Dependent tolerance according to GOST R 50056-92 - variable tolerance of the shape, location or coordinating size, the minimum value of which is indicated on the drawing or in technical requirements and which is allowed to be exceeded by an amount corresponding to the deviation of the actual size of the considered and (or) base element of the part from maximum limit material. According to GOST 25346-89, the maximum material limit is a term referring to that of the limit sizes, which corresponds to the largest volume of material, i.e. maximum shaft size limit dmax or the smallest limit hole size D min.

The following tolerances can be assigned as dependent:

• form tolerances:
  • - tolerance of straightness of the axis of the cylindrical surface;
  • - flatness tolerance of the symmetry surface of flat elements;
• location tolerances (orientation and location):
• - tolerance of perpendicularity of the axis or plane of symmetry relative to the plane or axis;
• - tolerance of the inclination of the axis or plane of symmetry relative to the plane or axis;
• - alignment tolerance;
• - symmetry tolerance;
• - tolerance of the intersection of the axes;
• - positional tolerance of the axis or plane of symmetry;
• tolerances of coordinating dimensions:
• - distance tolerance between the plane and the axis or plane of symmetry of the element;
• - tolerance of the distance between the axes or planes of symmetry of two elements.

Full value of dependent tolerance:

where T t in - the minimum dependent tolerance value specified

on the drawing, mm;

Gdop - permissible excess of the minimum value of the dependent tolerance, mm.

Dependent tolerances are recommended to be assigned, as a rule, for those elements of parts to which requirements are imposed. collection in connections with a guaranteed gap. Tolerance T m[P is calculated based on the smallest connection gap, and the permissible excess of the minimum value of the dependent tolerance is determined as follows:

for shaft

For hole

where d a and /) d - the actual dimensions of the shaft and hole, respectively, mm.

The value of G add can vary from zero to the maximum value. d

If the shaft has a valid size d min , and hole D max , then

for shaft

For hole

where TdwTD- size tolerance of the shaft and hole, respectively, mm.

In this case dependent tolerance has a maximum value:

for shaft

For hole

If the dependent tolerance is related to the actual dimensions of the element under consideration and the base element, then

where Gd 0P.r and Gd 0P.b - allowable excesses of the minimum value of the dependent tolerance, depending on the actual dimensions of the considered and basic elements of the part, respectively, mm.

Examples of the application of dependent tolerances are:

• - positional tolerance of the location of through holes for fasteners (Fig. 2.17, a);
• - alignment tolerances of stepped bushings and shafts (see Fig. 2.17, b, in), assembled with a gap;
• - tolerance of the symmetry of the location of the grooves, for example, keyways (see Fig. 2.17, d);
• - tolerance of perpendicularity of the axes of the holes and end surfaces of body parts for glasses, plugs, covers.

Rice. 2.17.a - positional tolerance of holes for fasteners; b, c - alignment of the surfaces of the stepped bushing and shaft; G - symmetry keyway relative to the shaft axis

Dependent location tolerances are more economical and beneficial for production than independent ones, as they expand the tolerance value and allow the use of less accurate and labor-intensive manufacturing technologies, as well as reduce waste from scrap. The control of parts with dependent location tolerances is carried out, as a rule, using complex through gauges.

The dependent tolerance of the shape or location is indicated in the drawing by the sign, which is placed according to GOST 2.308-2011:

• - after the numerical value of the tolerance (Fig. 2.17, a), if the dependent tolerance is related to the actual dimensions of the element in question;
• - after letter designation base or without a letter designation in the third field of the frame (see Fig. 2.17, b) if the dependent tolerance is related to the actual dimensions of the base element;
• - after the numerical value of the tolerance and the letter designation of the base (see Fig. 2.17, G) or without a letter designation (see.

rice. 2.17 in), if the dependent tolerance is related to the actual dimensions of the element under consideration and the base element.

On January 1, 2011, GOST R 53090-2008 (ISO 2692:2006) was put into effect. This GOST partially duplicates GOST R 50056-92, which has been in force since 01.01.1994, in terms of standardization and indication on the drawings of maximum material reguirement (MMR) requirements in cases where it is necessary to ensure the assembly of parts in joints with a guaranteed clearance. Minimum material requirements (LMR - least material reguirement), due to the need to limit minimum thickness walls of parts that were not presented earlier.

The MMR and LMR requirements allow you to combine the constraints imposed by dimensional tolerance and geometric tolerance into one complex requirement that more closely matches the intended purpose of the parts. This complex requirement allows, without prejudice to the performance of the part of its functions, to increase the geometric tolerance of the normalized (considered) element of the part, if the actual size of the element does not reach the limit value determined by the established size tolerance.

The maximum material requirement (as well as the dependent tolerance according to GOST R 50056-92) is indicated in the drawings by a sign, and the minimum material requirement is indicated by a sign (L), placed in a frame to indicate the geometric tolerance of the normalized element after numerical value this tolerance and/or base designation.

Calculation of geometric tolerance values T m providing the requirement for the maximum material, can be performed similarly to the calculation of dependent tolerances (see formulas 2.10-2.15).

Denoting similarly dependent tolerances T m geometric tolerances, to which the minimum material requirements are presented - T L , can be written:

where T m in - the minimum value of the geometric tolerance specified

on the drawing, mm;

Tdop - permissible excess of the minimum value of the geometric tolerance, mm.

The values ​​of T add are determined as follows:

for shaft

For hole

d min , a hole Dmax, then

If the shaft has a valid size d max , and hole Z) min , then

for shaft

For hole

In this case, the geometric tolerance has a maximum value:

for shaft

For hole

If the geometric tolerance is associated with the actual dimensions of the normalized and basic elements, then the value of Гadd is found from the dependence (2.15).

Examples of applying the maximum material requirements are examples of assigning dependent tolerances according to GOST R 50056-92 in fig. 2.17. An example of applying the minimum material requirement is shown in fig. 2.18, a.

Both maximum material requirements and minimum material requirements can be supplemented by an interaction requirement (RPR - reciprocity requirement), which allows increasing the size tolerance of a part element if the actual geometric deviation (deviation in shape, orientation or location) of the normalized element does not fully use the restrictions imposed by the requirements MMR or LMR. Example of application of minimum material requirements and the interaction of tolerance size 05 O_ o,oz9 and concentricity tolerance is shown in fig. 2.18, b, and an example of applying the requirement of the maximum material and the interaction of the size 16_o, c and the perpendicularity tolerance is in fig. 2.18, in.

Example 2.2. A dependent hole alignment tolerance 016 +OD8 relative to the outer surface 04O_o.25 of the bushing shown in fig. 2.19.

It can be seen from the symbol that the alignment tolerance depends on the actual size of the element whose axis is the base axis, i.e. surface 04O_ o 25.

Rice. 2.18.a- minimum material; b - minimum material and interaction; in- maximum material and interaction

Rice. 2.19.

The minimum value of the alignment tolerance indicated on the drawing (7pcs = 0.1 mm) corresponds to the limit of the maximum material of the outer surface, in this case, the size d a = d max = 40 mm, i.e. at d a = d max = 40 mm

If the outer surface will have a valid size d a = d min , alignment tolerance can be increased:

Intermediate sizes d a and their corresponding tolerance values T m are given in table. 2.9, and in fig. 2.20 shows a graph of the dependence of the alignment tolerance on the actual size of the outer surface of the sleeve.

Rice. 2.20.

Dependent alignment tolerance values, mm(see fig. 2.20)

dependent tolerance- tolerance of the location of surfaces, the numerical value of which may vary depending on the actual dimensions of the element under consideration and / or the base element. The dependent tolerance designation includes a location tolerance symbol, an indication of the radius or diametric representation of the tolerance, the value of the constant part of the tolerance, an indication that the tolerance is dependent (letter M in a circle). If the letter M in a circle is after the tolerance value, the tolerance depends on the actual dimensions of the element in question. If the letter M in a circle is after the designation of the base, the tolerance depends on the actual dimensions of the base element. If the letter M in a circle is after the tolerance value and the same designation is after the designation of the base, the tolerance depends on the actual dimensions of the element under consideration and the base element.

The assignment of a dependent tolerance means that the normalized deviation may go beyond the tolerance field, limited by the constant part of the tolerance, if such a deviation is compensated by the difference in the actual dimensions of the considered and / or base elements from the limit of the maximum material (for example, an increase in the diameter of the hole or a decrease in the diameter of the shaft). On fig. 3.20 shows how the dependent positional tolerances of the axes of two holes in the board relative to the base plane A are set. The tolerances are dependent, depending on the actual dimensions of the elements under consideration, the constant part of the tolerance is given in radius expression and is equal to 10 microns. However, the axes of the holes of a suitable part can be displaced from the nominal position by more than 10 microns, if such a displacement is compensated by an increase in the hole up to its largest limit size.

In this case, the suitability conclusion is given taking into account the actual size of the hole, since the displacement of its axis from the nominal location cannot be more than the increment of the actual size compared to the smallest limit size.

Rice. 3.20. Rationing of dependent positional tolerances

An illustration showing the possibility of assembling mating parts when the axis of the left hole of the board is offset from the nominal location is shown in fig. 3.21. The hole and pin axes can be offset by half the hole diameter increment without compromising the assembly.

It is clear from the example that dependent tolerances are intended to increase the yield of good parts by increasing the assembly of parts, the actual dimensions of which are shifted towards the minimum material of the part.

It is also clear that in order to conclude on suitability in this case, it is necessary to measure the location of the axes of the holes and their diameters, and then calculate the value of the compensated displacement of the axes, and only after that it is possible to give a correct conclusion on suitability.

In large-scale and mass production, a comprehensive control of the working through gauge gives an unambiguous answer to the question of the assembly of parts. To conclude on the suitability, it will also be necessary to additionally control the size of the holes with non-going gauges.

Rice. 3.21. Hole axis offset compensation by magnification

actual hole size

The “protruding tolerance field” is normalized for an element of limited length, assigning it to the continuation of an adjacent element, which is not an element of the part, but is important for the operation of the assembly assembly. For example, a hole in the tripod plate (Fig. 3.22) should be perpendicular to its base, and since a column is pressed into it, it is desirable to assign a perpendicularity tolerance on the working length of the tripod column.

Rice. 3.22. Normalization of the protruding perpendicularity tolerance

So I look at more or less accessible CAD systems such as Kompas, T-Flex, SolidWorks, SolidEdge and, at worst, Inventor and do not find the elementary functionality needed by foundry equipment designers, at least for casting metals, not plastics. Well, that's where in these programs there are such elementary features as: 1. The ability to display transition lines conditionally in the drawing in accordance with clause 9.5 of GOST 2.305-2008 "ESKD. Images - views, sections, sections."
2. The ability to draw up drawings and transfer data to the specification for parts obtained from blanks in accordance with clause 1.3 "Drawings of products with additional processing or alteration" in accordance with GOST 2.109-73 ESKD. "Basic requirements for drawings". In SW, this is implemented using SWPlus macros, but how is it in other programs?
3. Possibility to automatically obtain views and cuts in the casting drawing with thin lines of machined surfaces of the part in accordance with clause 3 of GOST 3.1125-88 - "ESTD. Rules graphic execution parts of molds and castings." In SW2020, this is half implemented using the alternative position view (in views you can show these thin lines, in cuts you can not). How about this in other programs?
4. The ability to set the size of the radius to an inclined twist, that is, to an ellipse, which are present all the time on parts with slopes (castings, forgings). I know that in SW it can be done. How about this in other programs?
5. The ability to specify on the 3D model a part made of metal, obtained by casting with subsequent machining and on 3D models of the casting, the accuracy of the casting according to GOST R 53464-2009 - "Castings from metals and alloys. Dimensional tolerances, weights and allowances for machining". And, accordingly, automatically obtain tolerances for the dimensions of cast surfaces. This is not in any program. Do developers dislike casters or something?

In addition, it would be nice to know the difference between an array in a solid and other cads. In the same tflex, an array is quickly created and slows down less, but only there the array is a single object. Hide/suppress one of the array components or select a different configuration for it will not work, as in the solid. And since tflexers hang out in the solid branch, I’ll cry to them, maybe they’ll tell me what. I need to save drawings in dxf. And tflex, as it turned out, does not convert drawings to a 1: 1 scale before exporting and makes polylines or segments with arcs from splines. With splines, as I understand it, everything is unambiguous, but with scale? Do not suggest scaling in autocad, the age is not the same) Regarding working with arrays, you can read (in English) - https://forum.solidworks.com/thread/201949 What is in a free and abbreviated translation) means - in most cases it is better to do multiple arrays instead of one.

It is necessary to make 73.2 thousand small studs of two different sizes: 37 mm and 32 mm at a price of 10 rubles per piece from your material. Material AISI 431 or 14X17n2
A productivity of 2-8 thousand studs per week is required. PULSAR23_Contact_screws_23.07.19.rar P23_Contact_screw_37_(2 sheets)_23.07.19.pdf P23_Contact_screw_32_(2 sheets).pdf

Here, the cloud has been uploaded to the mail https://cloud.mail.ru/public/heic/ZRvyFHBXn I will try to do this, it’s already interesting the reason why this assembly is not combined into one of the 3, but 2 thirds easily grew together, only the last one I can’t insert ... or rather, I can insert, splicing the last one does not work

Decree State Committee USSR according to the standards of January 4, 1979 No. 31, the introduction period is set

from 01.01.80

This standard establishes rules for specifying the tolerances of the shape and location of surfaces on the drawings of products in all industries.

Terms and definitions of tolerances for the shape and location of surfaces - according to GOST 24642-81.

Numerical values ​​​​of tolerances of the shape and location of surfaces - according to GOST 24643-81.

The standard fully complies with ST SEV 368-76.

1. GENERAL REQUIREMENTS

1.1. Tolerances of the shape and location of surfaces are indicated in the drawings by symbols.

The type of tolerance of the shape and location of the surfaces must be indicated on the drawing with the signs (graphic symbols) given in the table.

Tolerance group	Tolerance type	Sign
Shape tolerance	Straightness tolerance
	Flatness tolerance
	roundness tolerance
	Cylindrical tolerance
	Longitudinal section profile tolerance
Location tolerance	Parallelism tolerance
	Perpendicularity tolerance
	Tilt tolerance
	Alignment tolerance
	Symmetry tolerance
	Position tolerance
	Intersection tolerance, axes
Total shape and location tolerances	Radial runout tolerance Runout tolerance Runout tolerance in a given direction
	Total radial runout tolerance Full axial runout tolerance
	Tolerance of the shape of a given profile
	Tolerance of the shape of a given surface

The shapes and sizes of signs are given in the mandatory appendix.

Examples of indicating the tolerances of the shape and location of surfaces in the drawings are given in the reference appendix.

Note . The total tolerances of the shape and location of surfaces for which separate graphic signs are not established are indicated by signs of composite tolerances in the following sequence: location tolerance sign, form tolerance sign.

For example:

The sign of the total tolerance of parallelism and flatness;

The sign of the total tolerance of perpendicularity and flatness;

The sign of the total tolerance of inclination and flatness.

1.2. The tolerance of the shape and location of surfaces may be indicated in the text in the technical requirements, as a rule, if there is no sign of the type of tolerance.

1.3. When specifying the tolerance of the shape and location of surfaces in the technical requirements, the text should contain:

type of admission;

an indication of the surface or other element for which the tolerance is set (for this, a letter designation or constructive name is used that defines the surface);

numerical tolerance value in millimeters;

an indication of the bases relative to which the tolerance is set (for location tolerances and total shape and location tolerances);

an indication of dependent tolerances of form or location (if applicable).

1.4. If it is necessary to normalize the shape and location tolerances that are not indicated in the drawing by numerical values ​​​​and are not limited by other shape and location tolerances indicated in the drawing, the technical requirements of the drawing should contain a general record of the unspecified shape and location tolerances with reference to GOST 25069-81 or others. documents establishing unspecified shape and location tolerances.

For example: 1. Unspecified shape and location tolerances - according to GOST 25069-81.

2. Unspecified tolerances of alignment and symmetry - according to GOST 25069-81.

(Introduced additionally, Rev. No. 1).

2. APPLICATION OF TOLERANCES

2.1. With a symbol, data on the tolerances of the shape and location of surfaces are indicated in a rectangular frame divided into two or more parts (Fig.,), in which are placed:

in the first - a tolerance sign according to the table;

in the second - the numerical value of the tolerance in millimeters;

in the third and subsequent - the letter designation of the base (bases) or the letter designation of the surface with which the location tolerance is associated (clauses;).

Heck. eleven

2.9. Before numerical value permission should be:

symbol Æ if the circular or cylindrical tolerance field is indicated by the diameter (Fig. a);

symbol R, if a circular or cylindrical tolerance field is indicated by a radius (Fig. b);

symbol T, if the tolerances of symmetry, intersection of axes, the shape of a given profile and a given surface, as well as positional tolerances (for the case when the positional tolerance field is limited by two parallel lines or planes) are indicated in diametrical terms (Fig. in);

symbol T/2 for the same types of tolerances, if they are indicated in radius expression (Fig. G);

the word "sphere" and symbolsÆ or Rif the tolerance field is spherical (Fig. d).

Heck. 12

2.10. The numerical value of the tolerance of the shape and location of the surfaces indicated in the box (Fig. a), refers to the entire length of the surface. If the tolerance refers to any part of the surface of a given length (or area), then the given length (or area) is indicated next to the tolerance and separated from it by an inclined line (Fig. b, in), which must not touch the frame.

If it is necessary to assign a tolerance over the entire length of the surface and at a given length, then the tolerance at a given length is indicated under the tolerance over the entire length (Fig. G).

Heck. thirteen

(Revised edition, Rev. No. 1).

2.11. If the tolerance must refer to a section located in a certain place of the element, then this section is indicated by a dash-dotted line and is limited in size according to the features. .

Heck. fourteen

2.12. If it is necessary to set a protruding location tolerance field, then after the numerical value of the tolerance indicate the symbol

The contour of the protruding part of the normalized element is limited by a thin solid line, and the length and location of the protruding tolerance field are limited by dimensions (Fig.).

Heck. fifteen

2.13. Inscriptions supplementing the data given in the tolerance frame should be applied above the frame below it or as shown in Fig. .

Heck. sixteen

(Revised edition, Rev. No. 1).

2.14. If for one element it is necessary to set two different types of tolerance, then it is allowed to combine the frames and arrange them according to the features. (upper symbol).

If for the surface it is required to indicate simultaneously the symbol of the tolerance of the shape or location and its letter designation used to normalize another tolerance, then the frames with both symbols can be placed side by side on the connecting line (Fig. , lower designation).

2.15. Repeating the same or different types tolerances, denoted by the same sign, having the same numerical values ​​\u200b\u200band referring to the same bases, it is allowed to indicate once in the frame from which one departs connecting line, which then branches to all normalized elements (Fig. ).

Heck. 17

Heck. eighteen

2.16. The tolerances of the shape and location of symmetrically located elements on symmetrical parts are indicated once.

3. DESIGNATION OF BASES

3.1. The bases are indicated by a blackened triangle, which is connected with a connecting line to the frame. When making drawings with the help of computer output devices, the triangle denoting the base is allowed not to be blackened.

The triangle denoting the base must be equilateral, with a height approximately equal to the font size of the dimension numbers.

3.2. If the base is a surface or its profile, then the base of the triangle is placed on the contour line of the surface (Fig. a) or on its continuation (Fig. b). In this case, the connecting line should not be a continuation of the dimension line.

Heck. nineteen

3.3. If the base is an axis or a plane of symmetry, then the triangle is placed at the end of the dimension line (Fig.).

In case of lack of space, the arrow of the dimension line can be replaced with a triangle denoting the base (Fig.).

Heck. 20

If the base is a common axis (Fig. a) or a plane of symmetry (Fig. b) and it is clear from the drawing for which surfaces the axis (plane of symmetry) is common, then the triangle is placed on the axis.

Heck. 21

(Revised edition, Rev. No. 1).

3.4. If the base is the axis of the center holes, then next to the designation of the base axis, the inscription "Axis of centers" is made (Fig.).

It is allowed to designate the base axis of the center holes in accordance with Fig. .

Heck. 22

Heck. 23

3.5. If the base is a certain part of the element, then it is indicated by a dash-dotted line and limited in size in accordance with the features. .

If the base is a certain place of the element, then it must be determined by the dimensions according to the features. .

Heck. 24

Heck. 25

3.6. If there is no need to single out one of the surfaces as a base, then the triangle is replaced by an arrow (Fig. b).

3.7. If the connection of the frame with the base or other surface to which the location deviation relates is difficult, the surface is indicated by a capital letter that fits into the third part of the frame. The same letter is inscribed in a frame, which is connected to the designated surface by a line, instilled with a triangle, if the base is designated (Fig. a ), or an arrow if the indicated surface is not a base (Fig. b ). In this case, the letter should be placed parallel to the main inscription.

Heck. 26

Heck. 27

3.8. If the size of an element has already been specified once, then it is not indicated on other dimension lines of this element used to symbolize the base. Dimension line without dimension should be considered as constituent part base designation (damn.).

Heck. 28

3.9. If two or more elements form a combined base and their sequence does not matter (for example, they have a common axis or plane of symmetry), then each element is designated independently and all letters are entered in a row in the third part of the frame (Fig. , ).

3.10. If it is necessary to set the location tolerance relative to the set of bases, then the letter designations of the bases are indicated in independent parts(third and beyond) frame. In this case, the bases are written in descending order of the number of degrees of freedom they deprive (hell).

Heck. 29

Heck. thirty

4. INDICATION OF NOMINAL LOCATION

4.1. The linear and angular dimensions that determine the nominal location and (or) the nominal shape of the elements limited by the tolerance, when assigning a positional tolerance, tilt tolerance, tolerance of the shape of a given surface or a given profile, are indicated on the drawings without limiting deviations and are enclosed in rectangular frames (Fig.) .

Heck. 31

5. DESIGNATION OF DEPENDENT TOLERANCES

5.1. Dependent shape and location tolerances denote symbol which is placed:

after the numerical value of the tolerance, if the dependent tolerance is associated with the actual dimensions of the element in question (Fig. a);

after the letter designation of the base (Fig. b) or without a letter designation in the third part of the frame (Fig. G), if the dependent tolerance is related to the actual dimensions of the base element;

after the numerical value of the tolerance and the letter designation of the base (Fig. in) or without a letter designation (Fig. d), if the dependent tolerance is related to the actual dimensions of the element under consideration and the base element.

5.2. If a location or shape tolerance is not specified as dependent, then it is considered independent.

Heck. 32

APPENDIX 2
Reference

EXAMPLES OF INSTRUCTIONS ON THE DRAWINGS OF TOLERANCES FOR THE FORM AND LOCATION OF SURFACES

Tolerance type	Indication of shape and location tolerances by symbol	Explanation
1. Straightness tolerance		The straightness tolerance of the generatrix of the cone is 0.01 mm.
		Hole axis straightness toleranceÆ 0.08 mm (tolerance dependent).
		The surface straightness tolerance is 0.25 mm over the entire length and 0.1 mm over a length of 100 mm.
		Surface straightness tolerance in the transverse direction 0.06 mm, in the longitudinal direction 0.1 mm.
2. Flatness tolerance		Surface flatness tolerance 0.1 mm.
		Surface flatness tolerance 0.1 mm on area 100´ 100 mm.
		The flatness tolerance of the surfaces relative to the common adjacent plane is 0.1 mm.
		The flatness tolerance of each surface is 0.01 mm.
3. Roundness tolerance		Shaft roundness tolerance 0.02 mm.
		Cone roundness tolerance 0.02 mm.
4. Cylindrical tolerance		Shaft cylindricity tolerance 0.04 mm.
		Shaft cylindricity tolerance 0.01 mm over a length of 50 mm. Shaft roundness tolerance 0.004 mm.
5. Tolerance of the profile of the longitudinal section		Shaft roundness tolerance 0.01 mm. The tolerance of the profile of the longitudinal section of the shaft is 0.016 mm.
		The tolerance of the profile of the longitudinal section of the shaft is 0.1 mm.
6. Parallelism tolerance		Tolerance of surface parallelism with respect to surface BUT 0.02 mm.
		Tolerance of parallelism of the common adjacent plane of surfaces relative to the surface BUT 0.1 mm.
		Tolerance of parallelism of each surface relative to the surface BUT 0.1 mm.
		The tolerance of parallelism of the axis of the hole relative to the base is 0.05 mm.
		The tolerance of parallelism of the axes of the holes in the common plane is 0.1 mm. Tolerance of misalignment of the axes of the holes is 0.2 mm. Base - hole axis BUT.
		Tolerance of parallelism of the hole axis with respect to the hole axis BUT 00.2 mm.
7. Perpendicular tolerance		Surface Perpendicularity Tolerance BUT 0.02 mm.
		Tolerance of perpendicularity of the hole axis relative to the hole axis BUT 0.06 mm.
		Perpendicularity tolerance of the protrusion axis relative to the surface BUT Æ 0.02 mm.
		Tolerance of perpendicularity of the OSB of the protrusion relative to the base 0, l mm.
		Tolerance of perpendicularity of the projection axis in the transverse direction 0.2 mm, in the longitudinal direction 0.1 mm. Base - base
		Perpendicular tolerance of the hole axis relative to the surfaceÆ 0.1 mm (tolerance dependent).
8. Tilt tolerance		Tolerance of slope of the surface relative to the surface BUT 0.08 mm.
		Tolerance of inclination of the hole axis relative to the surface BUT 0.08 mm.
9. Alignment tolerance		Hole Alignment ToleranceÆ 0.08 mm.
		Alignment tolerance of two holes relative to them common axis Æ 0.01 mm (tolerance dependent).
10. Symmetry tolerance		Groove symmetry tolerance T 0.05 mm. Base - plane of symmetry of surfaces BUT
		Hole symmetry tolerance T 0.05 mm (tolerance dependent). Base - the plane of symmetry of the surface A.
		Tolerance of symmetry of the OSB hole relative to the common plane of symmetry of the grooves AB T 0.2 mm and relative to the common plane of symmetry of the grooves VG T 0.1 mm.
11. Position tolerance		Positional tolerance of the hole axisÆ 9.06 mm.
		Positional tolerance of hole axesÆ 0.2 mm (tolerance dependent).
		Positional tolerance of the axes of 4 holesÆ 0.1 mm (tolerance dependent). Base - hole axis BUT(tolerance dependent).
		Positional tolerance of 4 holesÆ 0.1 mm (tolerance dependent).
		Positional tolerance 3 threaded holes Æ 0.1 mm (tolerance dependent) in the area located outside the part and protruding 30 mm from the surface.
12. Tolerance of intersection of axes		Hole intersection tolerance T 0.06mm
13. Radial runout tolerance		Tolerance of radial runout of the shaft relative to the axis of the cone 0.01 mm.
		The tolerance of the radial runout of the surface relative to the common axis of the surface BUT and B 0.1 mm
		Tolerance of radial runout of a surface area relative to the axis of the hole BUT 0.2 mm
		Hole run-out tolerance 0.01 mm First base - surface L. The second base is the axis of the surface B. End runout tolerance relative to the same bases is 0.016 mm.
14. Axial runout tolerance		End runout tolerance at a diameter of 20 mm relative to the surface axis BUT 0.1 mm
15. Runout tolerance in a given direction		Cone run-out tolerance relative to the hole axis BUT in the direction perpendicular to the generatrix of the cone 0.01 mm.
16. Tolerance of full radial runout		Tolerance of total radial runout relative to a common axis is superficial BUT and B 0.1 mm.
17. Full axial runout tolerance		Tolerance of full face runout of the surface relative to the axis of the surface is 0.1 mm.
18. Tolerance of the shape of a given profile		Tolerance of the shape of a given profile T 0.04 mm.
19. Tolerance of the shape of a given surface		Tolerance of the shape of a given surface relative to surfaces A, B, C, T 0.1 mm.
20. Total parallelism and flatness tolerance		The total tolerance of parallelism and flatness of the surface relative to the base is 0.1 mm.
21. Total tolerance of perpendicularity and flatness		The total tolerance of perpendicularity and flatness of the surface relative to the base is 0.02 mm.
22. Total tilt and flatness tolerance		The total tolerance of the slope and flatness of the surface relative to the base is 0.05 mi

Notes:

1. In the examples given, the tolerances of alignment, symmetry, positional, intersection of axes, the shape of a given profile and a given surface are indicated in diametric terms.

It is allowed to specify them in a radius expression, for example:

In the previously issued documentation, the tolerances for alignment, symmetry, displacement of the axes from the nominal location (positional tolerance), indicated respectively by signs or text in the specification should be understood as tolerances in radius terms.

2. An indication of the tolerances of the shape and location of surfaces in text documents or in the technical requirements of the drawing should be given by analogy with the text explanation for symbols tolerances of shape and location given in this annex.

In this case, the surfaces to which the tolerances of the shape and location belong, or which are taken as the base, should be indicated by letters or their design names should be carried out.

It is allowed to indicate the sign instead of the words "tolerance dependent"and instead of indications before the numerical value of the charactersÆ ; R; T; T/2writing in text, for example, "0.1 mm axis position tolerance in diametric terms" or "0.12 mm symmetry tolerance in radial terms".

3. In the newly developed documentation, the entry in the technical requirements for tolerances of ovality, cone shape, barrel shape and saddle shape should be, for example, the following: “Tolerance of ovality of the surface BUT 0.2 mm (semi-difference in diameter).

In the technical documentation developed before 01/01/80, the limiting values ​​​​of ovality, cone shape, barrel shape and saddle shape are defined as the difference between the largest and smallest diameters.

(Revised edition, Rev. No. 1).

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BASIC REGULATIONS OF INTERCHANGEABILITY

DEPENDENT SHAPE TOLERANCES,
LOCATIONS AND COORDINATING DIMENSIONS

GENERAL APPLICATIONS

GOSSTANDART OF RUSSIA
Moscow

STATE STANDARD OF THE RUSSIAN FEDERATION

Date of introduction 01.01.94

This standard applies to dependent tolerances of the shape, location and coordinating dimensions of parts of machines and devices and establishes the basic provisions for their application.

The requirements of this standard are mandatory.

1. GENERAL PROVISIONS

1.1. Terms and definitions related to deviations and tolerances of dimensions, shape and location of surfaces, incl. to dependent tolerances of shape and location, - according to GOST 25346 and GOST 24642.

Indications on the drawings of dependent tolerances of the shape and location of surfaces - according to GOST 2.308, coordinating dimensions - according to GOST 2.307.

1.1.10. Symmetry surface of real flat elements - the locus of the midpoints of the local dimensions of an element bounded by nominally parallel planes.

1.1.11. Coordinating size- size that determines the location of the element in the selected coordinate system or relative to another element (elements).

1.2. Dependent tolerances are assigned only for elements (their axes or planes of symmetry) that are holes or shafts in accordance with the definitions in accordance with GOST 25346.

1.3. Dependent tolerances are assigned, as a rule, when it is necessary to ensure the assembly of parts with a gap between mating elements.

Notes:

1. Free (without interference) assembly of parts depends on the combined effect of the actual dimensions and actual deviations in the location (or shape) of the mating elements. The tolerances of the form or location indicated on the drawings are calculated from the minimum gaps in the landings, i.e. provided that the dimensions of the elements are made at the limit of the maximum material. The deviation of the actual size of the element from the limit of the maximum material leads to an increase in the gap in the connection of this element with a paired part. With an increase in the gap, the corresponding additional deviation in shape or location, permitted by the dependent tolerance, will not lead to a violation of the assembly conditions. Examples of assigning dependent tolerances: positional tolerances of the axes of smooth holes in flanges through which the bolts fastening them pass; alignment tolerances of stepped shafts and bushings connected to each other with a gap; tolerances of perpendicularity to the reference plane of the axes of smooth holes, which should include glasses, plugs or covers.

2. The calculation of the minimum values ​​​​of dependent tolerances of shape and location, determined by design requirements, is not considered in this standard. With regard to the positional tolerances of the axes of holes for fasteners, the calculation method is given in GOST 14140.

3. Examples of assigning dependent tolerances of shape, location, coordinating dimensions and their interpretation are given in Appendix 1, technological advantages of dependent tolerances - in Appendix 2.

1.4. Dependent tolerances of shape, location and coordinating dimensions ensure the assembly of parts according to the method of complete interchangeability without any selection of paired parts, since an additional deviation in the shape, location or coordinating dimensions of an element (or elements) is compensated by deviations in the actual dimensions of the elements of the same part.

1.5. If, in addition to the assembly of parts, it is necessary to ensure other requirements for parts, for example, strength or appearance, then when assigning dependent tolerances, it is necessary to check the fulfillment of these requirements at the maximum values ​​of dependent tolerances.

1.6. Dependent tolerances of shape, location or coordinating dimensions, as a rule, should not be assigned in cases where deviations in shape or location affect the assembly or functioning of parts, regardless of the actual deviations in the dimensions of the elements and cannot be compensated for by them. Examples are the location tolerances of parts or elements that form interference or transitional fits that provide kinematic accuracy, balance, tightness or tightness, incl. tolerances for the location of the axes of the holes for the gear shafts, seats for rolling bearings, threaded holes for studs and heavy-duty screws.

1.7. Notation

The following designations are used in this standard:

d, d 1 , d 2 - nominal size of the considered element;

d a- local size of the considered element;

d a max, d a min- maximum and minimum local dimensions of the element under consideration;

d LMc- the limit of the minimum material of the considered element;

d LMco- the limit of the minimum base material;

d mms- the maximum limit of the material of the element under consideration;

d mms o- maximum limit of the base material;

dp- size by conjugation of the element under consideration;

dpo- size by pairing the base;

d υ- the limiting effective size of the element under consideration;

L - nominal coordinating size;

RTP Ma, RTP M max , RTP M min- respectively, the actual, maximum and minimum values ​​of the dependent tolerances of alignment, symmetry, intersection of the axes and positional in radius expression;

T a, T d 1, T d 2- size tolerance of the considered element;

Td0- base size tolerance;

T ma- a generalized designation of the actual value of the dependent tolerance of the shape, location or coordinating size;

t M max , T M min- a generalized designation, respectively, of the maximum and minimum values ​​​​of the dependent tolerance of the shape, location: or coordinating size;

TF ma,TF Mmax,TF M min- respectively, the actual, maximum and minimum values ​​​​of the dependent shape tolerance;

TFz- permissible excess of the minimum value of the dependent shape tolerance;

TL m a, TL M max , TL M min- respectively, the actual, maximum and minimum values ​​​​of the dependent tolerance of the coordinating size;

TLz- permissible excess of the minimum value of the dependent tolerance of the coordinating size;

TP ma, TP M max , TP M min- respectively, the actual, maximum and minimum values ​​of the dependent tolerance of the location of the element in question;

TP mao (TP zo),TR mtaho- respectively, the actual (equal to the allowable excess of the dependent tolerance of the location of the base element) and the maximum value of the dependent tolerance of the location of the base;

TR ma- the actual value of the dependent location tolerance, depending on the deviations in the dimensions of the element in question and the base;

TPz- permissible excess of the minimum value of the dependent location tolerance due to the deviation of the size of the element in question.

2. DEPENDENT SHAPE TOLERANCES

2.1. The following form tolerances can be assigned dependent:

Tolerance of straightness of the axis of the cylindrical surface;

Flatness tolerance of the symmetry surface of flat elements.

2.2. With dependent shape tolerances, the limit dimensions of the element under consideration limit only any local dimensions of the element. The size by conjugation on the length of the normalized section, to which the shape tolerance belongs, may go out of the size tolerance field and is limited by the limiting effective size.

2.3. The permissible excess of the minimum value of the dependent shape tolerance is determined depending on the local size of the element.

2.4. The formulas for calculating the permissible excess of the minimum value of the dependent shape tolerance, as well as the actual and maximum values ​​​​of the dependent shape tolerance and the maximum effective size are given in table. one.

Table 1

Calculation formulas for dependent shape tolerances

Determined value
	for shafts	for holes
	d MMC - d a	d a - d MMC
TR Ma	TF M min + TF z	TF M min + TF z
TF M max	TF M min + T d	TF M min + T d
	d MMC + TF Mmin	d MMC - TF M min

Note. Formulas for TFz and TR ma, given in table. 1 correspond to the condition when all local dimensions of the element are the same, and there are no deviations from roundness for cylindrical elements. If these conditions are not met, the values TFz and TR ma can only be estimated approximately (for example, if in formulas instead of d a substitute values d a max for shafts or d a min for holes). The critical condition is that the real surface does not go beyond the current limiting contour, the size of which is equal to d υ .

3. DEPENDENT LOCATION TOLERANCES

3.1. The following location tolerances can be assigned as dependents:

Tolerance of perpendicularity of the axis (or plane of symmetry) relative to the plane or axis;

Tilt tolerance of the axis (or plane - symmetry) relative to the plane or axis;

Alignment tolerance;

Symmetry tolerance;

Axes intersection tolerance;

Positional tolerance of an axis or plane of symmetry.

3.2. With dependent location tolerances limit deviations the size of the element in question and the base are interpreted in accordance with GOST 25346.

3.3. The allowable excess of the minimum value of the dependent location tolerance is determined depending on the deviation of the size of the conjugation of the element and / or base in question from the corresponding limit of the maximum material.

Depending on the requirements for the part and the way the dependent tolerance is indicated on the drawing, the dependent tolerance condition can be extended:

On the element under consideration and the base at the same time, when the expansion of the location tolerance is possible both due to size deviations along the conjugation of the element under consideration, and due to size deviations along the base conjugation;

Only on the element under consideration, when the extension of the location tolerance is possible only due to the deviation of the size along the conjugation of the element under consideration;

Only to the base, when the expansion of the location tolerance is possible only due to the deviation of the size along the base mate.

3.4. Table 2 and 3.

3.5. If dependent tolerances are set on mutual arrangement two or more elements under consideration, then the values ​​\u200b\u200bspecified in Table. 2 and 3 are calculated for each element under consideration separately according to the dimensions and tolerances of the corresponding element.

table 2

Calculation formulas for dependent location tolerances in diametric terms (exceeding the minimum value of the dependent tolerance due to deviations in the size of the element in question)

Determined value
	for shafts	for holes
	dMMC-dp	d p ​​- d MMC
TR Ma	TP M min + TP z	TP M min + TP z
TF M max	TP M min + T d	TP M min + T d
	d MMC + TP Mmin	d MMC - TP M min

Table 3

Calculation formulas for dependent location tolerances in radius expression (exceeding the minimum value of the dependent tolerance due to deviations in the size of the considered element)

Determined value
	for shafts	for holes
	0,5 (dMMC-dp)	0,5 (d p ​​- d MMC)
RTP Ma	RTP M min + RTP z	RTP M min + RTP z
RTP M max	RTP M min + 0,5 T d	RTP M min + 0,5 T d
	dMMC+ 2 RTP Mmin	dMMC- 2 RTP Mmin

3.6. When the dependent tolerance condition extends to the base, then the deviation (displacement) of the base axis or symmetry plane relative to the considered element (or elements) is additionally allowed. The formulas for calculating the actual and maximum values ​​​​of the dependent tolerance of the location of the base, as well as the maximum effective size of the base, are given in Table. 4.

Table 4

Calculation formulas for dependent tolerances of the location of the base

Determined value
	for shafts	for holes
TR zo = TRmao	dMMCo - dpo	dpo-dMMCo
TP M max o
	Location tolerances in diametric terms
RTP zo = RTP Mao	0,5 (dMMCo-dpo)	0,5 (dpo-dMMCo)
RTP M max o	0,5 T do	0,5 T do
	Maximum effective base size

3.7. If, in relation to this base, a dependent tolerance for the location of one element under consideration is established, then the actual value of this tolerance can be increased by the actual value of the dependent tolerance for the location of the base according to Table. 4, taking into account the lengths and location in the axial direction of the element under consideration and the base (see Appendix 1, example 7).

If relative to this base, dependent tolerances for the location of several elements are set, then the dependent tolerance for the location of the base cannot be used to increase the actual value of the dependent tolerance for the relative position of the elements under consideration (see Appendix 1, example 8).

4. DEPENDENT TOLERANCES OF COORDINATING DIMENSIONS

4.1. The tolerances of the following coordinating dimensions, which determine the location of the axes or planes of symmetry of the elements, can be assigned as dependent ones:

Distance tolerance between the plane and the axis (or plane of symmetry) of the element;

Distance tolerance between the axes (planes of symmetry) of two elements.

4.2. With dependent tolerances of coordinating dimensions, the maximum deviations of the dimensions of the elements under consideration are interpreted in accordance with GOST 25346.

4.3. The allowable excess of the minimum value of the dependent location tolerance is determined depending on the deviation of the size of the pairing of the considered element (or elements) from the corresponding limit of the maximum material.

4.4. The formulas for calculating the permissible excess of the minimum value of the dependent tolerance of the coordinating size, the actual and maximum values ​​of the dependent tolerance of the coordinating size, as well as the limiting effective sizes of the elements under consideration are given in Table. 5.

Table 5

Calculation formulas for dependent tolerances of coordinating dimensions

	Determined value
		for shafts	for holes
	TL Mmax	dMMC-dp TL Mmin + TLz TL Mmin + T d d MMC + TL M min	dMMC-dp TL Mmin + TLz TL Mmin + T d d MMC + TL M min
	TL Mmax d 1υ d 2υ	|d 1MMC -d 1p | + |d 2MMC -d 2p | TL Mmin + TLz TL Mmin + T d 1 + T d 2
		d 1MMC + 0,5 TL Mmin d 2MMC + 0,5 TL Mmin	d 1MMC - 0,1 TL Mmin d 2MMC - 0,5 TL Mmin

5. ZERO DEPENDENT LOCATION TOLERANCES

5.1. Dependent location tolerances can be set to zero. In this case, location deviations are allowed within the element size tolerance field and only on condition that the mating size deviates from the maximum material limit.

5.2. With a dependent position tolerance of zero, the size tolerance is the sum of the element's size and position tolerance. In this case, the limit of the maximum material limits the size of the conjugation and is the limiting effective size of the element, and the limit of the minimum material limits the local dimensions of the element.

In extreme cases, the field of the total tolerance of size and location can be fully used for location deviations, if the size by mating is made at the limit of the minimum material, or for size deviations, if the location deviation is zero.

5.3. The assignment of separate tolerances for the size of an element and the dependent tolerance for its location can be replaced by the assignment of a total tolerance for size and location in combination with a zero dependent location tolerance, if, according to the conditions of assembly and operation of the part, it is permissible that for this element the limit size by mating coincides with the limit effective size determined according to separate size and location tolerances. An equivalent replacement is provided by increasing the size tolerance by shifting the maximum material limit by an amount equal to the minimum value of the dependent location tolerance in diametric terms, while maintaining the minimum material limit, as shown in Fig. 2. Examples of equivalent replacement of separate size and location tolerances are shown in Fig. 3, as well as in Appendix 1 (example 10).

Compared to separate assignment of size and location tolerances, the zero dependent location tolerance allows not only to increase the location deviation due to size deviations from the maximum material limit, but also to increase the size deviation with a corresponding decrease in the location deviation.

Note. Replacing separate tolerances of size and location with a total tolerance of size and location with a zero dependent location tolerance is not allowed for elements that form a fit during assembly, in which there is no guaranteed clearance that compensates for the minimum value of the dependent separate location tolerance, for example, for tolerances for the location of threaded holes in connections type B according to GOST 14143.

5.4. The ratio between deviations in size and location within the total tolerance (with zero dependent location tolerances) is not regulated. If necessary, it can be set in the technological documentation, taking into account the peculiarities of the manufacturing process, by assigning an element-by-element limit of the maximum material for a local size or size by conjugation ( d ′ MMC to hell. 2). Monitoring compliance with this limit during the acceptance control of products is not mandatory.

5.5. Zero dependent location tolerances can be set for all types of location tolerances specified in clause 3.1.

Notes:

1. Zero dependent form tolerance corresponds to the interpretation of the limiting dimensions in accordance with GOST 25346 and is not recommended to be assigned.

2. Instead of zero dependent tolerances of coordinating dimensions, zero dependent positional tolerances should be assigned.

6. CONTROL OF PARTS WITH DEPENDENT TOLERANCES

6.1. Control of parts with dependent tolerances can be carried out in two ways.

6.1.1. Complex method, in which compliance with the principle of maximum material is controlled, for example, using gauges to control the location (shape), instruments for coordinate measurements, in which the limiting active contours are modeled and the combination of measured elements with them; projectors by superimposing the image of real elements on the image of the limiting active contours. Regardless of this check, the dimensions of the element in question and the base are controlled separately.

Note. Gauge tolerances for location control and calculation of their dimensions - according to GOST 16085.

6.1.2. Separate measurement of deviations in the size of the considered element and / or base and deviations of the location (shape or coordinating size), limited by the dependent tolerance, followed by calculation of the actual value of the dependent tolerance and checking the condition that the actual deviation of the location (shape or coordinating size) does not exceed the actual value of the dependent tolerance.

6.2. In case of discrepancies between the results of integrated and separate control of deviations in shape, location or coordinating dimensions, limited by dependent tolerances, the results of integrated control are arbitrated.

APPENDIX 1

Reference

EXAMPLES OF ASSIGNING DEPENDENT TOLERANCES AND THEIR INTERPRETATION

The dependent tolerance of the straightness of the hole axis is set according to Fig. 4a.

The local dimensions of the hole must lie between 12 and 12.27 mm;

The real surface of the hole should not go beyond the limiting active contour - a cylinder with a diameter

d υ = 12 - 0.3 = 11.7 mm.

The actual values ​​of the dependent tolerance of the straightness of the axis at different values the local size of the hole is shown in the table in fig. 4.

In extreme cases:

If all local dimensions of the hole are made equal to the smallest limit size d mms= 12 mm, then the straightness tolerance of the axis will be 0.3 mm (the minimum value of the dependent tolerance, Fig. 4b);

If all values d a holes are made equal to the largest limit size d LMc= 12.27 mm, then the straightness tolerance of the axis will be 0.57 mm (the maximum value of the dependent tolerance, Fig. 4c).

12,00 dMMc

The dependent flatness tolerance of the plate symmetry surface is set according to Fig. 5a.

The part must meet the following requirements:

Thickness anywhere should be between 4.85 and 5.15 mm;

surfaces BUT the plates should not go beyond the limiting active contour - two parallel planes, the distance between which is 5.25 mm.

Actual values ​​of dependent flatness tolerance at different meanings The local thickness of the plate is given in the table in Fig. 5. In extreme cases:

If the thickness of the plate in all places is made equal to the largest limit size d mms= 5.15 mm, then the flatness tolerance of the symmetry surface will be 0.1 mm (the minimum value of the dependent tolerance, Fig. 5b),

If the thickness of the plate in all places is made equal to the smallest limit size d LMc= 4.85 mm, then the flatness tolerance of the symmetry surface will be 0.4 mm (the maximum value of the dependent tolerance, Fig. 5c).

5,15 dMMc
4,85 d LMc

The dependent tolerance of the perpendicularity of the axis of the protrusion relative to the plane is set according to Fig. 6a.

The part must meet the following requirements:

The local diameters of the protrusion should lie between 19.87 and 20 mm, and the diameter of the protrusion at the interface should not exceed 20 mm;

The surface of the protrusion should not go beyond the limiting active contour - a cylinder with an axis perpendicular to the base BUT, and diameter

d υ = 20 + 0.2 = 20.2 mm.

20,00 dMMc
19,87 d LMc

The actual values ​​​​of the dependent tolerance of the perpendicularity of the axis for various values ​​​​of the diameter of the protrusion along the conjugation are given in the table in Fig. 6 and are graphically shown in the diagram (Fig. 6b).

In extreme cases:

If the diameter of the protrusion along the conjugation is made equal to the largest limit size d mms= 20 mm, then the axis perpendicularity tolerance will be 0.2 mm (the minimum value of the dependent tolerance, Fig. 6c);

If the diameter of the protrusion by mating and all local diameters are made equal to the smallest limit size d LMc = 19.87 mm, then the axis perpendicularity tolerance will be 0.33 mm (the maximum value of the dependent tolerance, Fig. 6d).

The tolerance of the inclination of the plane of symmetry of the groove relative to the plane BUT according to hell. 7a.

The part must meet the following requirements:

The local dimensions of the groove must lie between 6.32 and 6.48 mm, and the mating dimension must be at least 6.32 mm;

The side surfaces of the groove should not go beyond the limiting active contour - two parallel planes located at an angle of 45 ° to the base plane BUT and separated from each other at a distance

d υ= 6.32 - 0.1 = 6.22 mm.

The actual values ​​​​of the dependent tolerance of the inclination of the plane of symmetry of the groove, depending on its size along the mating, are given in the table in Fig. 7 and are graphically shown in the diagram (Fig. 7b).

In extreme cases:

If the width of the groove along the mating is equal to the smallest limit size d mms= 6.32 mm, then the tolerance of the inclination of the plane of symmetry of the groove will be 0.1 mm (the minimum value of the dependent tolerance, Fig. 7c);

If the width of the groove at the interface and all local dimensions of the groove are equal to the largest limit size d LMc\u003d 6.48 mm, then the tolerance for the slope of the symmetry plane will be 0.26 mm (the maximum value of the dependent tolerance, Fig. 7d).

6,32 d mms
6,48 d LMc

The dependent tolerance of the outer surface alignment relative to the base hole is set according to Fig. 8a; the dependent tolerance condition applies only to the element in question.

The part must meet the following requirements:

The local diameters of the outer surface must lie between 39, 75 and 40 mm, and the mating diameter must not exceed 40 mm;

The outer surface should not go beyond the limiting active contour - a cylinder with a diameter of 40.2 mm, coaxial with the base hole.

The actual values ​​​​of the dependent alignment tolerance in diametric terms, depending on the diameter at the interface of the outer surface, are shown in the table in Fig. 8 and shown in the diagram (Fig. 8b).

In extreme cases:

If the diameter at the conjugation of the outer surface is equal to the largest limit size d mms= 40 mm, then the alignment tolerance will be Ø 0.2 mm

(minimum value of the dependent tolerance, Fig. 8c);

If the mating diameter and all local diameters of the outer surface are equal to the smallest limit size d LMc= 39.75 mm, then the alignment tolerance will be Ø 0.45 mm (the maximum value of the dependent tolerance, Fig. 8d).

40,00 d mms
39,75 d LMc

The dependent positional tolerance of the axes of the four holes in relation to each other is set according to Fig. 9a.

The part must meet the following requirements:

The local diameters of all holes must lie between 6.5 and 6.65 mm, and the diameters at the interface of all holes must be at least 6.5 mm

d υ= 6.5 - 0.2 = 6.3 mm,

whose axes occupy a nominal location (in a precise rectangular lattice with a size of 32 mm). The actual values ​​of the positional tolerance in diametric terms for the axis of each hole, depending on the diameter at the interface of the corresponding hole, are given in the table in Fig. 9 and shown in the diagram (Fig. 9b). In extreme cases:

d mms= 6.5 mm, then the positional tolerance of the axis of this hole will be Ø 0.2 mm (the minimum value of the dependent tolerance, Fig. 9b);

d mms= 6.65 mm, then the positional tolerance of the axis of this hole will be Ø 0.35 mm (the maximum value of the dependent tolerance, Fig. 9c).

The scheme of the gauge for controlling the location of the axes of the holes, which implements the limiting active contours, is shown in Fig. 9y.

6,50 d mms
6,65 d LMc

The dependent tolerance of the outer surface of the sleeve relative to the hole is set according to Fig. 10a; the dependent tolerance condition is also set for the base.

The part must meet the following requirements:

The local diameters of the outer surface must lie between 39, 75 and 40 mm, and the mating diameter must not exceed 40 mm;

The local diameters of the base hole must lie between 16 and 16.18 mm, and the mating diameter must be at least 16 mm;

The outer surface should not go beyond the limiting active contour - a cylinder with a diameter

d υ= 40 + 0.2 = 40.2 mm,

whose axis coincides with the axis of the base hole, if its mating diameter is equal to the smallest limit size d mms o = 16 mm. The actual values ​​​​of the dependent alignment tolerance, depending on the size of the interface of the outer surface, are given in the table in Fig. 10 (column 2) and are measured from Ø 0.210 mm (with d mms= 40 mm) up to Ø 0.45 mm (with d LMc= 39.75 mm);

The surface of the base hole should not go beyond the contour of the maximum material - a cylinder with a diameter of 16 mm ( d mms o), coaxial with the limiting active contour of the outer surface. Valid tolerance values tr mao for the displacement of the base axis relative to the axis of the contour of the maximum material, depending on the diameter at the interface of the base hole, are given in the table in Fig. 10 (4th line from the top) and change from 0 (when d mms o= 16 mm) up to Ø 0.18 mm (with d LMco= 16.18 mm).

		Total value TR′ ma = TR ma +T. P. Mao

The total actual value of the dependent tolerance of the coaxiality of the outer surface relative to the hole, depending on the deviations in the size of both the considered element and the base for a given configuration of the part (both elements have the same length and the same location in the axial direction) is equal to

TR′ ma = TR Ma + TR mao

Values TR′ ma at different sizes according to the conjugation of the element in question and the base are given in the table in Fig. 10. In extreme cases:

If the dimensions for conjugation of elements are made according to the limit of the maximum material ( d p ​​= 40 mm, dpo= 16 mm), then TR′ ma =Ø 0.2 mm (minimum dependent tolerance value, Fig. 10b);

If the dimensions by conjugation and all local dimensions of the elements are made to the limit of the minimum material ( dp= 39.75 mm; dpo= 16.18 mm), then TR′ ma =Ø 0.63 mm (maximum value of the dependent tolerance, Fig. 10c).

For other configurations of parts, when the element under consideration and the base are spaced apart in the axial direction, the total actual value of the dependent alignment tolerance depends on the length of the elements, the amount of their spacing in the axial direction, and also on the nature of the misalignment (the relationship between the parallel and angular displacement of the axes).

For example, for the part shown in Fig. 11a, in the case of angular displacement of the axes of the elements (Fig. 11b), the maximum value of the dependent alignment tolerance will be equal to

TR′ max= 2

However, with a parallel displacement of the axes (Fig. 11c), the maximum value of the dependent alignment tolerance will be different:

TR′ max= 2

When the nature of the deviation of the axes is unknown, it is decisive to observe the principle of maximum material, for example, when checking with a gauge shown in Fig. 11y.

A dependent positional tolerance of the axes of four holes is set in relation to each other and relative to the axis of the base hole according to Fig. 12a; the dependent tolerance condition is also set for the base.

5,5 d mms		7,00 d mmco
5,62 d LMco
		7,15 d LMco

The part must meet the following requirements:

The local diameters of the four peripheral holes must lie between 5.5 and 5.62 mm, and the diameters at the interface of these holes must be at least 5.5 mm;

The local diameters of the base hole must lie between 7 and 7.15 mm, and the diameter at the interface must be at least 7 mm;

The surfaces of the peripheral holes should not go beyond the limiting active contours - cylinders with a diameter

d υ = 5.5 - 0.2 = 5.3 mm,

whose axes occupy a nominal location (in a precise rectangular lattice with a size of 32 mm); the central axis of symmetry of the lattice coincides with the axis of the base hole, if its size by conjugation is made according to the smallest limit size ( dmmsabout = 7 mm). Actual values ​​of the dependent positional tolerance of the axis of each considered hole TR ma depending on the diameter at the interface of the corresponding hole are shown in the table in Fig. 12 and vary from Ø 0.2 mm (with dmms = 5.5 mm) up to Ø 0.32 mm (with d LMc= 5.62 mm), hell. 12b, c;

The surface of the base hole should not go beyond the contour of the maximum material - a cylinder with a diameter of 7 mm ( d υ o = dMMCo), the axis of which coincides with the central axis of symmetry of the limiting active contours of the four holes. Actual values ​​of the positional tolerance of the axis of the base hole tr mao depending on the diameter of the pairing of this hole are shown in the table in Fig. 12 and change from 0 (at dmmsabout =7 mm) up to Ø 0.15 mm (with d LMco= 7.15 mm), hell. 12b, c. This positional tolerance cannot be used to expand the positional tolerances of peripheral holes relative to each other.

The scheme of the gauge for controlling the location of the axes of the holes, which implements the limiting active contours of the four peripheral holes and the contour of the maximum material of the base hole, is shown in Fig. 12y.

The dependent tolerance of the distance between the axes of two holes is set according to Fig. 13a.

The part must meet the following requirements:

The local diameters of the left hole must lie between 8 and 8.15 mm, and the mating diameter must be at least 8 mm;

The local diameters of the right hole must lie between 10 and 10.15 mm, and the mating diameter must be at least 10 mm;

The surfaces of the holes should not go beyond the limiting active contours - cylinders with diameters of 7.8 and 9.8 mm, the distance between the axes of which is 50 mm. The actual values ​​\u200b\u200bof the dependent tolerance of the distance between the axes corresponding to this condition, depending on the diameters along the conjugation of both holes, are given in the table in Fig. thirteen.

In extreme cases:

If the diameters at the conjugation of both holes are equal to the smallest limit size d 1mms = 8 mm and d 2mms= 10 mm, then the maximum deviations of the distance between the axes will be ± 0.2 mm (the minimum value of the dependent tolerance, Fig. 13b);

If the mating diameters and all local diameters of both holes are equal to the largest limit size d 1 L ms= 8.15 mm and d 2 L ms = 10.15 mm, then the maximum deviations of the distance between the axes of the holes will be ± 0.35 mm (the maximum value of the dependent tolerance, Fig. 13c).

The scheme of the gauge for controlling the distance between the axes of two holes, which implements the limiting active contours of the holes, is shown in Fig. 13y.

d 1 p	d 2p
	±0.5 T LMa

The zero dependent positional tolerance of the axes of the four holes in relation to each other is set according to Fig. 14a.

AT this example for the part considered in example 6 (Fig. 8), the equivalent replacement of separate size and location tolerances was made for an extended size tolerance with a zero dependent location tolerance.

The part must meet the following requirements:

The local dimensions of all holes must lie between 6.3 and 6.65 mm, and the diameters at the interface of all holes must be at least 6.3 mm;

The surfaces of all holes should not go beyond the limiting active contours - cylinders with a diameter

d υ= 6.3 - 0 = 6.3 mm,

whose axes occupy a nominal location (in a precise rectangular lattice with a size of 32 mm).

The actual values ​​of the positional tolerance in diametric terms for the axis of each hole, depending on the diameter at the interface of the corresponding hole, are given in the table in Fig. 14 and shown in the diagram (Fig. 14b).

In extreme cases:

If the diameter at the interface of this hole is equal to the smallest limit size d mms= 6.3 mm, then the axis of the hole should occupy the nominal location (positional deviation is zero); in this case, the entire field of the total tolerance of the size and location of the element can be used for deviations of the local diameter and deviations - the shape of the hole;

If the diameter at the interface of a given hole and all its local diameters are equal to the largest limit size d LMc= 6.65 mm, then the positional tolerance of the axis of this hole will be Ø 0.35 mm (the maximum value of the dependent tolerance); in this case, the total allowance for the size and position of the element can be used for position deviations.

The scheme of the gauge for controlling the location of the axes of the holes, which implements the limiting active contours, is shown in Fig. 14th century

6,30 d mms
6,65 d LMc

APPENDIX 2

Reference

TECHNOLOGICAL ADVANTAGES OF DEPENDENT TOLERANCES

1. Technological advantages of dependent shape and location tolerances in comparison with independent ones consist primarily in the fact that they allow the use of less accurate, but more economical processing methods and equipment, as well as reduce losses from marriage. If the field of technological dispersion of location deviations exceeds the location tolerance value (independent or dependent), then with dependent location tolerances, the proportion of good parts increases compared to independent tolerances due to:

Parts whose shape and location deviations exceed the minimum value, but do not exceed the actual value of the dependent tolerance;

Details in which the deviations of the shape and location, although they exceed the actual value, do not exceed the maximum value of the dependent tolerance; these parts are reparable defects and can be converted into suitable ones by additional processing of the element for a corresponding change in its size towards the limit of the minimum material, for example, by boring or reaming holes (see example in Fig. 15).

2. If the field of technological dispersion of location deviations is limited, based on the condition that there is practically no correctable or final marriage due to location deviations (i.e., so that its share does not exceed a given risk percentage), then this field will be larger for the dependent location tolerance, according to compared to independent.

Its increase can be determined taking into account the laws of distribution of deviations in size and location, the proportion of risk, the ratio between size and location tolerances. Approximately, to assess the possible field of technological dispersion, it can be taken equal to the actual value of the dependent location tolerance when the actual dimensions of the elements are performed in the middle of the dimensional tolerance field.

3. If the dependent tolerance condition extends to the base, then this makes it possible to simplify the design of the base elements of technological devices, for example, conductors, and gauges, since their base elements can be made not self-centering, but rigid with a constant size corresponding to the maximum limit of the base material. The displacement of the base of the part due to the gap between it and the base element of the fixture or gauge, which occurs when the size of the base deviates from the maximum material limit, in this case is allowed by a dependent location tolerance.

4. With dependent location tolerances, the manufacturer has the opportunity, if necessary, to increase (in the technological documentation) the minimum value of the dependent location tolerance due to a corresponding reduction in the size tolerance field from the side of the maximum material.

5. Dependent tolerances allow you to reasonably use gauges to control the location (shape, coordinating dimensions) according to GOST 16085, evaluating the suitability of the part by entering it. The principle of operation of such calibers is fully consistent with the concept of dependent tolerances.

With independent location tolerances, the use of gauges may not be possible or require a preliminary recalculation of the independent tolerance into a dependent one (mainly in the technological documentation) or the use of a special methodology for calculating the executive dimensions of the gauges.

Independent Location Tolerance

Dependent Location Tolerance

INFORMATION DATA

1 . DEVELOPED AND INTRODUCED by the All-Union Research and Design Institute of Measuring Instruments in Mechanical Engineering

DEVELOPERS

A.V. Vysotsky, cand. tech. sciences; M.A. Paley(topic leader), Ph.D. tech. sciences; L.A. Ryabinin; O.V. Buyanina

2 . APPROVED AND INTRODUCED BY Decree of the State Standard of Russia dated July 28, 1992 No. 794

3 . The term of the first inspection is 2004, the frequency of inspection is 10 years

4 . The standard complies with the international standard ISO 2692-88 in terms of terminology (clauses1.1.1 - 1.1.5 , 1.1.9 ) and examples (examples1 , 3 , 4 , 6 , 7 (heck.11 ), 8 , 10 )

5 . INTRODUCED FOR THE FIRST TIME

6 . REFERENCE REGULATIONS AND TECHNICAL DOCUMENTS

1.1, 1.2, 3.2, 4.2, 5.5

ISO 1101/2-74