The disclosure relates generally to damping vibration in a turbomachine nozzle or blade. Further, the disclosure relates to a vibration damping system including a vibration damping element including a volute spring within a body opening in the turbomachine nozzle or blade.
One concern in turbine operation is the tendency of the turbine blades or nozzles to undergo vibrational stress during operation. In many installations, turbines operate under conditions of frequent acceleration and deceleration. During acceleration or deceleration of the turbine, the airfoils of the blades are, momentarily at least, subjected to vibrational stresses at certain frequencies and in many cases to vibrational stresses at secondary or tertiary frequencies. Nozzle airfoils experience similar vibrational stress. Variations in gas temperature, pressure, and/or density, for example, can excite vibrations throughout the rotor assembly, especially within the nozzle or blade airfoils. Gas exiting upstream of the turbine and/or compressor sections in a periodic, or “pulsating,” manner can also excite undesirable vibrations. When an airfoil is subjected to vibrational stress, its amplitude of vibration can readily build up to a point which may negatively affect gas turbine operations or component life.
All aspects, examples and features mentioned below can be combined in any technically possible way.
An aspect of the disclosure provides a vibration damping element for a vibration damping system for a turbomachine nozzle or blade, the vibration damping element comprising: a volute spring vibration damping element configured to be mounted within a body opening in the turbomachine nozzle or blade, the volute spring vibration damping element including a spiral coil of a metal sheet strip with a surface of the metal sheet strip contacting itself in a direction of an axis of the spiral coil; wherein the body opening has an inner dimension and the volute spring vibration damping element has an outer dimension sized to frictionally engage the inner dimension of the body opening to dampen vibration.
Another aspect of the disclosure includes any of the preceding aspects, and the body opening and the volute spring vibration damping element each have a conical perspective shape along at least a portion of respective lengths thereof.
Another aspect of the disclosure includes any of the preceding aspects, and the surface of the metal sheet strip frictionally engages with itself to dampen vibration.
Another aspect of the disclosure includes any of the preceding aspects, and the body opening extends through a body of the turbomachine nozzle or blade between a tip end and a base end thereof; and wherein the volute spring vibration damping element has a first, free end and a second end fixed relative to one of the base end and the tip end.
Another aspect of the disclosure includes any of the preceding aspects, and the second end of the volute spring vibration damping element is fixed relative to the tip end of the body of the turbomachine nozzle or blade, and the first, free end extends towards the base end.
Another aspect of the disclosure includes any of the preceding aspects, and the second end of the volute spring vibration damping element is fixed relative to the base end of the body of the turbomachine nozzle or blade, and the first, free end extends towards the tip end.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element and the body opening having mating circular cross-sectional shapes.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element and the body opening having mating oblong cross-sectional shapes.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element and the body opening having mating non-circular cross-sectional shapes.
Another aspect of the disclosure relates to a turbomachine nozzle or blade having a vibration damping system, the turbomachine nozzle or blade comprising: a body opening extending through a body of the turbomachine nozzle or blade between a tip end and a base end thereof; and a vibration damping element disposed in the body opening, the vibration damping element including a volute spring vibration damping element configured to be mounted within the body opening, the volute spring vibration damping element including a spiral coil of a metal sheet strip with a surface of the metal sheet strip contacting itself in a direction of an axis of the spiral coil; wherein the body opening has an inner dimension and the volute spring vibration damping element has an outer dimension sized to frictionally engage the inner dimension of the body opening to dampen vibration.
Another aspect of the disclosure includes any of the preceding aspects, and the body opening and the volute spring vibration damping element each have a conical perspective shape along at least a portion of respective lengths thereof.
Another aspect of the disclosure includes any of the preceding aspects, and the surface of the metal sheet strip frictionally engages with itself to dampen vibration.
Another aspect of the disclosure includes any of the preceding aspects, and wherein the volute spring vibration damping element has a first, free end and a second end fixed relative to one of the base end and the tip end.
Another aspect of the disclosure includes any of the preceding aspects, wherein a fixture member is secured to the second end of the volute spring vibration damping element to prevent the volute spring vibration damping element from rotating within the body opening and from pulling away from the fixture member.
Another aspect of the disclosure includes any of the preceding aspects, and the second end of the volute spring vibration damping element is fixed relative to the tip end of the body of the turbomachine nozzle or blade, and the first, free end extends towards the base end.
Another aspect of the disclosure includes any of the preceding aspects, and the second end of the volute spring vibration damping element is fixed relative to the base end of the body of the turbomachine nozzle or blade, and the first, free end extends towards the tip end.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element and the body opening having mating circular cross-sectional shapes.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element and the body opening having mating non-circular cross-sectional shapes.
Another aspect of the disclosure includes a method of installing a vibration damping element in a body opening in a turbomachine nozzle or blade, the method comprising: coiling a volute spring vibration damping element to a coiled position from a free position to reduce an outer dimension of the volute spring vibration damping element from a first outer dimension to a second, smaller outer dimension, the volute spring vibration damping element including a spiral coil of a metal sheet strip with a surface of the metal sheet strip contacting itself in a direction of an axis of the coil; positioning the volute spring vibration damping element in the coiled position within the body opening in the turbomachine nozzle or blade, the body opening having an inner dimension; and releasing the volute spring vibration damping element in the body opening such that a third outer dimension of the volute spring vibration damping element frictionally engages the inner dimension of the body opening, whereby the volute spring vibration damping element dampens vibration during operation of the turbomachine nozzle or blade.
Another aspect of the disclosure includes any of the preceding aspects, and the volute spring vibration damping element has a first end and a second end, and the body opening extends through a body of the turbomachine nozzle or blade between a tip end and a base end thereof, and further comprising fixing the second end of the volute spring vibration damping element relative to one of the base end and the tip end of the turbomachine nozzle or blade.
Two or more aspects described in this disclosure, including those described in this summary section, may be combined to form implementations not specifically described herein.
The details of one or more implementations are set forth in the accompanying drawings and the description below. Other features, objects and advantages will be apparent from the description and drawings, and from the claims.
These and other features of this disclosure will be more readily understood from the following detailed description of the various aspects of the disclosure taken in conjunction with the accompanying drawings that depict various embodiments of the disclosure, in which:
It is noted that the drawings of the disclosure are not necessarily to scale. The drawings are intended to depict only typical aspects of the disclosure and therefore should not be considered as limiting the scope of the disclosure. In the drawings, like numbering represents like elements between the drawings.
As an initial matter, in order to clearly describe the subject matter of the current disclosure, it will become necessary to select certain terminology when referring to and describing relevant machine components within a turbine. To the extent possible, common industry terminology will be used and employed in a manner consistent with its accepted meaning. Unless otherwise stated, such terminology should be given a broad interpretation consistent with the context of the present application and the scope of the appended claims. Those of ordinary skill in the art will appreciate that often a particular component may be referred to using several different or overlapping terms. What may be described herein as being a single part may include and be referenced in another context as consisting of multiple components. Alternatively, what may be described herein as including multiple components may be referred to elsewhere as a single part.
In addition, several descriptive terms may be used regularly herein, and it should prove helpful to define these terms at the onset of this section. It is often required to describe parts that are disposed at different radial positions with regard to a center axis. The term “radial” refers to movement or position perpendicular to an axis. For example, if a first component resides closer to the axis than a second component, it will be stated herein that the first component is “radially inward” or “inboard” of the second component. If, on the other hand, the first component resides further from the axis than the second component, it may be stated herein that the first component is “radially outward” or “outboard” of the second component. The term “axial” refers to movement or position parallel to an axis. Finally, the term “circumferential” refers to movement or position around an axis. It will be appreciated that such terms may be applied in relation to the center axis of the turbomachine.
In addition, several descriptive terms may be used regularly herein, as described below. The terms “first,” “second,” and “third” may be used interchangeably to distinguish one component from another and are not intended to signify location or importance of the individual components.
The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the disclosure. As used herein, the singular forms “a,” “an,” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms “comprises” and/or “comprising,” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. “Optional” or “optionally” means that the subsequently described event or circumstance may or may not occur or that the subsequently described component or element may or may not be present, and that the description includes instances where the event occurs or the component is present and instances where it does not or is not present.
Where an element or layer is referred to as being “on,” “engaged to,” “connected to” or “coupled to” another element or layer, it may be directly on, engaged to, connected to, or coupled to the other element or layer, or intervening elements or layers may be present. In contrast, when an element is referred to as being “directly on,” “directly engaged to,” “directly connected to” or “directly coupled to” another element or layer, there are no intervening elements or layers present. Other words used to describe the relationship between elements should be interpreted in a like fashion (e.g., “between” versus “directly between,” “adjacent” versus “directly adjacent,” etc.). As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items.
Embodiments of the disclosure provide vibration damping systems including a vibration damping element for a turbomachine nozzle (stationary vane) or blade (rotating blade). The systems may include a body opening extending through a body of the turbomachine nozzle or blade between the tip end and the base end thereof, e.g., through the airfoil among potentially other parts of the nozzle or blade. A vibration damping element includes a volute spring vibration damping element configured to be mounted within the body opening in the turbomachine nozzle or blade. The volute spring vibration damping element includes a spiral coil of a metal sheet strip with a surface of the metal sheet strip contacting itself generally in a direction of an axis of the coil. The body opening has an inner dimension and the volute spring vibration damping element has an outer dimension sized to frictionally engage the inner dimension of the body opening to dampen vibration.
In certain embodiments, the body opening and the volute spring vibration damping element each have a conical perspective shape along at least a portion of respective lengths thereof. The volute spring vibration damping element may be fixed at one end relative to the body opening. The vibration damping element reduces nozzle or blade vibration with a simple arrangement and does not add much extra mass to the nozzle or blade so that it generates low additional G-forces during use. Accordingly, the vibration damping element does not increase centrifugal force to the nozzle base end or blade tip end or require a change in nozzle or blade configuration. The vibration damping element is easily installed.
Referring to the drawings,
GT system 100 may be a 7HA.03 engine, commercially available from General Electric Company, Greenville, S.C. However, the present disclosure is not limited to any one particular GT system and may be implemented in connection with other engines including, for example, the other HA, F, B, LM, GT, TM and E-class engine models of General Electric Company and engine models of other companies. More importantly, the teachings of the disclosure are not necessarily applicable to only nozzles or blades for a turbine in a GT system, and may be applied to practically any type of industrial machine or other turbomachine, e.g., steam turbines, jet engines, compressors (as in
A plurality of stationary turbine vanes or nozzles 112 (hereafter “nozzle 112,” or “nozzles 112”) may cooperate with a plurality of rotating turbomachineblades 114 (hereafter “blade 114,” or “blades 114”) to form each stage L0-L3 of turbine 108 and to define a portion of a working fluid path through turbine 108. Blades 114 in each stage are coupled to rotor 110 (
With reference to
Referring to
It will be appreciated that airfoil 134 in nozzle 112 and blade 114 is the active component of the nozzle 112 or blade 114 that intercepts the flow of working fluid and, in the case of blades 114, induces rotor 110 (
During operation of a turbine, nozzles 112 or blades 114 may be excited into vibration by a number of different forcing functions. For example, variations in working fluid temperature, pressure, and/or density can excite vibrations throughout the rotor assembly, especially within the airfoils and/or tips of the blades 114 or nozzles 112. Gas exiting upstream of the turbine section in a periodic, or “pulsating,” manner can also excite undesirable vibrations. The present disclosure reduces the vibration of a stationary turbomachine nozzle 112 or rotating turbomachine blade 114 without significant change of nozzle or blade design.
Body opening 160 may be defined in any part of any structure of body 128. For example, where body 128 includes an internal partition wall (not shown), for example, for defining a cooling circuit therein, body opening 160 may be defined as an internal cavity in the partition wall in body 128. Body opening 160 generally extends radially in body 128. However, some angling, and perhaps curving, of body opening 160 relative to a radial extent of body 128 is possible. Body opening 160 has an inner surface 162. Body opening 160 may be formed using any now known or later developed technique, e.g., additive manufacturing during formation of nozzle or blade 112, 114, or drilling into an existing nozzle or blade 112, 114.
As shown for example in
Vibration damping system 120 for nozzles 112 or blades 114 may include a vibration damping element 166 disposed in body opening 160. Vibration damping element 166 may include a volute spring vibration damping element 170 (herein “volute spring 170”) within body opening 160 in turbomachine nozzle 114 or blade 114.
As shown in
More particularly, an outer surface 1780 of a coil of metal sheet strip 174 contacts an inner surface 1781 of another coil of metal sheet strip 174 as the sheet coils in a longitudinal direction, i.e., along an axis A of volute spring 170. Surfaces 178 of volute spring 170 contact each other and rub together, i.e., frictionally engage, during motion of nozzle 112 or blade 114 to dampen vibration. The coiling of volute spring 170 stores energy in the metal sheet strip 174 in a manner that the strip wants to uncoil to a relaxed state, which stores axially directed energy and radially outward directed energy. While a volute spring is typically used as a compression spring, i.e., under compression, the coils provide a reactive axial force, and it will be recognized that volute spring 170 is not necessarily employed for its reactive axial force. Rather, volute spring 170 is employed for its surface frictional engagement and for its radially outward reactive force. In the latter case, volute spring 170, as any volute spring, wants to uncoil to a relaxed state, which naturally creates a radially outward force. The radially outward force allows volute spring 170 to frictionally engage inner surface 162 of body opening 160 to further dampen vibration.
As shown in
Body opening 160 has inner surface 162 having an inner dimension ID and volute spring 170 has an outer dimension OD sized to frictionally engage inner dimension ID of body opening 160 to dampen vibration during motion of nozzle 112 or blade 114. That is, the outer dimension OD of volute spring 170 rubs against, i.e., frictionally engages, inner surface 162 of body opening 160 to dampen vibration, e.g., during movement of airfoil 134 of nozzle 112 or blade 114. In certain embodiments, as shown best in
Body opening 160 extends through body 128 of turbomachine nozzle or blade 112, 114 between tip end 132 and base end 130 thereof. Body opening 160 has an inner surface 162 and a closed end 164. As shown in
In
Closure and fixing members 176, 196 may include any now known or later developed structure to fixedly couple second end 182 of volute spring 170 relative to base end 130 or tip end 132 in body opening 160, e.g., a plate with a fastener, threaded fastener, or a weld. In one example, closure and fixing members 176, 196 may fix second end 182 of volute spring 170 from rotating within body opening 160, and from pulling away from closure and fixing members 176, 196 toward tip end 132 of nozzle or blade 112, 114. Closure and fixing members 176, 196 also set a limit of expansion of second end 182 of volute spring 170 within body opening 160. In an alternative embodiment, volute spring 170 may have a second end 182 that is not fully fixed. In this case, closure and fixing members 176, 196 do not fully fix second end 182, e.g., from rotating or pulling way, but simply abut it to define an extent of axial expansion of volute spring 170.
Regarding the cross-sectional shapes of volute spring 170 and body opening 160, in one example shown in
Alternately, other non-circular, mating cross-sectional shapes are also possible such as but not limited to oval or otherwise oblong; or polygonal such as square, rectangular, pentagonal; etc.
Regardless of cross-sectional shape, body opening 160 has a cross-sectional shape along its axial length L to mate with the cross-sectional shape of volute spring 170. A cross-sectional shape of body opening 160 may decrease in at least one dimension along its length to accommodate the corresponding decreasing dimensions of volute spring 170 along its axial length L. For example, as shown in
Metal sheet strip 174 of volute spring 170 may have any thickness sufficient to provide the desired vibration damping movement and requisite strength. In one non-limiting example, metal sheet strip 174 of volute spring 170 may have a thickness T (
During operation of turbomachine nozzle 112 or blade 114, vibration damping element 166 of vibration damping system 120 operates with tip end 132, i.e., of airfoil 134, driving relative motion with base end 130 of nozzle 112 or blade 114. Here, vibration damping system 120 allows vibration damping via the relative motion through the deflection of tip end 132 and frictional engagement of volute spring 170 with itself and/or inner surface 162 of body opening 160. In the
The vibration damping system 120 can be customized in a number of ways including, but not limited to: the size, coating(s), thickness(es), and material(s) of metal sheet strip 174 of volute spring 170; the number of coils of volute spring 170; the shape of coils of volute spring 170; the amount of radial force exerted by volute spring 170; and amount of axial overlap of surfaces 178 of volute spring 170 as controlled by, for example, the axial length of volute spring 170 (
According to various embodiments, a method of damping vibration in turbomachine nozzle 112 or blade 114 during operation of turbomachine nozzle 112 or blade 114 may include providing various levels of different vibration damping. For example, a method may dampen vibration by deflection of volute spring 170 disposed radially in body opening 160 and extending between tip end 132 and base end 130 of body 128 of turbomachine nozzle 112 or blade 114. As noted, volute spring 170 may include first, free end 180 and second, fixed end 182 fixed relative to base end 130 or tip end 132 of body 128. The method may also dampen vibration by frictional engagement of surfaces 178 of volute springs 170 with each other and/or with inner surface 162 of body opening 160. The surface contact of surfaces 178 of volute springs 170 creates friction, thus dissipating the input energy from the vibration. The frictional forces may also restrict motion of volute spring 170, thus reducing displacement. For rotating blades 114, damping of vibration by frictional engagement may be increased compared to nozzle 112 based on the centrifugal force increasing a force of frictional engagement of surfaces 178 of volute spring 170 with each other and/or with inner surface 162 of body opening 160.
It will be apparent that some embodiments described herein are applicable mainly to rotating turbomachine blades 114 that experience centrifugal force during operation and thus that may require certain structure to maintain high performance vibration damping. That said, any of the above-described embodiments can be part of a turbomachine nozzle 112 or blade 114.
Embodiments of the disclosure provide vibration damping element(s) 166 including volute spring vibration damping element 170 to reduce nozzle 112 or blade 114 vibration with a simple arrangement. Vibration damping system 120 does not add much extra mass to nozzle(s) 112 or blade(s) 114, and so it does not add additional centrifugal force to a blade tip end or require a change in nozzle or blade configuration. Moreover, the presence of vibration damping system 120 can reduce stresses on nozzle 112 or blade 114, thereby extending the useful life of such components. The vibration damping element 170 reduces nozzle or blade vibration with a simple arrangement, which is easily installed. The vibration damping element 170 is lightweight and does not add much extra mass to the nozzle or blade so that it generates low additional G-forces during use. The vibration damping system 120 may be applied to new nozzles or blades, or may be retrofitted by, for example, drilling a new body opening 160 therein.
Approximating language, as used herein throughout the specification and claims, may be applied to modify any quantitative representation that could permissibly vary without resulting in a change in the basic function to which it is related. Accordingly, a value modified by a term or terms, such as “about,” “approximately” and “substantially,” is not to be limited to the precise value specified. In at least some instances, the approximating language may correspond to the precision of an instrument for measuring the value. Here and throughout the specification and claims, range limitations may be combined and/or interchanged; such ranges are identified and include all the sub-ranges contained therein unless context or language indicates otherwise. “Approximately,” as applied to a particular value of a range, applies to both end values and, unless otherwise dependent on the precision of the instrument measuring the value, may indicate +/−10% of the stated value(s).
The corresponding structures, materials, acts, and equivalents of all means or step plus function elements in the claims below are intended to include any structure, material, or act for performing the function in combination with other claimed elements as specifically claimed. The description of the present disclosure has been presented for purposes of illustration and description but is not intended to be exhaustive or limited to the disclosure in the form disclosed. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the disclosure. The embodiment was chosen and described to best explain the principles of the disclosure and the practical application and to enable others of ordinary skill in the art to understand the disclosure for various embodiments with various modifications as are suited to the particular use contemplated.