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    • 专利摘要:
    The present invention relates to the limitation of the flow of gas in a marine acoustic vibrator (100) in order to compensate for the effects of a gas spring. One embodiment provides a marine acoustic vibrator (100), comprising: an outer casing (104); and a variable gas flow limiter (102) disposed within the outer shell (104), the marine acoustic vibrator (100) having a resonant frequency that can be selected at least in part based on the limiter variable gas flow (102). Figure for the abstract: Fig. 4.
    公开号:FR3082953A1
    申请号:FR1906897
    申请日:2019-06-25
    公开日:2019-12-27
    发明作者:Rune Lennart Tenghamn Stig；David Snodgrass Jonathan；Carl Fredrik LÖFGREN Bo；Karl-Henrik Ryttersson
    申请人:PGS Geophysical AS；
    IPC主号:
    专利说明:

    Description
    Title of the invention: MARINE ACOUSTIC VIBRATOR WITH GAS SPRING COMPENSATION Technical Field [0001] The present invention relates generally to acoustic vibrators for marine seismic research. More particularly, embodiments relate to limiting the flow of gas in a marine acoustic vibrator in order to compensate for gas spring effects.
    PRIOR ART [0002] Sound sources are generally devices which generate acoustic energy. One use of sound sources is in marine seismic research in which sound sources can be used to generate acoustic energy that travels down through water and into rock below the surface. After interaction with the rock below the surface, for example at the boundaries between different layers below the surface, part of the acoustic energy can be returned to the surface of the water and be detected by specialized sensors. The energy detected can be used to deduce certain properties of the rock below the surface, such as structure, mineral composition and fluid content, thereby providing information useful in the recovery of hydrocarbons.
    Most sound sources used today in marine seismic research are of the pulse type, in which efforts are made to generate as much energy as possible in as short a time as possible. The most commonly used of these pulse type sources are pneumatic cannons which typically use compressed air to generate a sound wave. Other examples of pulse type sources include explosives and weight drop pulse sources. Another type of sound source that can be used in seismic research includes marine acoustic vibrators, such as hydraulically operated sources, electromechanical vibrators, electric marine acoustic vibrators, and sources using piezoelectric or magnetostrictive material. Vibrator sources typically generate vibrations over a frequency range in a configuration known as "sweep" or "chirp" ("compression-expansion").
    [0004] Earlier sound sources for use in marine seismic research have typically been designed for relatively high frequency operation (for example above 10 Hz). However, it is well known that when sound waves travel through water and through geological structures below the surface, higher frequency sound waves can fade faster than lower frequency sound waves. , and therefore lower frequency sound waves can be transmitted over longer distances through water and geological structures than higher frequency sound waves. Thus, efforts have been made to develop sound sources which can operate at low frequencies. Marine acoustic vibrators that can have at least a resonant frequency of about 10 Hz or less have been developed. In order to obtain a given level of output to water, these marine acoustic vibrators typically have to undergo a change in volume. In order to operate at depth while minimizing structural weight, the marine acoustic vibrator can be pressure balanced with external hydrostatic pressure. When the internal gas (for example air) in the source increases in pressure, the compressibility module of the internal gas also increases. This increase in the compressibility module or “gas spring” thus tends to make the stiffness of the internal gas a function of the operating depth of the source. In addition, the stiffness of the structure and the internal gas are the main determining factors in the frequency of the resonance of the source. Consequently, the resonance of the marine acoustic vibrator can vary with depth, particularly in vibrators where the internal volume of the source can be balanced in pressure with the external hydrostatic pressure.
    Disclosure of the invention In order to solve the problems of the prior art, the present invention provides, in a first aspect, a marine acoustic vibrator which comprises an outer casing, a variable gas flow limiter disposed at the inside the outer envelope, the marine acoustic vibrator having a resonant frequency which can be selected at least in part on the basis of the variable gas flow limiter.
    The marine acoustic vibrator may further include a drive device disposed at least partially inside the outer casing and connected to it, which drive device may include an electrodynamic drive device. The marine acoustic vibrator can have at least two resonant frequencies of about 10 Hz or less when immersed in water at a depth of about 0 meters to about 300 meters.
    The variable gas flow limiter may include a first plate having holes, and a second plate having holes, the second plate being movable so as to at least partially cover the holes in the first plate. The variable gas flow restrictor may have an open position and a closed position, the holes in the first plate being at least partially obstructed by the second plate in the closed position, and the holes in the first plate and the holes in the second plate being aligned in the open position for maximum gas flow through the variable gas flow limiter. The variable gas flow limiter can be attached to a frame in the marine acoustic vibrator, the frame being connected to the outer casing.
    The marine acoustic vibrator may further include a frame connected to the flexion-extension envelope, the drive device having a first end fixed to the outer envelope and a second end fixed to the frame. It may further include a spring connected to the outer casing, and masses attached to the spring.
    According to a second aspect, the present invention provides a marine acoustic vibrator which comprises an external flexion-extension envelope, a frame connected to the external flexion-extension envelope, a drive device having a first end and a second end, the first end being fixed on the external flexion-extension envelope, and the second end being fixed on the frame, a gas spring being provided with a mass in order to generate a first resonant frequency, and the value of gas spring being changed by limiting the flow of gas through the marine acoustic vibrator to thereby control the first depth resonance frequency.
    The marine acoustic vibrator can have at least two resonant frequencies of about 10 Hz or less when it is immersed in water to a depth of about 0 meters to about 300 meters. It may further include a gas flow limiter disposed inside the outer casing. The variable gas flow restrictor may include a first plate having holes, and a second plate having holes, the second plate being movable to at least partially cover the holes in the first plate. The variable gas flow restrictor may have an open position and a closed position, the holes in the first plate being at least partially obstructed by the second plate in the closed position, and the holes in the first plate and the holes in the second plate being aligned in the open position for maximum gas flow through the variable gas flow limiter. The variable gas flow restrictor can be attached to the frame.
    Finally, the present invention provides, in a third aspect, a method which comprises towing an acoustic vibrator in an expanse of water, triggering the acoustic vibrator in order to generate acoustic energy in the expanse of water, to limit a flow of gas in the acoustic vibrator in order to control a first resonant frequency of the acoustic vibrator, and to detect acoustic energy coming from the acoustic vibrator.
    The acoustic vibrator can be towed to a first depth of about 0 meters to about 300 meters. The method may further include towing the acoustic vibrator to a second depth, the flow of gas being limited in the acoustic vibrator when it is towed to the first depth such that the first resonant frequency of the acoustic vibrator is substantially constant when a towing depth varies from the first depth to the second depth. Limiting the flow of gas through the vibrator can include moving a plate to at least partially block holes in another plate.
    The method may further include opening a variable gas flow limiter to allow increased gas flow in the acoustic vibrator when the acoustic vibrator is towed through the body of water. It may also include increasing a gas pressure inside the envelope of the acoustic vibrator in order to equalize the gas pressure inside the envelope with the water pressure at depth. It may also include producing a product of geophysical data from the detected acoustic energy indicative of certain rock properties below the surface below the body of water.
    The accompanying drawings illustrate certain aspects of certain embodiments of the present invention and should not be used to limit or define the invention. Brief description of the drawings [fig-1] Figures 1 and 2 illustrate the effect of the gas spring when the marine acoustic vibrator is towed more deeply according to exemplary embodiments.
    [Fig.2] Figures 1 and 2 illustrate the effect of the gas spring when the marine acoustic vibrator is towed more deeply according to exemplary embodiments.
    [Fig.3] Figure 3 is a simulated amplitude spectrum showing the expected effect of compressed gas which generates a gas spring when the marine acoustic vibrator is towed deeper according to exemplary embodiments.
    [Fig.4] Figure 4 illustrates an exemplary embodiment of a marine acoustic vibrator with a variable gas flow limiter.
    [Fig.5] Figure 5 illustrates an exemplary embodiment of a variable gas flow limiter for use with a marine acoustic vibrator.
    [Fig.6] Figure 6 illustrates an exemplary embodiment of a marine acoustic vibrator with a variable gas flow limiter in section.
    [Fig.7] Figure 7 illustrates another exemplary embodiment of a marine acoustic vibrator with a variable gas flow limiter in section.
    [Fig-8] Figure 8 illustrates yet another exemplary embodiment of a marine acoustic vibrator with a variable gas flow limiter in section.
    [Fig.9] Figure 9 is a top view of the marine acoustic vibrator of Figure 8 according to exemplary embodiments.
    [Fig. 10] Figures 10 and 11 are plots of amplitude spectrum with respect to frequency for an example marine acoustic vibrator at 10 meters and 100 meters, respectively, according to embodiments of 'example.
    [Fig.l 1] Figures 10 and 11 are plots of amplitude spectrum relative to the frequency for an example marine acoustic vibrator at 10 meters and 100 meters, respectively, according to embodiments example.
    [Fig. 12] Figure 12 illustrates an exemplary embodiment of a marine acoustic vibrator according to exemplary embodiments.
    [Fig. 13] Figure 13 is an exemplary embodiment of a marine study seismic system using an acoustic vibrator.
    Description of the embodiments It is obvious that the present description is not limited to particular devices or methods, which can of course vary. It is also obvious that the terminology used here is intended to describe particular embodiments only, and is not intended to be limiting. All numbers and ranges described here may vary to some extent. Whenever a numeric range with a lower limit and an upper limit is described, any number and any included range falling within the range are specifically disclosed. Although individual embodiments are discussed, the invention covers all combinations of all of these embodiments. As used herein, the singular forms "one", "one", "the" and "the" refer to configurations where one or more of the targeted elements are present, unless the content clearly requires otherwise . The term "may" is used in this description with a broad meaning (that is, having the potential for, being capable of) and not a strict meaning (that is, must). The term "includes" and its derivatives means "including, but not limited to". The term "connected" means connected directly or indirectly. If there is any conflict in the uses of a word or term in this description, the definitions which are related to this description must be adopted for the understanding of this invention.
    The embodiments relate generally to acoustic vibrators for marine seismic research. More particularly, in one or more embodiments, a gas flow can be limited in a marine acoustic vibrator in order to compensate for gas spring effects. As discussed in more detail below, the flow of gas through the marine acoustic vibrator can be limited to make the gas spring more or less stiff to thereby control the first depth resonant frequency.
    Acoustic vibrators can be used in marine seismic research to generate acoustic energy that travels down through water and down into the earth. Embodiments of marine acoustic vibrators may include an outer shell which contains pressurized gas. For example, a marine acoustic vibrator can include an external envelope which defines an internal volume in which a gas can be placed. The gas can be any gas or a combination of gases (by air, oxygen, nitrogen, carbon dioxide, etc.) which is chosen on the basis of the expected operational requirements of the device. A person skilled in the art having the benefit of this description is able to choose a gas or a combination of gases suitable for use in the marine acoustic vibrator. Examples of marine acoustic vibrators may include hydraulically actuated vibrators, electromechanical vibrators, electric marine acoustic vibrators, and vibrators using piezoelectric or magnetostrictive material. In certain embodiments, the marine acoustic vibrator can be a source of the flexionextension envelope type. Flex-extension devices including actuators and transducers act as mechanical transformers, which transform and amplify the displacement and force generated in the active element to meet the demands of different applications. Sources of the flexion-extension envelope type are generally marine acoustic vibrators having an external envelope which vibrates and flexes in order to generate acoustic energy. Examples of flexion-extension envelope type sources can be found in U.S. Patent No. 8,446,798.
    In some embodiments, the marine acoustic vibrator may have a pressure compensation system. The pressure compensation system can be used, for example, to equalize the internal gas pressure of the outer shell of the marine acoustic vibrator with the external pressure. The internal gas pressure of the outer shell of the marine acoustic vibrator is hereinafter called "gas pressure inside the shell". Pressure compensation can be used, for example, with marine acoustic vibrators, where the source must undergo a volume change to obtain a given output level. When the depth of the marine acoustic vibrator, the gas pressure inside the enclosure can be increased to equalize a pressure with the water pressure which increases due to the depth. Air or another suitable gas can be introduced into the outer shell of the vibrator, for example, to increase the internal gas pressure.
    However, increasing the gas pressure inside the enclosure can create a "gas spring" effect which affects the resonant frequency of the marine acoustic vibrator. In particular, the resonant frequency can increase as the gas pressure inside the envelope increases. The pressurized gas inside a marine acoustic vibrator may have a higher stiffness than that of the outer casing of the sound source in some embodiments. Those skilled in the art, with the benefit of this description, should appreciate the fact that an increase in the gas pressure inside the envelope can also result in an increase in the compressibility modulus (stiffness) of the gas (e.g. air) in the outer shell. Because the resonant frequency of the marine acoustic vibrator is based at least on the combination of the stiffness of the outer shell and the stiffness of the gas in the outer shell, this increase in compressibility modulus affects the resonant frequency. Thus, the resonant frequency of the marine acoustic vibrator can increase when the vibrator is towed to a greater depth.
    Figures 1 and 2 illustrate the effect of a gas spring (for example compressed air) on a deep marine acoustic vibrator according to exemplary embodiments. In FIG. 1, the internal envelope gas is represented by the reference 2. To illustrate the gas spring, the internal envelope gas 2 is represented in the neutral state at 4, is in compression at 6, and is in relaxation at 8. With regard to FIG. 2, the curve 10 is a hypothetical representation of the output of a marine acoustic vibrator at D meters without pressure compensation, while the curve represented at 12 represents the output of the acoustic vibrator sailor at D + x meters with pressure compensation. Pressure compensation means an increase in pressure and a resulting increase in the stiffness of the gas spring. As illustrated, the resonance of the marine acoustic vibrator moves upward with pressure compensation, thereby showing how a stiff gas spring can result in a higher resonant frequency.
    Figure 3 is a simulated amplitude spectrum from a finite element simulation showing the effect of the gas spring as a function of depth. The curves in Figure 3 represent the output of a marine acoustic vibrator towed to a variable depth with pressure compensation. In particular, the curves in Figure 3 represent the output of the marine acoustic vibrator towed at 0 meters, 50 meters, 100 meters, and 120 meters, respectively, shown at 14, 16, 18, and 20 in Figure 3. As this As illustrated, the increase in the resonant frequency may be more pronounced at greater depths, thereby indicating that the resonant frequency increases when the gas spring is made stiffer.
    According to the present embodiments, the gas spring can be controlled by limiting a flow of gas in the marine acoustic vibrator. As an example, a variable gas flow limiter can be placed inside the marine acoustic vibrator and can change the internal volume of gas to make the gas spring more or less stiff. Since the stiffness of the gas spring affects the resonant frequency, the gas spring can be changed to thereby control the resonant frequency. This may be particularly desirable with a marine acoustic vibrator which can be towed to different depths. In some embodiments, it may be desirable to have the resonant frequency which remains substantially constant (for example which varies by no more than 5%) regardless of the depth. However, as previously described, when the marine acoustic vibrator can be lowered into the water, the gas can be compressed by the pressure compensation system so that the gas spring can become stiffer at increasing depths . For example, a marine acoustic vibrator with a resonance of 2.5 Hz at 120 meters can have a much lower resonance at 50 meters. To compensate for this gas spring effect, the flow of gas through the marine acoustic vibrator can be limited to shallower depths to make the gas spring stiffer, thereby increasing the resonant frequency.
    In some embodiments, the marine acoustic vibrator may have at least one resonant frequency (when immersed in water at a depth of about 0 meters to about 300 meters) between about 1 Hz and about 200 Hz. In alternative embodiments, the marine acoustic vibrator may have at least one resonant frequency (when immersed in water) between about 0.1 Hz and about 100 Hz, alternatively, between about 0.1 Hz and approximately 10 Hz, and alternatively, between approximately 0.1 Hz and approximately 5 Hz. In a certain embodiment, the marine acoustic vibrator may have at least two resonant frequencies of approximately 10 Hz or less (when immersed in water). In some embodiments, the first resonant frequency can be controlled by limiting a flow of gas through the marine acoustic vibrator. In particular embodiments, the first resonant frequency can be increased by limiting the flow of gas through the marine acoustic vibrator. For example, the first resonant frequency can be controlled to be substantially constant regardless of the depth.
    FIG. 4 illustrates an exemplary embodiment of a marine acoustic vibrator 100 which comprises a variable gas limiter 102, for example, in order to limit a flow of gas, and thus compensate for the effects of a gas spring . In the illustrated embodiment, the marine acoustic vibrator 100 is a source of the flexion-extension envelope type. As illustrated, the marine acoustic vibrator 100 may include an outer casing 104, which can be closed, for example, by two side casing parts 106a, 106b. While not shown in Figure 4, the side casing parts 106a, 106b can be connected at or near the ends of their longer long axes by an appropriate connection mechanism, such as hinges . As illustrated, the marine acoustic vibrator 100 may further comprise one or more drive devices 108, which may be an electrodynamic drive, for example. The outer casing 104 as well as the drive devices 108 can operate to determine a first resonant frequency for the marine acoustic vibrator. The driving devices 108 can be connected to the face of the two lateral envelope parts 106a, 106b. As illustrated, the marine acoustic vibrator 100 may further comprise a frame 109 capable of suspending the drive devices 108 in the outer casing 104. In the illustrative embodiment, the frame 109 may be in the form of a frame.
    In the sectional illustration of Figure 4, the variable gas limiter 102 is disposed inside the outer casing 104. As illustrated, the variable gas limiter 102 can be fixed on the frame 109. In exemplary embodiments, the variable gas limiter 102 has a sliding plate structure which is movable between a closed position and an open position. In the closed or partially closed position, the variable gas limiter 102 can be used to limit the flow of gas in the outer casing 104. In some embodiments, the variable gas limiter 102 can completely isolate part of the volume internal of the outer casing 104. Consequently, the gas flow can be limited when it is desired to make the gas spring stiffer, which may be desired in certain embodiments. For example, one may wish to make the gas spring stiffer and thus increase the first resonant frequency at shallow depths. This type of gas spring compensation can be achieved, for example, when a substantially constant resonant frequency is desired regardless of the depth. Without gas spring compensation, the gas spring can stiffen when the marine acoustic vibrator 100 is lowered into the water, causing the first resonant frequency to vary with depth. However, the present embodiments can provide a resonant frequency for the marine acoustic vibrator 100 chosen on the basis of at least in part the variable gas limiter 102 so that the marine acoustic vibrator 100 can have a resonant frequency substantially constant regardless of depth.
    Referring now to Figure 5, an exemplary embodiment of a variable gas limiter 102 will now be described in more detail. As illustrated, the variable gas limiter 102 may have a sliding plate structure which includes a first plate 110 and a second plate 112. The first plate 110 may have holes 114, and the second plate 112 may also have holes 116. The first plate 112 and the second plate 110 as illustrated can each be of a generally rectangular shape in certain embodiments, but other plate configurations may be appropriate by including square, circular, elliptical structures, or irregularly shaped. The number of holes 114 in the first plate 110 and holes 116 in the second plate 112 can be chosen in order to obtain the desired amount of gas flow. Each of the holes 114 and the holes 116 may have a chosen diameter and spacing based on the desired amount of gas flow and a desired resonant frequency, among others. For example, the hole size can be reduced with increased spacing if less gas flow is desired while the hole size can be increased with reduced spacing if more gas flow is desired.
    The variable gas limiter 102 can be movable from (or towards) a closed or partially closed position (for example on the left side of FIG. 5) towards (or from) an open position (for example on the right side of FIG. 5 ). In the open position, the holes 114 in the first plate 110 can be aligned with the holes 116 in the second plate 112 so that through holes 118 are formed in the variable gas limiter 102 allowing maximum gas flow. In the closed position, the holes 114 in the first plate 110 can be at least partially limited by the second plate 112 thereby limiting a flow of gas in through holes 118. Thanks to a movement of the second plate 112, the size of through hole 118 can be reduced, limiting gas flow. In other words, the second plate 112 can be positioned to effectively limit the size of the through holes 118. In some embodiments as shown in Figure 5, the second plate 112 can be positioned to partially close the variable gas limiter 102 so that the holes 114 in the first plate 110 are substantially blocked. An electric drive, pneumatic drive, hydraulic drive, or other suitable drive can be used in the control of the variable gas limiter 102. A mechanism (not shown) can connect the variable gas limiter 102 to a control system which can operate to control the position of the second plate 112 and thus the gas flow. The variable gas limiter 102 can be controlled, for example, in order to maintain a substantially constant resonant frequency when the depth of the marine acoustic vibrator 100 changes. For example, the variable gas limiter 102 can be closed when the frequency increases to maintain a substantially constant resonant frequency. In some embodiments, the variable gas limiter 102 can be passively driven, for example on the basis of a pressure sensor. In some embodiments, the variable gas limiter 102 can be remotely controlled from the towing vessel or a work boat (eg, the research vessel 200 of Figure 13). In some embodiments, the variable gas limiter 102 can be fixed in place in certain operations. It is obvious that the first plate 110 can be fitted with slots or other suitable cover (for example a shutter, a guillotine device, etc.) which can be controlled in order to allow or limit a flow of gas through the holes 114. Although FIG. 5 illustrates the variable gas limiter 102 in the form of a sliding plate structure, other suitable mechanisms intended to limit the flow of gas in the marine acoustic vibrator 100 can be used according to exemplary embodiments, including hinged doors, roll-up doors, and the like. For example, a device (for example a plate, a door, etc.) can be used to isolate part of the internal volume available for the gas spring.
    Figure 6 illustrates a marine acoustic vibrator 100 which includes a variable gas limiter 102. The marine acoustic vibrator 100 of Figure 6 is shown in section. As illustrated, the marine acoustic vibrator 100 includes an outer casing 104, which can be made of spring steel or a similar elastic metal, and which can be a class V flexion-extension transducer. In the illustrated embodiment , the shape of the outer casing 104 can be generally called as flexion-extension. As illustrated, the outer casing 104 may be formed, for example, by two lateral casing portions 106a, 106b connected at or near the ends of their longer long axes, by respective hinges 120 in shapes of particular achievements. In particular embodiments, the outer casing 104 can act as a spring having a first spring constant in order to generate a first resonant frequency. As is obvious to a person skilled in the art with the benefit of this description, the spring constant of the outer casing 104 can be determined by its dimensions, its composition of matter, and its shape in the relaxed state, by example. Although Figure 6 shows a substantially semi-elliptical flexion-extension envelope, flexion-extension envelopes of other shapes, including convex, concave, flat, or combinations thereof, may also be suitable. In certain embodiments, the dimensions, the composition of matter, and the shape of the outer casing 104 can be chosen in order to provide a flexible spring constant for vibrations between approximately 1 and 10 Hz when the marine acoustic vibrator is immersed. in water at a depth of about 0 meters to about 300 meters.
    As illustrated, the marine acoustic vibrator 100 may further include a drive device 108, which may be an electrodynamic drive device. The outer casing 104 as well as the drive device 108 can operate in order to determine a first resonant frequency of the marine acoustic vibrator 100. In certain embodiments, the drive device 108 can be a drive device for " voice coil ”or“ voice coil ”, which can provide the ability to generate very large amplitudes of acoustic energy. Although the particular embodiment described here shows a bidirectional drive device, embodiments with one or more unidirectional drive devices or in which a plurality of drive devices are used in parallel, are within the scope of the invention. The drive device 108 can be connected to the face of the two lateral envelope parts 106a, 106b. For example, as illustrated in FIG. 6, the drive device 108 can be connected approximately to the vertical midpoint of the face of the outer casing 104, near the ends of the shorter short axes of the lateral parts of envelope 106a, 106b.
    In some embodiments, the marine acoustic vibrator 100 may further include a frame 109 capable of suspending a drive device 108 inside the outer casing 104. For example, in the illustrated embodiment , the frame 109 extends along the long axis of the outer casing 104 and can be connected to the outer casing 104 with linear bearings 122. In certain embodiments, the frame 109 may be of circular section and can be mounted on the hinges 120 using the linear bearings 122. This support can allow contraction of the major axis of the outer casing 104 when the minor axis is enlarged by the movement of the drive device 108.
    As illustrated, the drive device 108 may include a bidirectional voice coil drive device, having two sets of electric coil 124, transmission element 126, and magnetic circuit 128, which are capable of generating a magnetic field. As illustrated, the magnetic circuit 128 can be connected to the frame 109, while the transmission element 126 can be connected to the outer casing 104. In certain embodiments (not shown), this arrangement can be reversed ( that is, the magnetic circuit 128 is connected to the outer casing 104, while the transmission element 126 is connected to the frame 109). By attaching the heavier part (magnetic circuit 128) of the drive device 108 to the outer casing 104, it may be easier to generate low frequencies without having to make the outer casing 104 too weak to allow a constant of flexible spring. As illustrated, each transmission element 126 can transfer the movement of the electric coil 124 to the inner surface of the outer casing 104 near its minor axis. When an electric current I is applied to the electric coil 124, a force F acting on the electric coil 124 can be generated as follows:
    [Math.l]
    F = I1B (Equation 1) where I is the current, 1 is the length of the conductor in the electric coil 124, and B is the magnetic flux generated by the magnetic circuit 128. By varying the importance of the electric current and therefore the magnitude of the force acting on the electric coil 124, the length of the drive device stroke must vary. The driving device 108 can provide stroke lengths of several centimeters (up to and including about 25.4 cm (10 inches)), which can allow the marine acoustic vibrator 100 to generate an acoustic output of amplitude improved in low frequency ranges, for example, between approximately 1 Hz and approximately 100 Hz, and more particularly between approximately 1 and 10 Hz when the marine acoustic vibrator 100 is immersed in water to a depth of approximately 0 meters 300 meters. Magnetic circuit 128 can often include permanent magnets, although any device capable of generating magnetic flux can be incorporated.
    In the illustrated embodiment, the marine acoustic vibrator 100 further comprises the variable gas limiter 102 disposed inside the outer casing 104. As illustrated, the variable gas limiter 102 can be fixed on the frame 109. As described above, the variable gas limiter 102 can be movable between an open position and a closed position in order to limit a flow of gas inside the outer casing 104. By way of For example, limiting the gas flow can be used to increase the first resonant frequency by stiffening the gas spring.
    As is obvious to a person skilled in the art, the total impedance which can be supported by a marine acoustic vibrator 100 can be expressed as follows: [0049] [Math.2]
    Z r = R r + jX r (Equation 2) where Z r is the total impedance, R r is the radiation impedance, and X r is the reactive impedance.
    In an analysis of the energy transfer from the marine acoustic vibrator 100, the system can approach a baffle piston. In the expression of the total impedance which is supported, the radiation impedance R r of a baffle piston can be [Math52]
    R r = Ka 2 p o cRi (x) (Equation 3) and the reactive impedance can be:
    [Math.4]
    Xr = π3 2 ρ ο οΧι (χ) (Equation 4) [0055] where [0056] [Math.5] x = 2ka = (4πά / λ) = (2œa / c) (Equation 5) [0057] and where [Math.6]
    Ri (x) = 1 - (2 / x) Ji (x) and (Equation 6) [0059] [Math.7] π / 2
    Xi (x) = ( - ) f sin (x cos ot) sm ocda (Equation 7) π J [0060] where p o is the density of water, ω = radial frequency, k = wave number, a = piston radius, c = speed of sound, λ = wavelength, and Ji = first-order Bessel function.
    The use of the Taylor series development on the above equations gives the following:
    [Math. 8] „2,„ 4
    [Math.9] xx 3 x 5
    Xi (x) = (-) (3 · - 375 · + 3 ^ 7 - (Equation 9) [0064] For low frequencies, when x = 2ka is much smaller than 1, the real and imaginary part of the expression of total impedance can be approximated with the first term of the expression of Taylor. The expressions for low frequencies, when the wavelength is much greater than the radius of the piston become:
    [Math. 10] [0067] [0068] [0069]
    Ri (x) = (1/2) (ka) 2 (Equation 10) [Math. 11]
    Xi (x) (8ka) / (3K) (Equation 11)
    It follows that, for low frequencies, R is a small number compared to X, which suggests very low efficiency signal generation. However, embodiments can introduce resonance in the lower part of the frequency spectrum so that low frequency acoustic energy can be generated more efficiently. At resonance, the imaginary (reactive) part of the impedance is canceled, and the marine acoustic vibrator 100 may be able to efficiently transmit acoustic energy into the body of water.
    In certain embodiments, the marine acoustic vibrator 100 can have two resonant frequencies (when immersed in water at a depth of approximately 0 meters to approximately 300 meters) in the range of seismic frequency of interest, for example, between about 1 Hz and about 200 Hz. In particular embodiments, the marine acoustic vibrator 100 can have two resonant frequencies (when immersed in water) between about 0.1 Hz and about 10 Hz, and alternatively between approximately 0.1 Hz and approximately 5 Hz. As described above, the first resonant frequency can be controlled by limiting a flow of gas in the marine acoustic vibrator 100. In particular embodiments , the first resonant frequency can be increased by limiting the gas flow in the marine acoustic vibrator 100. For example, the first frequency resonance can be controlled to be substantially constant regardless of depth.
    FIG. 7 illustrates another embodiment of a marine acoustic vibrator 100 comprising a variable gas limiter 102. In the illustrated embodiment, the marine acoustic vibrator 100 further comprises a spring 130 inside the envelope outer 104 with masses 132 fixed thereon along the ends of the major axis and slidably supported on the frame 109 using a linear bearing 134. As illustrated, the spring 130 may be of a generally elliptical shape. The spring 130 can be connected to the outer casing 104 near the minor axis. In the illustrated embodiment, the drive device 108 can be connected to the outer casing 104. The spring 130 with the masses 132 can cause a second system resonant frequency when the marine acoustic vibrator 100 is immersed in the water at a depth of about 0 meters to about 300 meters in the seismic frequency range of interest (for example between about 1 Hz and about 10 Hz). Although a marine acoustic vibrator 100 as shown in Figure 6 which includes only the outer casing 104 acting as a spring typically has a second resonant frequency, for systems having a size suitable for use in geophysical exploration, the second resonant frequency when the marine acoustic vibrator 100 is immersed in water is typically much higher than the range of seismic frequency of interest.
    Figure 8 illustrates yet another embodiment of a marine acoustic vibrator 100 having a variable gas limiter 102. In the illustrated embodiment, the major axis ends of the spring 130 can be connected to the major ends axis of the outer casing 104 at the hinges 120. The masses 132 can be fixed to the spring 130 near its minor axis. As illustrated in FIG. 9, the spring 130 can be vertically divided into two springs 130a, 130b, each with added masses 132. In the illustrated embodiment, a spring 130a is arranged above the drive device 108, while the other internal spring 130b is disposed below the drive device 108, and the drive device 108 remains connected to the outer casing 104, as shown in FIG. 8.
    In an evaluation of the effects of a gas spring, a finite element analysis can be used as is known to those skilled in the art. In such an analysis, the following principles may be relevant. If the outer envelope 104 of the marine acoustic vibrator 100 is approached in the form of a piston, then, for low frequencies, the mass load, or the equivalent fluid mass acting on the envelope can be:
    [Math. 12]
    Msheii - Po (8a 3/3) (Equation 12) [0073] where M she u is the mass load of the outer shell 104, p o is the density of water, and a is the equivalent radius for a piston which corresponds to the size of the outer casing 104. The outer casing 104 may also have a spring constant, for example, in the direction of the moving electric coils of the marine acoustic vibrator 100.
    The stiffness of the entrained gas (gas spring) can be described by the following general formula:
    [Math. 13]
    Kvariabiegasspring = AVolume / Volume * Ρ * γ (Equation 13) [0076] where K Variable i egasspring is the value of the gas spring, issue is the internal volume of marine acoustic vibrator 100, AVolume is the volume change of at action of the marine acoustic vibrator 100, P is the absolute pressure of the gas inside the marine acoustic vibrator 100, and γ is the adiabatic constant which is a unique property depending on the chemical composition of the gas.
    Therefore, taking into account the effects of gas spring, the first resonant frequency, f reson ance i, due to the interaction of the outer shell 104 acting as a spring can be significantly determined by the relationship following spring mass:
    [Math. 14] r- _ 1 _ / Kst- 1 ell ~ i ~ K var j_ a i 3 ] _ ea x rS p 3 -j -n q fre S o „ a0 ee-i - 2jt -yy (Equation 14) [ 0079] where K u she is the spring constant of the outer shell 104, K egasspring Variable i is the gas spring value determined by the change in volume of gas using, for example, equation 13 above , M driver is the mass load of the drive device, and M she u is the mass load of the outer casing 104. Therefore, it may be possible, as shown above, to adjust the first resonant frequency by compensating for the gas spring. By limiting the flow of gas into the outer casing 104, the effective volume of gas can be changed, which results in a variation of the gas spring value. The first resonant frequency may also change because the gas spring value has also changed. For example, a stiffer gas spring due to an increase in pressure or a reduction in the base volume of gas has a higher gas spring value thereby causing a corresponding increase in the first resonant frequency.
    To obtain efficient energy transmission in the seismic frequency range of interest, it may be desirable to obtain a second resonant frequency in the seismic frequency range of interest. In the absence of the spring 130 with its added masses 132, the second resonant frequency appears when the outer casing 104 has its second natural mode. This resonant frequency, however, is normally much higher than the first resonant frequency, and therefore is typically outside of the seismic frequency range of interest. As is evident from the previous equation, the resonant frequency is reduced if the mass load on the outer casing 104 is increased. However, in order to add sufficient mass to obtain a second resonant frequency in the seismic frequency range of interest, the quantity of [0081] [0082] [0083] [0084] [0085] [0086] [0087] Mass that may need to be added to the outer casing 104 may make this system less practical for use in marine seismic operations.
    In some embodiments, the spring 130 is included inside the outer casing 104 with added masses 132 on the side of the spring 130. The spring 130 may have a transformation factor Tspring between the large and the small axis of its ellipse, so that the clearance of the two lateral parts has a higher amplitude than the clearance of the end fixed on the outer casing 104 and the drive device 108.
    The effect of these added masses 132 can be equivalent to adding a mass to the end of the drive device 108 where it is fixed to the outer casing 104.
    [Math. 15] ^ spring - (-L spring) · ^ added (EcjUcltΪ.ΟΠ 15)
    Where M spring is the mass of the spring, T spring is the transformation factor of the spring, and M a dded is the mass of the added mass 132.
    The use of the spring 130, with the added masses 132, can allow the second resonant frequency of the system to be tuned so that the second resonant frequency is in the seismic frequency range of interest, thereby improving the effectiveness of the marine acoustic vibrator 100 in the seismic band. [Math. 16] fresonance2 _ I _______ Ksprinq + Kshell _______
    2tî 'y spring) M a dded + M s hell (Equation 16) where Kspnng is the spring constant of spring 130, K she ii is the spring constant of outer shell 104, T spring is the transformation factor of spring, M adde d is the mass of the added mass 132, and M she ii is the mass load on the outer casing 104.
    Therefore, it may be possible, as shown above, to choose the added mass 132 on the spring 130 to tune the second resonant frequency. It may also be possible to choose the magnitude of the influence that the second resonant frequency should have on the system. For example, if the spring 130 has a low spring constant compared to the outer casing 104, and a corresponding mass 132 is added to the spring 130, the spring 130 with its mass 132 operates relatively independently of the outer casing 104. In this case, the second resonant frequency can be as follows:
    [Math. 17] _ A fresonance2 - n
    2π __________ 2.gE £ j; .. ng; __________ / p _ + - _ · _ „1 -7 7m ' 2. p *, (Equation 1 /) I 1 spring / · LJ adaea [0090] De la same way, it may also be possible in certain embodiments to make the second resonant frequency very large by choosing a high spring constant for the spring 130 with a corresponding mass 132 so that the second resonant frequency has an amplitude greater than the first resonant frequency.
    In some embodiments, the marine acoustic vibrator 100 can be towed relatively deep, for example, from about 10 meters to as deep as 100 meters or more. Figures 10 and 11 are plots showing the attenuation for a model of a marine acoustic vibrator 100 due to the phantom source. Figure 10 shows the attenuation due to the phantom source at 10 meters. Figure 11 shows the attenuation due to the phantom source at 100 meters. Therefore, the marine acoustic vibrator 100, in particular embodiments, must be towed more deeply as seen in Figures 10 and 11 to avoid unwanted attenuation of the signal by the phantom source.
    The dimensions of the marine acoustic vibrator 100 can vary as necessary for a particular application. Referring to FIG. 12, an exemplary embodiment of a marine acoustic vibrator 100 can have an envelope size as follows: 1) envelope height Hi extending from approximately 0, 5 meters to about 4 meters, for example about 1.59 meters; 2) envelope end height H 2 of the envelope end extending from about 0.3 meters to about 1 meter; 3) envelope width Wj ranging from about 0.5 meters to about 4 meters, for example, about 1.75 meters, 4) envelope thickness Ti ranging from about 0.2 meters to about 3 meters, for example, about 2.5 meters. As illustrated, the envelope height Hi is the height of the outer envelope 104 at or near its center line while the envelope end height H 2 is the height of the outer envelope 104 at its longitudinal end. In particular embodiments, the marine acoustic vibrator 100 may have an envelope size as follows: 1) envelope height Hi of 1.59 meters; 2) envelope end height H 2 of 1.0 meter; 3) envelope width Wi of 1.75 meters; 4) Ti envelope thickness of 2.5 meters.
    Figure 13 illustrates an example technique for acquiring marine seismic data which can be used with embodiments of the present techniques. In the illustrated embodiment, a research vessel 200 travels along the surface of a body of water 202, such as a lake or an ocean.
    Research vessel 200 may include equipment, generally represented at 204 and collectively referred to hereinafter as the "recording system". The recording system 204 may comprise devices (none being shown separately) intended to detect and carry out a time-indexed recording of the signals generated by each of seismic sensors 206 (explained further below) and intended to activate one or more seismic sources (as illustrated, a marine acoustic vibrator 100) at selected times. The recording system 204 may also include devices (none being shown separately) intended to determine the geodetic position of the research vessel 200 and the various seismic sensors 206.
    As illustrated, the research ship 200 (or a different ship) can tow the marine acoustic vibrator 100 into the body of water 202. A source cable 208 can connect the marine acoustic vibrator 100 to the ship of search 200. The marine acoustic vibrator 100 can be towed in the body of water 202 to a depth ranging from 0 meters to about 300 meters, for example. Although a single marine acoustic vibrator 100 is shown in Figure 13, it is intended that the embodiments may include more than one seismic source (e.g. marine acoustic vibrators or pneumatic cannons) towed by the research vessel 200 or a different ship. In some embodiments, one or more rows of seismic sources can be used. At selected times, the marine acoustic vibrator 100 can be triggered, for example, by the recording system 204, in order to generate acoustic energy. The research vessel 200 (or a different vessel) can also tow at least one marine sensor flute 210 in order to detect the acoustic energy which originates from the marine acoustic vibrator 100 once it has interacted, for example, with the rock formations 212 below the bottom 214. As shown, the marine acoustic vibrator 100 and the sensor marine streamer 210 can be towed above the bottom 214. The seismic streamer 210 can contain seismic sensors 206 in spaced locations. Although not shown, some seismic research positions 206 seismic sensors on ocean bottom cables or nodes in addition to, or in place of, a marine sensor flute 210. The 206 seismic sensors can be any type of seismic sensor known in the art, including hydrophones, geophones, particle velocity sensors, particle displacement sensors, particle acceleration sensors, or pressure gradient sensors , for example. For example, the seismic sensors 206 can generate response signals, such as electrical or optical signals, in response to detected acoustic energy. Signals generated by the seismic sensors 206 can be transmitted to the recording system 204. In some embodiments, more than one sensor marine streamer 210 can be towed by the research vessel, which can be spaced laterally, vertically or both laterally and vertically. The energy detected can be used to deduce certain properties of the rock below the surface, such as structure, mineral composition, and fluid content, thereby providing information useful in the recovery of hydrocarbons.
    According to an embodiment of the invention, a geophysical data product indicative of certain properties of the rock below the surface can be produced from the energy detected. The geophysical data product can include processed seismic geophysical data and can be recorded on a machine-readable, tangible medium. The geophysical data product can be produced at sea (i.e. by equipment on a ship) or ashore (i.e. at an onshore facility) in the United States or elsewhere country. If the geophysical data product is manufactured at sea or in another country, it can be imported on land at a facility in the United States. Once ashore in the United States, a geophysical analysis can be performed on the data product.
    权利要求:
    Claims (1)
    [1" id="c-fr-0001]
    claims [Claim 1] Marine acoustic vibrator (100), characterized in that it comprises: an external bending-extension envelope (104);a frame (109) connected to the outer envelope (104) of flexion-extension; a drive device (108) having a first end and a second end, the first end being fixed on the outer casing (104) of flexion-extension, and the second end is fixed on the frame (109);a gas spring being provided with a mass to generate a first resonant frequency, and the value of the gas spring being changed by limiting the flow of gas in the marine acoustic vibrator (100) to thereby control the first deep resonant frequency. [Claim 2] Marine acoustic vibrator (100) according to claim 1, characterized in that the marine acoustic vibrator (100) has at least two resonant frequencies of about 10 Hz or less when immersed in water at a depth of about 0 meter to about 300 meters. [Claim 3] Marine acoustic vibrator (100) according to claim 1 or 2, characterized in that it further comprises a gas flow limiter arranged inside the outer casing (104). [Claim 4] Marine acoustic vibrator (100) according to claim 3, characterized in that the variable gas flow limiter (102) has a first plate (110) having holes, and a second plate (112) having holes, the second plate (112) being movable to at least partially cover the holes in the first plate (110). [Claim 5] Marine acoustic vibrator (100) according to claim 4, characterized in that the variable gas flow limiter (102) has an open position and a closed position, the holes in the first plate (110) being at least partially obstructed by the second plate (112) in the closed position, and the holes in the first plate (110) and the holes in the second plate (112) being aligned in the open position for maximum gas flow through the flow restrictor variable gas (102). [Claim 6] Marine acoustic vibrator (100) according to any one of claims 3 to 5, characterized in that the variable gas flow limiter (102) is fixed to the frame (109).
    1/12
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    US9612347B2|2014-08-14|2017-04-04|Pgs Geophysical As|Compliance chambers for marine vibrators|
    US9389327B2|2014-10-15|2016-07-12|Pgs Geophysical As|Compliance chambers for marine vibrators|
    US10488542B2|2014-12-02|2019-11-26|Pgs Geophysical As|Use of external driver to energize a seismic source|
    US10605934B2|2015-08-31|2020-03-31|Pgs Geophysical As|Apparatus with thermal stress relief mechanism for heat generating coil and associated methods|
    US10234585B2|2015-12-10|2019-03-19|Pgs Geophysical As|Geophysical survey systems and related methods|
    US10222499B2|2016-01-11|2019-03-05|Pgs Geophysical As|System and method of marine geophysical surveys with distributed seismic sources|
    法律状态:
    2019-07-04| PLFP| Fee payment|Year of fee payment: 6 |
    2020-05-25| PLFP| Fee payment|Year of fee payment: 7 |
    2020-08-14| PLSC| Search report ready|Effective date: 20200814 |
    2021-10-01| RX| Complete rejection|Effective date: 20210820 |
    优先权:
    申请号 | 申请日 | 专利标题
    US201361823892P| true| 2013-05-15|2013-05-15|
    US61/823892|2013-05-15|
    US14/145,214|US9864080B2|2013-05-15|2013-12-31|Gas spring compensation marine acoustic vibrator|
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