CN114110168A - Matching design method for assembling relation of thrust wheels - Google Patents

Matching design method for assembling relation of thrust wheels Download PDF

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Publication number
CN114110168A
CN114110168A CN202111429692.8A CN202111429692A CN114110168A CN 114110168 A CN114110168 A CN 114110168A CN 202111429692 A CN202111429692 A CN 202111429692A CN 114110168 A CN114110168 A CN 114110168A
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Prior art keywords
floating seal
seal seat
clearance
assembly
relation
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Inventor
徐轲
刘彬
陈元锋
魏贺
刘阳
常艳红
董春锋
徐明洋
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Xuzhou Xugong Caterpillar Base Plate Co ltd
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Xuzhou Xugong Caterpillar Base Plate Co ltd
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Priority to CN202111429692.8A priority Critical patent/CN114110168A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)

Abstract

The disclosure relates to a matching design method of a thrust wheel assembly relationship, which comprises the following steps: determining the specific pressure requirement of the floating seal end face, and constructing the relation between the specific pressure Pc of the floating seal end face and the clearance A of the floating seal seat; and determining the value range of the floating seal seat gap A under the requirement of the floating seal end face specific pressure based on the relation between the floating seal end face specific pressure Pc and the floating seal seat gap A. The matching design method of the thrust wheel assembly relation obtains the value range of the floating seal seat gap A according to the specific pressure requirement of the floating seal end face by constructing the relation between the specific pressure of the floating seal end face and the floating seal seat gap, reasonably designs and matches the sizes of different thrust wheels and thrust wheel assembly components under a floating seal structure, and ensures the sealing performance during the operation of engineering machinery.

Description

Matching design method for assembling relation of thrust wheels
Technical Field
The disclosure relates to a matching design method for a thrust wheel assembly relationship.
Background
The statements herein merely provide background information related to the present disclosure and may not necessarily constitute prior art.
The floating seal is an important component for ensuring that a thrust wheel in one of four wheels does not have oil leakage failure, and the clearance of the floating seal seat is an important parameter influencing the performance of the floating seal and is used for compensating clearance change caused by the size and form and position tolerance of the floating seal structure. The thrust wheel floating seal seat clearance receives performance and sealing performance's restriction, both will guarantee that the thrust wheel body passes through the free reasonable axial float motion and the circumferential motion of slide bearing on the shaft, will prevent the entering of external foreign matter when the normal operation of thrust wheel again, and the terminal surface ratio under this fitting gap of while need guaranteeing is pressed in the required scope, prevents the oil leak.
The floating seal seat clearance is defined according to different influence factors as follows: (1) direct axial variation clearance caused by actual assembly axial dimension and form and position tolerance; (2) the floating seal constitutes a relative axially varying clearance caused by the radial dimensions and form and position tolerances of the components. The design of the structural components of the floating seal cavity mainly selects standards or series, the gap of the floating seal seat is reasonably designed and matched under the existing established standards or series, and the most direct and effective method is to reasonably design the matching and assembling relationship.
The design matching of the assembling relation of the thrust wheel reflects the assembling position and the assembling sequence of each component of the thrust wheel, determines the assembling position at the extreme value of the clearance of the floating seal seat, directly influences the direct axial clearance change of the floating seal seat after tolerance accumulation and finally influences the size of the clearance of the floating seal seat.
Disclosure of Invention
One technical problem to be solved by the present disclosure is: the matching design method for the assembling relation of the thrust wheels is provided, and the sealing performance of the engineering machinery during operation can be guaranteed.
Some embodiments of the present disclosure provide a matching design method of a thrust wheel assembly relationship, including:
determining the specific pressure requirement of the floating seal end face, and constructing the relation between the specific pressure Pc of the floating seal end face and the clearance A of the floating seal seat; and
and determining the value range of the floating seal seat gap A under the requirement of the floating seal end face specific pressure based on the relation between the floating seal end face specific pressure Pc and the floating seal seat gap A.
In some embodiments, the relationship between the floating seal end face specific pressure Pc and the floating seal seat clearance a is obtained by the following relation:
the relation between the specific pressure Pc of the floating seal end face and the deformation quantity Delta d of the floating seal ring is expressed as follows:
Figure BDA0003379786370000021
the relation between the deformation quantity delta d of the floating seal ring and the height h of the floating seal cavity at the end of assembly is expressed as follows:
△d＝d0-h
the relation between the height h of the floating seal cavity and the clearance A of the floating seal seat at the end of assembly is expressed as follows:
Figure BDA0003379786370000022
wherein alpha is the taper angle of the floating seal ring, S is the area of the contact end surface of the two floating seal rings, EaThe elastic modulus of the floating seal rubber ring, the deformation quantity of the floating seal rubber ring, d0Is the diameter of the section of the floating seal rubber ring D0The inner diameter of the floating seal rubber ring is measured, mu is the friction coefficient of the floating seal rubber ring and the floating seal cavity, A0A gap of the floating seal seat at the initial assembly position, h0The height of the floating seal cavity at the initial assembly position is A, the clearance of the floating seal seat at the end of assembly is A, and the height of the floating seal cavity at the end of assembly is h.
In some embodiments, the method further comprises: and adjusting the clearance of the floating seal seat based on the use requirement of the floating seal.
In some embodiments, adjusting the floating seal seat clearance based on the floating seal usage requirements comprises: according to the use requirement of the floating seal, the size of the floating seal rubber ring or the contact area of the contact end surfaces of the two floating seal rings is adjusted to adjust the gap of the floating seal seat.
In some embodiments, the method further comprises: based on the use requirement and the floating seal seat gap requirement determined by the specific pressure of the floating seal end face, determining the matching relation between the relative axial floating seal seat gap change caused by the radial dimension of the floating seal cavity structure and the direct axial floating seal seat gap change caused by the thrust wheel assembly relation, and determining the thrust wheel assembly relation and the floating seal seat gap change requirement.
In some embodiments, the method further comprises: and determining the limit position of the clearance of the floating seal seat according to the position of the assembly component of the thrust wheel and the assembly sequence, matching the limit value of the clearance of the floating seal seat based on the determined change range of the clearance of the direct axial floating seal seat under the limit position of the clearance of the floating seal seat, and ensuring that the limit value of the clearance of the floating seal seat meets the use requirement of the thrust wheel.
In some embodiments, the method further comprises: according to the limit position of the clearance of the floating seal seat and the extreme value of the clearance of the floating seal seat, determining the actual assembly relation of the thrust wheel, determining an assembly dimension chain, carrying out dimension and tolerance distribution on the basis of the clearance change of the floating seal seat caused by the dimension and tolerance of the assembly structure of the thrust wheel and the actual assembly relation, and determining the structural dimension and form and position tolerance of the assembly component of the thrust wheel.
Therefore, according to the matching design method of the thrust wheel assembly relationship, the value range of the floating seal seat gap A is obtained according to the specific pressure requirement of the floating seal end face by constructing the relationship between the specific pressure of the floating seal end face and the floating seal seat gap, the sizes of the thrust wheel assembly components under different thrust wheels and floating seal structures are reasonably designed and matched, and the sealing performance of the engineering machinery during operation is ensured.
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In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 illustrates a floating seal arrangement in some embodiments of the present disclosure;
FIG. 2 illustrates the floating seal arrangement of FIG. 1 in a mated configuration at various mated positions;
FIG. 3 illustrates the floating seal arrangement of FIG. 1 in an initial mating position;
FIG. 4 illustrates the axial clearance A versus distance h for the floating seal arrangement of FIG. 1;
FIG. 5 illustrates a bogie wheel assembly arrangement in some embodiments of the present disclosure;
FIG. 6 illustrates the location of a floating seat clearance minimum in some embodiments of the present disclosure;
FIG. 7 illustrates a dimensional chain of slider seat gap minima in some embodiments of the present disclosure;
FIG. 8 illustrates the location of a floating seat clearance maximum in some embodiments of the present disclosure;
FIG. 9 illustrates a dimensional chain of floating seat clearance maxima in some embodiments of the present disclosure.
Description of the reference numerals
1. A floating seal seat; 2. a floating seal ring; 3. and (5) floating and sealing the rubber ring.
Detailed Description
Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not as limitative, unless specifically stated otherwise.
The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word covers the element listed after the word, and does not exclude the possibility that other elements are also covered. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be intervening devices between the specific device and the first device or the second device. When a particular device is described as being coupled to other devices, the particular device may be directly coupled to the other devices without intervening devices or may be directly coupled to the other devices with intervening devices.
All terms used in the present disclosure have the same meaning as understood by one of ordinary skill in the art to which the present disclosure belongs, unless otherwise specifically defined. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.
As shown in fig. 1 to 4, the floating seal is an annular floating seal for a DO type floating seal of a thrust wheel of a large excavator of a certain construction machine, and includes: a floating seal seat 1, a floating seal ring 2 and a floating seal rubber ring 3. In the figure, A is the clearance of the floating seal seat, h is the height of the floating seal cavity, alpha is the taper angle of the floating seal ring, and beta is the taper angle of the floating seal seat. The schematic view of the thrust wheel assembling components and the assembling relationship is shown in fig. 5.
Some embodiments of the present disclosure provide a matching design method of a thrust wheel assembly relationship, including: determining the specific pressure requirement of the floating seal end face, and constructing the relation between the specific pressure Pc of the floating seal end face and the clearance A of the floating seal seat; and
and determining the value range of the floating seal seat gap A under the requirement of the floating seal end face specific pressure based on the relation between the floating seal end face specific pressure Pc and the floating seal seat gap A.
In the illustrative embodiment, the value range of the clearance A of the floating seal seat is obtained by constructing the relation between the specific pressure of the floating seal end face and the clearance of the floating seal seat according to the specific pressure requirement of the floating seal end face, the sizes of different thrust wheels and thrust wheel assembling components under the floating seal structure are reasonably designed and matched, and the sealing performance of the engineering machinery during operation is ensured.
With reference to fig. 1 to 4, in some embodiments, the relationship between the floating seal end face specific pressure Pc and the floating seal seat clearance a is obtained by the following relation:
the relation between the specific pressure Pc of the floating seal end face and the deformation quantity Delta d of the floating seal ring is expressed as follows:
Figure BDA0003379786370000051
the relation between the deformation quantity delta d of the floating seal ring and the height h of the floating seal cavity at the end of assembly is expressed as follows:
△d＝d0-h
the relation between the height h of the floating seal cavity and the clearance A of the floating seal seat at the end of assembly is expressed as follows:
Figure BDA0003379786370000061
wherein alpha is the taper angle of the floating seal ring, S is the area of the contact end surface of the two floating seal rings, EaThe elastic modulus of the floating seal rubber ring, the deformation quantity of the floating seal rubber ring, d0Is the diameter of the section of the floating seal rubber ring D0The inner diameter of the floating seal rubber ring is measured, mu is the friction coefficient of the floating seal rubber ring and the floating seal cavity, A0A gap of the floating seal seat at the initial assembly position, h0The height of the floating seal cavity at the initial assembly position is A, the clearance of the floating seal seat at the end of assembly is A, and the height of the floating seal cavity at the end of assembly is h.
The relation between the floating seal end face specific pressure Pc and the floating seal seat gap A can be obtained through the relational expression, and the value range of the floating seal seat gap A is obtained according to the requirement of the floating seal end face specific pressure.
In this embodiment, the taper angle α of the floating seal ring is 15 °, the contact end surface area S of the two floating seal rings is 1486mm2, and the elastic modulus E of the floating seal ringaTaking the volume of 30.39Kg/cm3Diameter d of section of floating seal rubber ring012.6mm, the inner diameter D of the floating seal rubber ring0166mm, the friction coefficient mu of the floating seal rubber ring and the floating seal cavity is 0.25, and the clearance A of the floating seal seat at the initial assembly position026.801mm, floating seal chamber height h at initial assembly position0Is 12.6 mm.
The end face specific pressure requirement of the large excavator for ensuring the sealing performance is generally 0.3 MPa-0.6 MPa, the deformation delta d of the floating seal ring under 0.3MPa and 0.6MPa and the height h of the floating seal cavity at the end of assembly are respectively calculated according to the established relation between the end face specific pressure and the floating seal seat gap, and the floating seal seat gap A meeting the performance requirement under the floating seal structure is determined to be 2.835 mm-9.841 mm.
In some embodiments, the method further comprises: and adjusting the clearance of the floating seal seat based on the use requirement of the floating seal. The floating seal seat clearance is restricted by the use performance, the floating seal seat clearance and the range requirement are determined by considering the requirement of ensuring the free and reasonable axial float motion and circumferential motion of the thrust wheel body on the wheel shaft, and meanwhile, the external foreign matters are prevented from entering during operation.
In some embodiments, adjusting the floating seal seat clearance based on the floating seal usage requirements comprises: according to the use requirement of the floating seal, the size of the floating seal rubber ring or the contact area of the contact end surfaces of the two floating seal rings is adjusted to adjust the gap of the floating seal seat.
In the embodiment, the free and reasonable axial float motion and circumferential motion of the wheel body of the thrust wheel on the wheel shaft are met, and the clearance of the floating seal seat meeting the service performance requirement under the floating seal structure is determined to be 1.50-7.00 mm when external foreign matters enter in normal operation; the clearance A of the floating seal seat is preliminarily determined to be 2.835 mm-9.841 mm based on the requirement of floating seal performance. The size of the floating seal rubber ring or the contact area of the contact end surfaces of the two floating seal rings needs to be adjusted to adjust the gap of the floating seal seat within the range of the use requirement. For the present example, the floating seal seat gap A meeting the end face specific pressure requirement and the use requirement is determined to be 2.835 mm-7.00 mm by adjusting the area of the contact end faces of the two floating seal rings.
In some embodiments, the method further comprises: based on the use requirement and the floating seal seat gap requirement determined by the specific pressure of the floating seal end face, determining the matching relation between the relative axial floating seal seat gap change caused by the radial dimension of the floating seal cavity structure and the direct axial floating seal seat gap change caused by the thrust wheel assembly relation, and determining the thrust wheel assembly relation and the floating seal seat gap change requirement.
The clearance of the floating seal seat under the requirements of the end face specific pressure and the performance of the large excavator is 2.835 mm-7.00 mm, and the clearance range is 4.165 mm; for the embodiment, the matching relation between the clearance change of the relative axial floating seal seat caused by the radial dimension of the floating seal cavity structure and the clearance change of the direct axial floating seal seat caused by the assembling relation of the thrust wheels is determined to be 4:6, and the clearance change of the direct axial floating seal seat caused by the assembling relation of the thrust wheels is determined to be 2.508 mm.
In some embodiments, the method further comprises: and determining the limit position of the clearance of the floating seal seat according to the position of the assembly component of the thrust wheel and the assembly sequence, matching the limit value of the clearance of the floating seal seat based on the determined change range of the clearance of the direct axial floating seal seat under the limit position of the clearance of the floating seal seat, and ensuring that the limit value of the clearance of the floating seal seat meets the use requirement of the thrust wheel.
In the embodiment, one end of the end cover, the bearing bush and the wheel body which are close to each other in the assembling process of the thrust wheel is a floating seal seat clearance minimum position end, and the other end of the end cover, the bearing bush and the wheel body is a maximum position end. The minimum position gap is determined to be
Figure BDA0003379786370000071
When left end lid and axle bush contact promptly, it is to become the clearance between tip floating seal seat: 1.9 mm-3.15 mm; determining the maximum position gap as
Figure BDA0003379786370000072
Namely, when the left end cover is contacted with the bearing bush, the gap of the floating seal seat at the enlarged end is 265 mm-4.408 mm. The clearance change of the floating seal seat caused by the assembly relation determined based on the limit position is 1.9-4.408 mm. In the present example, the clearance required for the normal operation of the thrust wheel is 1.5mm to 7.0mm, and the clearance of the floating seal seat is changed to 1.9mm to 4.408mm, so that the thrust wheel can be used.
In some embodiments, the method further comprises: according to the limit position of the clearance of the floating seal seat and the extreme value of the clearance of the floating seal seat, determining the actual assembly relation of the thrust wheel, determining an assembly dimension chain, carrying out dimension and tolerance distribution on the basis of the clearance change of the floating seal seat caused by the dimension and tolerance of the assembly structure of the thrust wheel and the actual assembly relation, and determining the structural dimension and form and position tolerance of the assembly component of the thrust wheel.
For the present example, in the thrust wheel assembly process, one end of the end cover, the bearing bush and the wheel body which are close together is the floating seal seat gap minimum position end, and the other end is the maximum position end. The clearance change of the floating seal seat caused by the assembly relation is 1.9-4.408 mm, and the direct axial change clearance range is 2.508 mm.
And determining an actual assembly dimension chain based on the limit position of the clearance of the floating seal seat and the size of the clearance of the floating seal seat, and distributing the structural dimension tolerance of the assembled components such as the wheel body, the bearing bush and the like based on the dimension chain. The assembly dimension chain and the thrust wheel assembly component parts are shown in figures 5-9 in terms of structural dimension and form and position tolerance.
In summary, according to the matching design method for the assembling relationship of the thrust wheel provided by the present disclosure, under the requirement of the clearance of the floating seal seat, the clearance change of the relative axial floating seal seat caused by the radial dimension of the structure of the matching floating seal cavity and the clearance change of the direct axial floating seal seat caused by the assembling relationship of the thrust wheel are determined, and after the requirement of the clearance change of the floating seal seat of the assembling relationship of the thrust wheel is determined, the dimension and tolerance of the matching floating seal seat and the wheel body are designed based on the requirement, and the assembling dimension chain and the like are designed. The method can reasonably design and match the sizes, tolerances and tolerance zones of the different thrust wheels and the thrust wheel assembly components under the floating seal structure based on the clearance requirement of the floating seal seat, adjust the reference and reasonably design the size chain.
The reasonable design matching of the structure size and tolerance of the bearing wheel assembly relation and the assembly component directly ensures that the bearing wheel body freely and reasonably performs axial float motion and circumferential motion on the wheel shaft through the sliding bearing, prevents external foreign matters from entering during normal operation of the bearing wheel, and avoids abnormal abrasion caused by unreasonable motion of the wheel body during normal operation of the excavator. Meanwhile, the reasonable design matching of the structural size and tolerance of the thrust wheel assembly relation and the assembly component also determines the rationality of the floating seal seat gap, ensures the rationality of the specific pressure of the lower end surface of the floating seal seat gap, and ensures the sealing performance of the excavator during installation and operation.
Thus, various embodiments of the present disclosure have been described in detail. Some details that are well known in the art have not been described in order to avoid obscuring the concepts of the present disclosure. It will be fully apparent to those skilled in the art from the foregoing description how to practice the presently disclosed embodiments.
Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the foregoing examples are for purposes of illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that various changes may be made in the above embodiments or equivalents may be substituted for elements thereof without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.

Claims (7)

1. A matching design method for a thrust wheel assembly relation comprises the following steps:
determining the specific pressure requirement of the floating seal end face, and constructing the specific pressure P of the floating seal end facecThe relation with the floating seal seat gap A; and
based on floating seal end face specific pressure PcAnd determining the value range of the floating seal seat gap A under the specific pressure requirement of the floating seal end face according to the relation with the floating seal seat gap A.
2. The matching design method for the assembling relationship of the thrust wheels according to claim 1, wherein the construction of the floating seal end face specific pressure PcThe relationship with the floating seal seat gap A is obtained by the following relational expression:
floating sealSpecific pressure P of end facecAnd the deformation quantity delta d of the floating seal rubber ring are expressed as follows:
Figure FDA0003379786360000011
the relation between the deformation quantity delta d of the floating seal ring and the height h of the floating seal cavity at the end of assembly is expressed as follows:
△d＝d0-h
the relation between the height h of the floating seal cavity and the clearance A of the floating seal seat at the end of assembly is expressed as follows:
Figure FDA0003379786360000012
wherein alpha is the taper angle of the floating seal ring, S is the area of the contact end surface of the two floating seal rings, EaThe elastic modulus of the floating seal rubber ring, the deformation quantity of the floating seal rubber ring, d0Is the diameter of the section of the floating seal rubber ring D0The inner diameter of the floating seal rubber ring is measured, mu is the friction coefficient of the floating seal rubber ring and the floating seal cavity, A0A gap of the floating seal seat at the initial assembly position, h0The height of the floating seal cavity at the initial assembly position is A, the clearance of the floating seal seat at the end of assembly is A, and the height of the floating seal cavity at the end of assembly is h.
3. The matching design method of the assembling relationship of the thrust wheels according to claim 1 or 2, further comprising: and adjusting the clearance of the floating seal seat based on the use requirement of the floating seal.
4. The matching design method for the thrust wheel assembly relationship according to claim 3, wherein the adjusting the floating seal seat gap based on the floating seal use requirement comprises: according to the use requirement of the floating seal, the size of the floating seal rubber ring or the contact area of the contact end surfaces of the two floating seal rings is adjusted to adjust the gap of the floating seal seat.
5. The matching design method of the assembling relationship of the thrust wheels according to claim 3, further comprising: based on the use requirement and the floating seal seat gap requirement determined by the specific pressure of the floating seal end face, determining the matching relation between the relative axial floating seal seat gap change caused by the radial dimension of the floating seal cavity structure and the direct axial floating seal seat gap change caused by the thrust wheel assembly relation, and determining the thrust wheel assembly relation and the floating seal seat gap change requirement.
6. The matching design method of the assembling relationship of the thrust wheels according to claim 5, further comprising: and determining the limit position of the clearance of the floating seal seat according to the position of the assembly component of the thrust wheel and the assembly sequence, matching the limit value of the clearance of the floating seal seat based on the determined change range of the clearance of the direct axial floating seal seat under the limit position of the clearance of the floating seal seat, and ensuring that the limit value of the clearance of the floating seal seat meets the use requirement of the thrust wheel.
7. The matching design method of the assembling relationship of the thrust wheels according to claim 6, further comprising: according to the limit position of the clearance of the floating seal seat and the extreme value of the clearance of the floating seal seat, determining the actual assembly relation of the thrust wheel, determining an assembly dimension chain, carrying out dimension and tolerance distribution on the basis of the clearance change of the floating seal seat caused by the dimension and tolerance of the assembly structure of the thrust wheel and the actual assembly relation, and determining the structural dimension and form and position tolerance of the assembly component of the thrust wheel.
CN202111429692.8A 2021-11-29 2021-11-29 Matching design method for assembling relation of thrust wheels Pending CN114110168A (en)

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