line of this, and here I wonder: if a stage like this (z15-30-75, m1) has no interference problems is better to leave it unchanged or can you change it at will?

 

[meccanicamg]

lx torque of wheels are those that gear together, once solar satellite and once satellite/crown.
Since you are using khk gear calculator tries to also do flex and wear checks to see what is best.

 

[Calender]

So you think it's better not to put it?

exactly.

how and where would you fix it?

You mean by a couple of wheels? i.e. the sum between xsolar solar e xsatellite must stay between -0.6 and +1 and same thing for the sum between xsatellite e xcrown ? ...or is the sum of all three xes?

I bring you back the procedure we used in my old company, to make a choice of "maximum" of the values of the profile of the teeth when making a correction (present on the baldassini). (although it is dated as a manual and the regulations are not always updated is still a valid reference)

 

[Calender]

feeling my current supplier for sintered as accuracy manages to reach jis6 and khk recommends on all my stages a 0.1mm backlash, but I think you consider jis4... can it be okay anyway?

try to see din 3967 and the like, however I place a table taken from a well-known manufacturer (just to give you an idea)

 

[meccanicamg]

As always, don't give me a good one? (I play, of course, better so)

Didn't I notice? I'm trying to do it again tomorrow. . .
to make a "truth" I also tried to animate the design and seemed all appropriate. . .
But I had some doubts about the crown, even if it turned well, visually there was something that didn't come back.
I had corrected this way to strengthen both solar and satellite teeth as they are the most suffering. how and where would you fix it?

feeling my current supplier for sintered as accuracy manages to reach jis6 and khk recommends on all my stages a 0.1mm backlash, but I think you consider jis4... can it be okay anyway?

'
You mean by a couple of wheels? i.e. the sum between xsolar solar e xsatellite must stay between -0.6 and +1 and same thing for the sum between xsatellite e xcrown ? ...or is the sum of all three xes?

then I tried to make a variant even in the third stage on the false line of this, and here I wonder: if a stage like this (z15-30-75, m1) has no interference problems is better to leave it unchanged or can you change it at will?

pair = two

 

[meccanicamg]

in case of gearboxes that do not work in oil baths and that do not work with high intermittent services and that need positioning accuracy you can have a reduced game.
on din 3967 there are various tolerance classes to be adopted according to use.
I'll take you back. Home.

 

[PIETRO2002]

to those interested in deepening the topic corrections dentature allego a pdf.

 

[Mattymecc]

I looked at the formulas of niemann for the theoretical game jt and for the normal game jn, which are calculated through the tolerances indicated by the table of mechanicsmg, but knowing jt or jn how is the tolerance to be assigned to the wildaber measure? I looked at a couple of drawings and noticed that jn is double the tolerance assigned to the wildaber measure (or discard), is it a coincidence?

 

[PIETRO2002]

I looked at the formulas of niemann for the theoretical game jt and for the normal game jn, which are calculated through the tolerances indicated by the table of mechanicsmg, but knowing jt or jn how is the tolerance to be assigned to the wildaber measure? I looked at a couple of drawings and noticed that jn is double the tolerance assigned to the wildaber measure (or discard), is it a coincidence?

I did a test with the khk program, hypothesized two toothed wheels, in the first test I kept the theoretical data, in the example I considered two wheels module 1 z 50.
In the second test, on a wheel I made a correction of x= -013, in practice, to give game to the teeth, with the creator you enter more than the theorist. I'll attach the two sheets to you, so you realize the variations on the control quotas.

 

[Mattymecc]

thanks for the example but what are tolerances in relationships? I would also like to know how they normally settle, are there any formulas or procedures about it?

 

[PIETRO2002]

based on the tolerance classes that you can see on the tables that placed mechanicsmg, depends on the operation, whether it has to be a gear that rotates quickly or not, depending on the construction of the gear if it has the rectified teeth or cut by maker, according to the lubrication.. etc. etc.
a gear that must be silent must not have so much game, but this provides good detachment work.

 

[PIETRO2002]

thanks for the example but what are tolerances in relationships? I would also like to know how they normally settle, are there any formulas or procedures about it?

I'll put a pattern for you to be clearer.
Knowing the tolerance class you know what the tooth thickness is, max and minimum.
so you know the normal game that there must be, from them you get the radial "correction" share that you have to create on the gear so you have the required game.

 

[Mattymecc]

thank you again for the clarifications, but I think not to be explained: with the tables of mechanicsmg I find the tolerance of tooth thickness and that on the whole, then calculate the game with the formulas of niemann. but on the "cartellino" of the measures of the toothed wheel, what tolerance do I put for the measure of discard?
The scheme you made me is the relationship between normal and transversal play?