Patent Application
20140283368
This invention relates to an adaptive design of fixture for shell/cylindrical components, for the purpose of enabling them to be machined with sufficient supporting rigidity and dynamic stability, so as to maintain the machining precision and surface finish to an acceptable engineering standard. The invention is particularly applicable to thin-walled components where secure fixture and vibration avoidance during machining is difficult to achieve.
According to the theory of structural mechanics, well known to those skilled in the art, shell/cylindrical components are defined as a group of hollow objects with openings, shaped with continuity and curvature. A bowl-like structure characterises a shell component, having a single major opening, whereas a hollow tubular structure having a through-opening characterises a cylindrical component. Both have a wall that has a wall-thickness, and each has a profile-dimension, which is either its radius, if its diameter is larger than its height, or its height otherwise. In terms of the profile-dimension-to-wall-thickness ratio, shell/cylindrical components are classified as:
Based on this classification, the thin-walled shell/cylindrical components to which the present invention particularly relates are defined as, and limited to, hollow structures with one major opening, or through opening, having:
The defined thin-walled shell/cylindrical component may have minor openings and an uneven internal/external surface without changing its character. Such component is difficult to hold while it is machined. The thin wall lacks sufficient static rigidity and dynamic stability to withstand the cutting force generated in the machining process. Through lack of shear effects, the thin wall becomes dynamically unstable and liable to vibrate, causing machining precision problems, mainly from the insufficient supporting rigidity, and surface finish problems, mainly from the unstable self-excited vibration between the cutting-tool and workpiece (called hereafter for simplicity “chatter”).
A well-designed static fixture will not help with this situation mainly because, on the one hand, a static fixture precisely fitting most of the shell/cylindrical surface will be expensive and sometimes impossible, and, on the other hand, even if a static fixture is very well designed and fits precisely the at-rest position of a thin-walled component, when excited by the cutting force, the flexible thin wall, mainly maintained by stretching and bending effects, will still deflect around the still position and bounce against the still support, so as to deteriorate the dynamic stability of the component. Design of a dynamic fixture adaptively fitting, supporting and dampening the thin-walled components is obviously a desirable objective.
In any industry, it is undesirable to have waste. Consequently it is always desirable to minimise component mass, provided of course that other factors do not militate against this. For example, there is no purpose in reducing component mass if the component will consequently fail sooner than is desirable, particularly if the mass of the component is not otherwise detrimental to the operation of the component. However, in some industries, component mass is itself a substantial issue and nowhere is this more the case than in the aerospace and defence industries.
Rocket shell and jet engine casing are typical thin-walled shell/cylindrical components. Most of them are made from difficult-to-machine material, such as heat-resistant alloy, and there is always a very strict requirement on removing the unnecessary component mass to the minimum. In order to provide all the precise interfaces for connection, also to remove all the unnecessary mass from a forging or casting part to get a finished component, machining work is inevitable. Holding such a component during the comparatively tougher machining process is problematic, since the thin wall is flexible and dynamically unstable. The currently employed solution by most engineers is to treat the components individually, studying the vibration characteristics of such components and predict problem areas, and then to determine appropriate machining procedures to minimise the effects of chatter.
Nevertheless, the present invention is particularly (although not, by any means, exclusively) concerned with providing an adaptive fixture for holding such a component during the required machining operations, and one that adaptively fits most of the component surface, adaptively supports the component for a higher rigidity, and adaptively dampens the thin wall for a higher stability. Here, ‘adaptive’ means the capability of self-adaptation both in geometric and dynamic senses.
U.S. Pat. No. 6,015,154 discloses a holder in the form of a metallic sleeve having slots and surrounding a polymeric sleeve sealed at its ends to an arbour so as to define a hydrostatic chamber between the polymeric sleeve and arbour whereby pressurising the chamber expands the sleeves, the metal sleeve gripping and holding internally a cast engine cylinder liner sleeve to permit machining thereof. The metallic sleeve can expand about 8 mm in diameter. Although dampening vibrations is stated as an objective, there is no explanation of how this is provided beyond the holder itself.
U.S. Pat. No. 4,811,962 discloses a similar arrangement, but without the metallic sleeve. The polymeric sleeve in this case comprises a Teflon® shell that, while having some flexibility to permit expansion to grip a cylindrical sleeve internally, has capacity to expand only a few millimetres in diameter.
U.S. Pat. No. 4,253,694 discloses an internal pickup device for round products comprising a cylindrical part and elastomeric rings in grooves of the part, the base of whist grooves can be pressurised with fluid to expand the elastomer rings to grip the object internally.
GB-A-1445216 discloses a clamping device for a thin-walled cylindrical object to be trued, comprising a similar arrangement as described in U.S. Pat. No. 4,253,694.
However, even with thick-walled components, a fixture therefor that provides adaptive damping would be advantageous in the search for improved machining performance. Again, in this context, “adaptive” means both capable of fitting components of different sizes and being tailored to suit the dynamic vibration characteristics associated with particular machining operations.
In accordance with the present invention there is provided a fixture for a shell/cylindrical component comprising: a thick- or very thick-walled base having first location means to locate and clamp one end of the component; a thick- or very thick-walled column fixed in the base; an endless tubular inflatable elastomeric pressure element, disposed on the base between the column and, when in use, the component; and a sacrificial liner adapted to fit between the pressure element and component.
Preferably, the fixture further comprises a thick- or very thick-walled lid to be fixed to the column and having second location means to locate the other end of the component.
Being thick-walled, the column, base and lid provide structures with at least stretching, bending and higher order transverse shear effects considered, coupled with obvious sparseness of vibration modes at a frequency of 1000 Hz.
Preferably, said liner has a total thickness between 10 mm and 20 mm, whereby penetrating tool movements through the shell/cylindrical components during a machining operation do not penetrate the pressure element. Preferably, the liner is a multi-layered polymeric/elastomeric material, the layers being adhered or otherwise bonded together. Thus, the liner also serves to spread a uniform supporting pressure, mainly through the shear effects between layers, and dynamic damping, mainly through the polymeric or elastomeric material, normal to the component surface to be machined. Regional enhancements around minor openings of the component are employable by inserting curled nylon sheet inside the outer layer of the liner, against the thin wall to be machined.
Preferably, said pressure element is pneumatically inflated, within a stable and safe working range up to 5 times of its flat diameter and inflating pressure up to 4.0 Bar. Conveniently, it may comprise a modified vehicle wheel inner tube, which is capable of expansion to the required size and very well fitting the enclosure confined within the shell/cylindrical component, supporting arbour or cylinder, mounting base and lid. An inflation valve of the tube may protrude though an aperture provided for this purpose on the internal arbour or external supporting cylinder. Two or more tubes are employable one on top of the other, for long shell/cylindrical components.
In one arrangement, the column is inside the component, the pressure element surrounding the column, the liner surrounding the pressure element, and the component, when the fixture is in use, surrounding the liner, pressure element and column. In this arrangement, the component is pressed radially outwardly by the pressure element and machining operations can be effected on its external surface.
However, in another arrangement, the column is hollow and is outside the component, the pressure element being within the column surrounding the liner which itself surrounds the component, when the fixture is in use. In this arrangement, the component is pressed radially inwardly by the pressure element and machining operations can be effected on its internal surface.
Adaptive fixture design satisfies the demand in advanced manufacturing engineering of an agile and flexible fixture combination adaptable to different products with similar structural functions but different detailed shapes and sizes. An important element in the present invention is the pressure element, particularly when in the form of an expansible pneumatic tube, which is inflatable within a stable and safe working range up to 5 times its flat diameter and inflating pressure up to 4 Bar. Helped by this, the fixture is not only adaptive to fit the detailed shape of the component, but also adaptive to fit a considerable range of component sizes up to around 4 times of a nominated component diameter. Another special advantage from the pneumatic element is that, by providing a pneumatic damping cavity with the fixture, machining chatter energy is absorbed preventing the usual exponential growth of vibration once it begins.
Said internal or external supporting cylinder plays a key role in sustaining sufficient supporting rigidity and dynamic stability to the thin-walled component. Said thin-walled shell/cylindrical components are mainly balanced by stretching and bending stresses and lack shear effects to maintain a global rigidity. Therefore, with this rigid support, the pneumatic element applies a uniform normal pressure through the multi-layered liner onto the thin wall and, adaptively fits the thin-walled surface, with obvious dynamic damping effects.
Said adaptive damping includes both the dynamic damping applied by the polymeric or elastomeric material of the said liner on the thin wall, and the energy absorbed by the damping cavity of the pneumatic element (Total Loss-Coefficient: Cd≧0.1, see below and
More than an individual fixture, this invention presents an adaptive fixture design approach for thin-walled shell/cylindrical components, for the purpose of enabling them to be machined with sufficient supporting rigidity and dynamic stability, so as to maintain the machining precision and surface finish to an acceptable engineering standard.
The fixture is particularly adapted to thin-walled structures, and of these airplane jet engine casings and rocket nose cones are typical examples. Indeed, the invention further provides a combination of a fixture as defined above and a thin-walled shell/cylindrical component secured in the fixture. Preferably, said component is an airplane jet engine casing or a rocket nose cone.
Embodiments of the invention are further described hereinafter, by way of example, with reference to the accompanying drawings and figures, in which:
In
A thick-walled rigid arbour or column 5 is fixed centrally of the base 1 by bolts (not shown). The arbour 5 terminates with a flange to connect to a thick-walled lid 12. Two modified vehicle-wheel inner tubes 8, having an internal radius R corresponding with the radius of the arbour 5, are fitted on the arbour. Being made of elastomeric, resiliently flexible material, the tubes 8 can be inflated to fit the enclosure confined within the cylindrical component 10, support arbour 5, mounting base 1 and lid 12. Each tube 8 has its own air inlet valve 9 on its inner surface, and this is fitted through a respective aperture provided for this purpose on the arbour 5. Each inlet valve 9 is extendable upwardly through the arbour, which is hollow.
A multi-layered sacrificial liner 6 comprises 3 to 5 sheets of polymeric or elastomeric material adhered to each other and wrapped around the tubes 8, having a total thickness ≧10 mm, whereby penetrating tool movements through the cylindrical component 10 during a machining operation do not penetrate the pressure element 8. Meanwhile, the liner spreads a uniform supporting pressure, mainly through the shear effects between layers, and provides a dynamic damping, mainly through the polymeric or elastomeric material, normal to the component surface to be machined. Regional enhancements around minor openings (not shown) are employed by inserting curled nylon sheet 7 inside the outer layer of the liner, against the thin wall to be machined.
The lid 12 is a thick-walled circular plate provided with a wedged step (not shown) around its circumference to hold the top end of the cylindrical component. Lid 12 also is provided with holes 11 by which it can be attached to the top end of the internal arbour 5 by bolts (not shown).
In
A multi-layered sacrificial liner 6′ is also wrapped around the tubes 8 internally, against the external surface of component 10. Regional enhancements around the minor openings are employed by inserting curled nylon sheet 7′ inside the inner layer of the liner 6′, against the thin wall to be machined.
The circular lid 12′ is fixed on the top end of the external cylinder 5′, with a wedged step 38 around its circumference to hold the top end of the component 10 and form an enclosure confined within the cylindrical component 10, supporting cylinder 5′, mounting base 1′ and lid 12′, for the inflatable pneumatic tubes 8′.
Illustrated in
A multi-layered sacrificial liner 6″ is also wrapped around the tubes 8 externally, against the internal surface of the shell component 10 for external machining. Regional enhancements around the minor openings are employed by inserting curled nylon sheet 7 inside the outer layer of the liner 6″, against the thin wall to be machined.
In
A multi-layered sacrificial liner 6′″ is also wrapped around the tubes 8′″ internally, against the external surface of the shell component 10′″ for internal machining. Regional enhancements around the minor openings are employed by inserting curled nylon sheet 7 inside the inner layer of the liner 6′″, against the thin wall to be machined.
Component 10 in the drawings, (and hereafter use of a numeral includes its equivalent structure 10′,10″,10′″) may comprise a rocket shell or a jet engine casing. Most rough parts of thin-walled rocket shell or jet engine casings are monolithic castings or forgings from difficult-to-machine material, such as heat-resistant alloy. There is always a very strict requirement on reducing unnecessary component mass to a minimum. In order to provide all the precise interfaces for connection, as well as to remove all the unnecessary mass from the forging or casting part to get a finished component, machining work is inevitable. By applying an adaptive fixture of the type illustrated in
The internal supporting arbour or external supporting cylinder 5 plays a key role in sustaining sufficient supporting rigidity and dynamic stability to the thin-wall. The thin-walled shell/cylindrical components 10 are mainly balanced by the stretching and bending stresses and lack of shear effects to maintain a global rigidity. Therefore, the arbour or cylinder 5 is made as thick-walled as defined above. With this rigid support, the pneumatic element 8 applies a uniform normal pressure through the multi-layered liner 6 onto the thin wall and adaptively fits the thin-walled surface with dynamic damping effects.
Said adaptive damping includes both the dynamic damping applied by the polymeric or elastomeric material of the said liner 6 on the thin wall, and the energy absorbed by the damping cavity of the pneumatic element 8. Validation of this adaptive damping effect is explored below with reference to
Vibration-Amplitude-Ratio between the thin-walled component 10 with fixture shown in
corresponding to the respective inflation pressures 0.0, 1.0 and 2.0 Bar. Increase of the Supporting-Rigidity-Ratio from a transitional stage
up to a stable stage (identified with the elliptic hysteretic loop 22, as stated below)
demonstrates the effectiveness of the adaptive fixture in support of the thin-walled component 10. As a validation criterion, the Supporting-Rigidity-Ratio should be in the range of Kd≧3.0, for all the thin-walled shell/cylindrical components with the fixture applied, as defined.
Also from
Loss-Coefficient Cd is a general measure for complicated damping effects from engineering structures or materials, statistically, for general thin-walled metallic structure, Cd≦0.001, and for thin-walled metallic structure with adhered polymeric or elastomeric damping layer, 0.01≦Cd≦0.1. As a validation criterion on the effectiveness of the adaptive fixture related to this invention, Loss-Coefficient should be in the range of Cd≧0.1, for all the thin-walled shell/cylindrical components with the fixture applied, as defined.
More than an individual fixture, this invention presents an adaptive fixture design approach for thin-walled shell/cylindrical components, for the purpose of enabling them to be machined with sufficient supporting rigidity and dynamic stability, so as to maintain the machining precision and surface finish to an acceptable engineering standard.
Design and validation procedure of the adaptive fixture for different sized thin-walled shell/cylindrical components 10, as defined with the invention, is concluded below:
(1). Confirmation of the thin-walled 10 and thick-walled 5 components.
(2). Validation of dynamic stability and adaptive damping of the thin-walled components 10, with adaptive fixture applied.
(3). Validation of adaptive supporting rigidity: See
Although described above in relation to thin-walled components, the fixture of the present invention is not limited thereto but can be applied to thick-walled components with advantage. Not only is the fixture adaptive in the sizes of component it can accommodate, but also it is adaptive in its vibration damping characteristic by virtue of the pneumatic pressure.
Throughout the description and claims of this specification, the words “comprise” and “contain” and variations of the words, for example “comprising” and “comprises”, means “including but not limited to”, and is not intended to (and does not) exclude other moieties, additives, components, integers or steps.
Throughout the description and claims of this specification, the singular encompasses the plural unless the context otherwise requires. In particular, where the indefinite article is used, the specification is to be understood as contemplating plurality as well as singularity, unless the context requires otherwise.
Features, integers, characteristics, compounds, chemical moieties or groups described in conjunction with a particular aspect, embodiment or example of the invention are to be understood to be applicable to any other aspect, embodiment or example described herein unless incompatible therewith.
The reader's attention is directed to all papers and documents which are filed concurrently with or previous to this specification in connection with this application and which are open to public inspection with this specification, and the contents of all such papers and documents are incorporated herein by reference.
All of the features disclosed in this specification (including any accompanying claims, abstract and drawings), and/or all of the steps of any method or process so disclosed, may be combined in any combination, except combinations where at least some of such features and/or steps are mutually exclusive.
Each feature disclosed in this specification (including any accompanying claims, abstract, drawings and testing results), may be replaced by alternative features serving the same, equivalent or similar purpose, unless expressly stated otherwise. Thus, unless expressly stated otherwise, each feature disclosed is one example only of a generic series of equivalent or similar features.
The invention is not restricted to the details of any foregoing embodiments. The invention extends to any novel one, or any novel combination, of the features disclosed in this specification (including any accompanying claims, abstract and drawings), or to any novel one, or any novel combination, of the steps of any method or process so disclosed.
| Number | Date | Country | Kind |
|---|---|---|---|
| GB0704298.9 | Mar 2007 | GB | national |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 12529834 | Mar 2010 | US |
| Child | 14223076 | US |
