DD142461A1 - LIP RING OF ELASTIC MATERIAL AND, PREFERABLY, SYMMETRICAL PROFILE CUT - Google Patents

Abstract

The invention relates to lip rings made of elastic material and preferably symmetrical profile cross-section for installation in Sealing chambers of different nominal diameter but the same, preferably standardized width for sealing of pistons or Piston rods. The lip ring contains a tight fit on the unmoved surface, while on the moving surface only the required Sealing lip contact acts. The aim of the invention is the creation a sealing ring whose structural design such optimal Installation conditions allows for an inaxial functionality is guaranteed for a long service life and at the same time by the dual use as piston or piston rod seal a minimization of the range of seals and thus a Lot size increase is achieved by the manufacturer.

Description

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Lip ring made of elastic material and preferably symmetrical profile section.

Field of application of the invention;

The invention relates to lip rings made of elastic material and preferably symmetrical profile cross-section for installation in sealing chambers of different characteristic diameter but the same, preferably standardized width for sealing of pistons or piston rods .. It receives the lip ring '' a snug fit on the unmoved surface, while on the moving Surface only the required sealing lip contact acts.

Characteristics of the known technical solutions Lip rings are produced depending on their purpose in different profiles and materials or material compositions. '.

From the point of view of the position fixing from three different basic versions are known. 1. Lip rings, each with a sealing lip on the inner and outer circumferential surface, wherein the profile cross section is largely symmetrical. In this type, the sealing lips seal on both the adjacent hubbewegten surface and on the adjacent resting surface by a suitable excess (bias) from. The remaining parts of the lateral surface of the lip ring generally have no contact on the inner or outer wall of the installation space in the pressureless state. An advantage for the user is the use of only one sealing ring dimension for two applications. The following disadvantages occur: At the manufacturer, the contour-forming tool cavities are only for forming

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of elastomers of a limited range of turn sizes. The user does not experience a reliable fit due to the only linear contact of the sealing lips on the adjacent resting surface. A shortening of the life as a result of increased wear or increasing leakage are the result. Reference is made to TGL 636I. From the above-mentioned disadvantages, those described below developed. Versions. ,

2. Lip ring with only one sealing lip on the moving inner

: Lateral surface · _...., · ...-.

The outer surface of the sealing ring is due to the profile shape and a predetermined excess of the adjacent resting surface over a wide range with a

... sufficient tightness and ensures a stable position. The profile section is often asymmetrical. They can only be used as an inner seal, for example as a rod seal. Reference is made to TGL 6357 and 38482.

3. lip ring with only one sealing lip on the moving outer surface. '; '

It is also known that for sealing rings of this type, depending on the manufacturer, a small, moderate or very tight Featsitz is provided by an appropriate dimensioning. The profile section is often asymmetrical. They can only be used as an outer seal, for example as a piston seal. Reference is made to TGL 6359 and 34483. The advantages of the lip rings mentioned under 2 and 3 result · from the functionally reliable positional fixation in the relatively stationary part of the installation space, which makes it possible to achieve a longer service life, lower leakage and a lower abrasion or extrusion wear.

The mastery of a larger shrinkage range of the elastomers used with a given tool contour processing is possible.

The disadvantages of the embodiments mentioned under 2 and 3 can be seen in the fact that for each Abdichtfall "inside" and "outside" at the same Nenndurciimessern two different sealing rings and thus also Urformwerkzeuge are required.

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As a result, lot sizes in production are reduced, necessary inventory increases, and the economic balance deteriorates accordingly.

Object of the invention

The aim of the invention is to provide a sealing ring whose. constructive 'design such optimal installation conditions allows maximum puncture at high. Life is guaranteed and at the same time by the _ bivalent usability as a piston or piston rod seal minimization of the range of seals and thus'a lot size increase is achieved by the manufacturer.

presentation; the essence of the invention

The technical problem is to develop a seal, which in housings of different inner nominal diameter ^ fSt ) ^UELC ^ outer nominal diameter D / r _r \ on the lifting side, but the same installation space width s = 0.5 ( ¹ W) ~ ^ (K)) or ε = 0.5 ( ^D fst) ~ ^ (S *) ^ ^e i ^nse ' ^fcz k ^ar is and because of their profile design both for sealing pistons and piston rods both produced mostly in internationally standardized large series, find use can, while meeting the two important function-determining requirements: Rigid tight fit without additional auxiliary elements on the stationary lateral surface and relatively low-friction and leakage-preventing sliding fit on the hubbewegten lateral surface. The object is achieved in that the average diameter of a lip ring to the average of the nominal diameter sum on the hubbewegten side of the installation space of the respectively associated piston and piston rod seal is dimensioned so that when using the lip ring in the first case, an expansion and in the second case, a compression occurs , These amounts according to the diameter assignment elastomer-dependent - without increasing the aging susceptibility, jeopardize the mountability and cause impermissible cross-sectional changes - can be up to 10 % , based on the average lip ring diameter, and sliding or

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Firmly fix the fixed seat side.

For equal amounts of elongation and compression (^ dp = Δ (ΐ), the average lip ring diameter in the compact, cross-sectional area d ^ = 0.5 (D-, + dj,) is equal to half the sum of the lien diameter = 0.5 C - ⁰ Vv-) ⁺ . ^ RST ^ ^to ^ ^{he ewe} O u ^s hubbewegten side of the associated installation space of the piston sealing ^ (TT) and the piston rod sealing d / O ^ ν.

For a larger amount of elongation than that of the compression ^ (^ d _D > ^ dg), the average lip ring diameter in the compact cross-sectional area dp _m = 0.5 (Dj, + dp) is equal to half the sum of the belt diameters. = 0.5 (^ W) ⁺ ^ Cst) ^ ^on the respective stroke-moving side of the associated Sinbauraumes the piston seal D / τ, χ and the Kolbenstangenabdiehtung minus half the deformation value difference = Ό, 5.

For a larger amount of compression compared to that of elongation (Δά ^ Δά ^) , the average lip ring diameter in the compact cross-sectional area d 1, = 0.5 (D + d 1) is equal to half the sum of the nominal diameter = 0.5 (D. (xr) + d / g. \) at the respective Hubbevvegten side of the associated installation space of the piston seal D / "^ and the piston rod seal

plus half the deformation value difference = 0.5 ^

Ausführun ^ SExample

The subject of the invention will be explained on the following embodiment.

For a sealed by means of an inner lip ring hub-. moving piston rod with a ITenndurchmesser ^ (5 ^) = 63 mm and to be sealed by means of outer lip rings lifting piston with a nominal diameter D / ^ = 80 mm according to the present international standard, the installation space width S each 7 »5 mm.

If, due to the presence of the same installation space width (equation 1), only one lip ring size of the design and dimensioning according to the invention is used for both sealing cases, then the same amounts for elongation and compression can be used (equation 2 fulfilled)

According to equation 3, the average lip ring diameter can be determined. According to equations 4a and 4b, the inner and outer lip ring diameters can be calculated in the compact cross-sectional area. , · ', »,

- Calculation equations:

S = 0.5 (Dp - dp) - 0.5 (D. _(K) - d _(K) ) = 0.5 (^ - d ^) '(1)

Λά _Ώ = d _s _ - (2)

Δά _Ώ = d _(K) - d _p .

* ^d S = ^D F - ^D (St)

^d Pm = ° ' ^{5 (D} (K) - ^d (St) ⁾ " ⁽³⁾

- S (4a)

+ S '(4b)

- Calculation case 1:

Given: S = 7.5 mm

^d (St) ^{= 63 Ksm (D} (St) = 78 mm = 80 mm ^ ^d (K) = 65 mm

average lip ring diameter in the compact cross-sectional area

^{+ δ} 3 mm) = 71.5 mm

outer lip ring diameter in the compact cross-sectional area Dp = 71.5 mm + 7.5 mm = 79 mm

inner lip ring diameter in the compact cross-sectional area dp = 71.5 mm - 7.5 mm = 64 mm

absolute elongation (piston seal)

• Ad-, = 65 mm - 64 mm = 1mm

absolute compression (piston seal)

Δ dg = 79 mm - 78 mm = 1 mm

relative deformation value

f. = ^1mm - . TOO % = 1.4 % ". '

71.5 mm '

Calculation date 2:. ·. , '

Assuming, for example, that the elastomer-dependent relative deformation values for the elongation = 1.4 to 8.4 % and for the compression = 1.4 to 5.6%, the following nominal diameter ranges can be sealed with the lip ring discussed in the exemplary embodiment become.

Piston sealing:

absolute stretching. - '

a ^ 8.4 % · 71 * 5 mm = 6 mm η ⁼

, '; 100 %

Inner diameter of the installation space

d / rr · «= 64 mm +.6 mm = 70 mm

Outside diameter of the installation space

= 70 mm + 15 mm = 85 mm -

sealable nominal diameter range

= 80 to 85 mm

Piston rod seal: absolute compression

- 5.6% . 71.5 mm = 4 mm * 100%

Outside diameter of the installation space ^ (St) = 79 mm - 4 mm = 75 mm

Inner diameter of the installation space

= 75 mm - 15 mm = 60 mm

sealable nominal diameter range

d = 60 to 63 mm (St) '.

Presentation:

The discussed lip ring is shown in FIG. Pig. Fig. 2 shows the construction example of a piston rod seal; Pig. 3 that of a piston seal. The illustrations take into account the fact that the lip ring width in the compact cross-sectional area in practice is slightly narrower than the installation space width, in order to keep the loss of leakage, in particular at low pressure - as low as possible. '

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Claims (4)

Claims:. , , 1. Lip ring made of elastic material and preferably symmetrical profile cross-section for installation in. Sealing chambers of different nominal diameter, however, the same width for sealing piston or piston rods, characterized in that the average diameter of a lip ring size for half sum of the Henndurchmesser on hubbewegten side of the lip ring mounting space of the respectively associated piston and piston rod seal is dimensioned so that when using the lip ring in the first If an expansion and in the second Pail a. Compression occurs, these amounts according to the diameter allocation 'elastomer dependent can be up to 10 % , based on the average lip ring diameter and the sliding or Pestsitzseite clearly fix. , 2. Lip ring according to point 1 dadurc hg e characterize t that at the same amounts for the elongation and compression of the average lip ring diameter in the compact cross-sectional area equal to half the sum of the nominal diameter on the hubbewegten side of the lip ring installation space of the respectively associated piston and piston rod seal. 3. Lip ring according to point 1. , characterized in that at a greater amount of elongation relative to the compression of the average lip ring diameter in the compact cross-sectional area equal to half the sum of the Uenndurchmesser on the hubbewegten side of the lip ring installation space of the respective   ordered piston and piston rod seal minus the. is half the difference in the deformation amounts. 4 # lip ring after point 1 By this I mean that, with a greater amount of compression compared to the expansion of the mean lip ring diameter in the compact cross-sectional area is equal to half the sum of the nominal diameter on the stroke-moving side of the lip ring installation space of the respectively associated piston and piston rod seal plus half the difference in the deformation amounts. nut Λ C \ Ί (\ -λ! "7 i *