EP0202246A1 - Generateur sismique - Google Patents

Generateur sismique

Info

Publication number
EP0202246A1
EP0202246A1 EP85905171A EP85905171A EP0202246A1 EP 0202246 A1 EP0202246 A1 EP 0202246A1 EP 85905171 A EP85905171 A EP 85905171A EP 85905171 A EP85905171 A EP 85905171A EP 0202246 A1 EP0202246 A1 EP 0202246A1
Authority
EP
European Patent Office
Prior art keywords
piston
post
passageway
power
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP85905171A
Other languages
German (de)
English (en)
Other versions
EP0202246A4 (fr
Inventor
Serge S. Wisotsky
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Industrial Vehicles International Inc
Original Assignee
Industrial Vehicles International Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Industrial Vehicles International Inc filed Critical Industrial Vehicles International Inc
Publication of EP0202246A1 publication Critical patent/EP0202246A1/fr
Publication of EP0202246A4 publication Critical patent/EP0202246A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01V—GEOPHYSICS; GRAVITATIONAL MEASUREMENTS; DETECTING MASSES OR OBJECTS; TAGS
    • G01V1/00—Seismology; Seismic or acoustic prospecting or detecting
    • G01V1/02—Generating seismic energy
    • G01V1/143—Generating seismic energy using mechanical driving means, e.g. motor driven shaft
    • G01V1/155—Generating seismic energy using mechanical driving means, e.g. motor driven shaft using reciprocating masses

Definitions

  • This invention relates generally to improved method and apparatus for the generation of vibratory impulses in liquid. More particularly, but not by way of limitation, this invention relates to an improved seismic generator apparatus and method that provides for more precise cyclic rate control and an extended operational life to the apparatus.
  • U.S.Patent No. 3,349,367 issued October 27, 1967 to Serge S. isots y contains a further discussion of the background and uses of such devices.
  • the '367 patent also discloses a marine seismic genera- tor that is similar to the generator disclosed herein.
  • the apparatus of this invention is an improvement to the apparatus disclosed therein. While apparatus constructed in accordance with the '367 patent operated satisfactorily, apparatus constructed in accordance with the present invention is more efficient, provides more accurate control and response to changes of the cyclic rate.
  • Marine seismic generators are deployed from vessels and operate in conjunction with an array of electronic devices to receive the seismic signals.
  • the generator of this invention is also useful in generating vibratory impulses in inland seismic operations when the generator is immersed in a pond, lake, mud pit or the like during operation. Such vibrations are sometimes utilized in connection with the vertical deployment of an array of geophones in a well bore or the like.
  • the generator in such uses provides a point source of vibratory energy and the geophones sense the time occurrence and signal strength to provide geologists and geophysicist with information concerning the formations traversed and to be traversed by the well bore.
  • An object of the present invention is to pro ⁇ vide improved apparatus for the generation of vibratory impulses in liquid that has a longer operating life, is lighter, more compact, and provides for more accurate control of the cyclic rate of the vibratory impluses.
  • this invention provides an improved seismic generator for creating vibratory impulses in liquid comprising: a housing having a post projecting therefrom.
  • a piston is mounted for recipro ⁇ cating movement on the post and has a surface thereon that is arranged to engage the liquid.
  • the piston includes an annular portion encircling the post. The annular portion and the post cooperate to provide a pair of expansible power chambers.
  • First conduit or passageway means in said post provides pressurized fluid alternately to said chambers to cause reciproca ⁇ tion of the piston and to permit return flow of such fluid.
  • Second conduit means is provided in the post for, at times, relieving the pressure in the chambers.
  • a passageway in the piston connects the chambers with the second conduit means when the piston is near the end of its travel.
  • this invention provides an improved method for causing seismic vibrations in liquid comprising the steps of: supplying a pressure fluid; directing the pressure fluid to a first expan- sible chamber to cause movement of a piston assembly in one direction; trapping fluid in the damping portion of a second expansible chamber to reduce the speed of movement of the piston assembly; directing the pressure fluid to the second expansible chamber to cause the piston assembly to move in the opposite direction; and, trapping fluid in the damping portion of the first expansible chamber to reduce the speed of movement of the piston assembly in the opposite direction.
  • FIG. 1 is a schematic view of a seismic generator that is constructed in accordance with the invention.
  • FIG. 2 is a partial cross-sectional view of the generator in FIG. 1 illustrating the structure thereof in more detail.
  • FIG. 3 is an enlarged fragmentary, cross- sectional view illustrating, somewhat schematically, the operational relationship between the piston and post contained in the generator of FIG. 1.
  • FIG. 4 is a view similar to FIG. 3, but illustrating the post and piston in another operating position.
  • the generator 10 includes a housing assembly 12 having a post assembly 14 projecting generally downwardly therefrom and a piston assembly 16 that is arranged, with respect to the post assembly 14, for reciprocating motion therebetween. As shown in elevation in FIG. 2 and schemati ⁇ cally in FIG. 1, the generator 10 also includes a control valve assembly 18.
  • the control valve assembly 18 operates in conjunction with electronic apparatus 20, for causing reciprocation of the piston assembly 16 relative to the post assembly 14, and for controlling the cyclic rate of such reciprocating movement.
  • the housing assembly 12 includes a cup shaped portion 22 that is arranged to receive the control valve 18 and to which the post assembly 14 is secured by fasteners 23; a lower bell housing 24 that is sized to receive the piston assembly 16; and, an upper bell housing 26 that is welded to the cup shaped member 22 and to the lower bell housing 24.
  • the upper bell housing 26 includes a plurality of circumferentially spaced, radially pro ⁇ jecting reinforcing members 28 that extend between the upper bell housing 26 and lower bell housing 24.
  • the housing 26 is welded to the members 28 by a plurality of plug welds 30.
  • each of the reinforcing members 28 is provided with a plurality of openings 32 to permit communication throughout the upper bell housing 26. Also, adjacent to the juncture between the upper bell housing 26 and lower bell housing 24, there is provided a plurality of vent holes 34 (only one hole 34 is shown in FIG. 2) that permit movement of gaseous fluid between the interior of the upper bell housing 26 and the interior of the lower bell housing 24.
  • the cup shaped member 22, the lower bell housing 24, and the upper bell housing 26 are designed and constructed so that the housing assembly 12 has a natural frequency that is outside of the operating fre ⁇ quency of the piston assembly 16. Accordingly, reciprocation of the piston assembly 16 will have no deleterious effect upon the structure of the housing assembly 12 since no harmful resonant frequencies will be generated.
  • the piston assembly 16 includes an annular portion 36 having a plurality of circumferentially spaced reinforcing members 38 that project radially from said annular portion 36. Each member 38 having a plurality of openings 38a to provide communication throughout the piston 16.
  • the reinforcing members 38 carry an annular peripheral member 40 and are attached at the lower ends thereof to a liquid engaging member 42 having a substantially planar lower surface 43.
  • the members 38 are attached at their upper ends to con ⁇ tiguous reinforcing members 42a each of which is pro- vided with vent holes 38b that permit communication between the interior of piston 16 and the cavity in the housing cavity 24.
  • the annular peripheral member 40 is disposed in juxtaposition with an annular member 44 that is attached to the lower end of the lower bell housing 24.
  • a rolling seal 46 Disposed between the member 40 and the member 44 is a rolling seal 46 that has one end attached to the member 40 and the other end attached to the member 44.
  • the seal 46 is arranged to permit reciprocation of the piston assembly 16 relative to the annular member 44 on the housing 12 while maintaining a watertight seal therebetween.
  • FIG. 2 illustrates in detail the structure of the annular portion 36 of the piston assembly 16 and of the post assembly 14. Because of the complexity of the arrangement of the conduits, that is, the ports and passageways in the post assembly 14 and in the annular portion 36, such flow passageways are schematically illustrated in FIGS. 3 and 4.. The flow passageways are also illustrated schematically in FIG. 1 in connec ⁇ tion with a schematic illustration of the control valve 18. The same reference characters will be used whether the various components are illustrated structurally or schematically.
  • a first power passageway 48 is formed in the post assembly 14 and has the upstream end of thereof connected with a power valve 50 which forms a part of the control valve assembly 18.
  • the downstream end 52 of the first power passageway 48 extends through a sidewall 54 of the post assembly 14.
  • a second power passageway 56 extends through the post assembly 14 and has its upstream end also con ⁇ nected with the power valve 50.
  • the lower or downstream end 58 of the second power passageway 56 extends through the sidewall 54 of the post assembly 14 in spaced relation to the end 52 of the first passa ⁇ geway 48.
  • passageways 48 and 56 have been described as power passageways, it should be understood
  • one of the passageways 48 and 56 functions as a power passageway while the other functions as a return passageway.
  • the roles of the passageways 48 and 56 are reversed to cause reciprocation of the piston assembly 16, as will be described.
  • the post assembly 14 also includes a radially projecting annular flange 60 that provides an upwardly facing surface 62 and a downwardly facing surface 64. Disposed between such surfaces 62 and 64 and extending through the peripheral surface of the flange 60 is a return passageway 66. Located between the surfaces 62 and 64 are a pair of spaced annular seals 65 and 67. The seals are positioned on each side of the passageway 66.
  • the return passageway 66 is connected to a fluid reservoir 68 as is schematically illustrated in FIG. 1. Also connected to the reservoir 68 is a return passageway system 70 that is connected to the power valve 50.
  • the system 70 connects the appropriate power passageway 48 or 56 by means of the power valve 50 to return said fluid from valve 50 to the reservoir 68 from the appropriate passageway 48 or 56.
  • High pressure fluid is supplied to the power valve 50 through a conduit 72 which has a hydraulic pump 74 located therein. Depending upon the position of the power valve 50, fluid from the pump 74 flows through the conduit 72 into the appropriate power passageway 48 or 56.
  • the piston assembly 16 includes an upper bearing 76 that is attached to and moves with the piston assembly 16 and a lower bearing 78 that also moves with the piston assembly 16.
  • a spacer member 80 located between the bearing 76 and 78 holds the bearings in the desired spaced relation.
  • the upper bearing 76 provides a downwardly facing surface 82 which, in conjunction with the upwardly facing surface 62 on the flange 60, the spacer member 80 and the sidewall 54, form a first expansible power chamber 84.
  • the lower bearing 78 pro ⁇ vides an upwardly facing surface 86 that, in conjunc ⁇ tion with the sidewall 54, the spacer member 80, and the upwardly facing surface 64 on the lower bearing 78, form a second expansible power chamber 88 (see FIG. 4).
  • Seals 65 and 67 engage the member 80 to seal the hydraulic fluid within the power chambers 84 and 88.
  • An upper main seal 90 and a lower main seal 92 are carried by the bearings 76 and 78, respectively, and are located between the piston assembly 16 and the post assembly 14. To extend the operating life of the generator 10, the seals 90 and 92 are protected from the imposition of extremely high pressures generated during reciprocation of the piston assembly 16 by the presence of drain passageways 94 and 96, which are con ⁇ nected into a drain passageway 98. As can be seen, the drain passageway 98 is routed through a sliding connec- tion 100 to connect to a passageway 102.
  • the sliding connection 100 includes a tubular member 104 that projects upwardly from a base cap 106 (see FIG. 2) into a cavity 108 that is formed in the post assembly 14. Within the cavity 108, there is located an upper and lower seal 110 that provides a fluid tight seal between the tubular member 104 and the post assembly 14.
  • the member 104 includes a plurality of ports 112 that provide communication between the drain passageway 98 and the drain passageway 102.
  • the pur ⁇ pose of the sliding seal assembly 100 is to prevent any possibility of the reciprocation between the piston assembly 16 and the post assembly 14 causing "pumping" of fluid contained in the passageway 98.
  • the various com ⁇ ponents of the annular portion 36 of the piston assembly 16 are trapped between a bottom cap 106 and a top cap 114.
  • the caps 106 and 114 are attached to the portion 36 by threaded fasteners and retain the upper and lower bearings 76 and 78 and the spacer member 80 in the relationship illustrated. They also function indirectly to prevent movement of the piston assembly 16 off of the post assembly 14 during reciprocation.
  • the downstream ends 52 and 58 of the power passageways 48 and 56 respectively, connect into the chambers 84 and 88, respectively, at locations slightly above and below the surfaces 62 and 64 on the flange 60.
  • a small damping chamber is formed therein in which fluid is trapped and thus dampens the movement of the piston assembly 16 relative to the post assembly 14.
  • the fluid trapped therein is discharged along the bearing 76 or 78, as is appropriate, from whence it is discharged through the drain passageway 98.
  • the spacer member 80 is provided with two vertically spaced rows of ports 116 and 118 that are also circumferentially spaced. Communication between the rows of ports 116 and 118 is provided by an annular space 120 formed in the annular portion 36.
  • the rows of ports 116 or 118 are moved into communication with the chamber 84 or 88 prior to the time that the surface 82 impacts the surface 62 or the surface 86 impacts the surface 64 to permit the high pressure fluid flowing through the pressure supply passageway 48 or 56 to flow into the return passageway 66.
  • the force moving the piston assembly 16 is relieved so that full pressure load is not applied to drive the piston assembly 16 into the post assembly 14.
  • the generator 10 is more responsive and more accurate in its cyclic control of the frequency of operation. This is due to the construction of the cup shaped member 22 which per- mits the control valve assembly 18 to be located very close to the piston assembly 16.
  • the power passageways 48 and 56 are very short and relatively small, and thus contain a very small amount of hydraulic fluid. Since the compliance of hydraulic fluid is relatively high, the quantity of oil in the power passageways 48 and 56 can limit the upper frequency response of the genera ⁇ tor. Accordingly, pressure can be quickly applied and quickly released since a small volume of fluid is involved and thus very quick response to cyclic rate changes can be made and a fast cyclic rate (e.g. 250 Hertz) can be attained.
  • a fast cyclic rate e.g. 250 Hertz
  • a pilot valve 122 which receives pressurized fluid from the power valve 50 through a passageway 124.
  • a regulator 126 that modulates the pressure required to shift the position of the pilot valve 122.
  • the regulator 126 is responsive to the electronic system 20 and shifts the pilot valve 122 to the desired -11-
  • control valve assembly 18 including the valves 50, 122 and the regulator 126, has not been described in detail because they are purchased items.
  • control valve is manufactured by MOOG, Inc. of East Aurora, New York 14052.
  • the electronic system 20 receives signals from the operator of the generator 10 and from a linear variable differential transformer 128 that is moving with the power valve 50 so that the position of the power valve 50 is transmitted to the electronic system 20.
  • a second linear variable differential transformer 130 is located in the housing 12 and extends into con- tact with the piston assembly 16 so that the position of the piston assembly 16 is also transmitted to the electronic assembly 20.
  • the input to *the electronic system 20 of the desired cyclic rate by the operator is applied through the pilot valve 122 and the power valve 50 to the piston assembly 16 through the post 14 assembly to obtain the desired cyclic rate.
  • the power passageways are relatively small and relatively short so that a very small volume of hydraulic fluid is involved in the reciprocation of the piston assembly 16 and the cyclic rate can be effi ⁇ ciently and accurately controlled and changes thereto can be made quickly.
  • the generator is immersed in liquid, that the electronic assembly 20 has been provided with cyclic rate data, and that pressurized hydraulic fluid is being supplied by the pump 74 into the control valve assembly 18, that is, into the power valve 50 and into the pilot valve 122.
  • the piston assembly 16 is driven upwardly as the fluid enters the expansible power chamber 84. If for any unforseen reason, the piston assembly 16 overtravels and nears the upper end of its travel and before the surface 64 impacts the surface 86, the ports 116 move into communication with the chamber 84.
  • the linear variable differential transformer 130 (FIG. 1) signals the electronics apparatus 20 the position of the piston assembly 16.
  • the pilot valve 122 is shifted, causing shifting of the power valve 50 which in turn reverses the roles of the passageways 48 and 56. That is, the passageway 56 now becomes the supply passageway for the pressure fluid which enters into the expansible power chamber 88, moving the piston assembly 16 toward its lowermost position as illustrated in FIG. 4 and the passageway 48 serves to return fluid from the chamber 84.
  • the chamber 88 is brought into communication with the return passageway 66 through the lower ports 118, the annular space 120, and the upper ports 116.
  • the power driving the piston assembly 16 downwardly is substantially reduced.
  • a small portion of fluid is trapped in the power chamber 84 due to the location of the exit 52 of the passageway 48.
  • the fluid pressure that is generated therein that damps the downward movement of the piston assembly 16 is not imposed upon the upper seal 90 since such fluid pressure is vented outwardly through the drain passa ⁇ geway 98.
  • the foregoing detailed description sets forth a marine seismic generator that is quickly and easily changed from one cyclic rate to the other, one in which the cyclic rate is accurately and easily controlled, and one having an extended service life.
  • the extended service life results from the release of the fluid pressure from the power chambers so that the force driving the piston assembly stops prior to impact with the post assembly; the use of a small trapped volume for damping the movement of the piston assembly; and the relief protection provided to the main seals so that the high fluid pressure is not exerted thereacross.
  • Accuracy and rapidity of cyclic control and reciprocation is accomplished by posi ⁇ tioning the control valve assembly very close to the piston assembly 16 so that the passageways supplying the hydraulic fluid to cause reciprocation are small in volume.

Landscapes

  • Engineering & Computer Science (AREA)
  • Remote Sensing (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Acoustics & Sound (AREA)
  • Environmental & Geological Engineering (AREA)
  • Geology (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • General Physics & Mathematics (AREA)
  • Geophysics (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Disintegrating Or Milling (AREA)

Abstract

Un procédé et un appareil pour générer des vibrations sismiques dans un liquide comprennent un générateur (10) à moteur hydraulique et à commande électronique comprenant un agencement de piston (16) monté de façon alternative sur un montant cylindrique (14) dans le boîtier (12) du générateur. L'appareil de commande comprend une soupape de commande (18) située très près de l'agencement de piston (16), ce qui réduit le volume des conduites (48, 56) allant jusqu'à l'agencement de piston (16), de sorte que la vitesse cyclique de l'agencement de piston (16) peut être très rapide et peut être modifiée avec rapidité et précision. Une durée de vie plus longue est obtenue si l'on libère le fluide de haute pression qui actionne l'agencement de psiton (16) avant l'impact de l'agencement de piston (16) sur le montant (14) et si l'on forme des volumes enfermés de fluide dans les cavités (84, 88) afin d'amortir le mouvement de l'agencement de piston (16) vers le montant (14).
EP19850905171 1984-11-09 1985-10-04 Generateur sismique. Withdrawn EP0202246A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US67037884A 1984-11-09 1984-11-09
US670378 1984-11-09

Publications (2)

Publication Number Publication Date
EP0202246A1 true EP0202246A1 (fr) 1986-11-26
EP0202246A4 EP0202246A4 (fr) 1987-07-30

Family

ID=24690172

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850905171 Withdrawn EP0202246A4 (fr) 1984-11-09 1985-10-04 Generateur sismique.

Country Status (4)

Country Link
EP (1) EP0202246A4 (fr)
CA (1) CA1254296A (fr)
NO (1) NO862757L (fr)
WO (1) WO1986003015A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2981759B1 (fr) 2011-10-19 2014-07-18 Cggveritas Services Sa Procede et dispositif pour determiner un signal de commande pour des sources marines vibrosismiques
FR2981746B1 (fr) 2011-10-19 2014-11-21 Cggveritas Services Sa Source et procede d'acquisition sismique marine
FR2981758B1 (fr) 2011-10-19 2013-12-06 Cggveritas Services Sa .
US8619497B1 (en) 2012-11-15 2013-12-31 Cggveritas Services Sa Device and method for continuous data acquisition
US8724428B1 (en) 2012-11-15 2014-05-13 Cggveritas Services Sa Process for separating data recorded during a continuous data acquisition seismic survey

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4114722A (en) * 1976-08-24 1978-09-19 Texas Instruments Incorporated Broadband seismic energy source
EP0024117A2 (fr) * 1979-08-08 1981-02-25 Conoco Phillips Company Plaque de base et boîtier d'un transducteur sismique

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2882685A (en) * 1956-07-02 1959-04-21 Gleason Works Hydraulic motion transmitting system
US3329930A (en) * 1965-05-20 1967-07-04 Continental Oil Co Marine vibration transducer
US3365019A (en) * 1965-07-23 1968-01-23 Continental Oil Co Seismic vibrator for marshland and submarine use
US3349367A (en) * 1965-10-23 1967-10-24 Raytheon Co Electrohydrosonic transducer
US3745885A (en) * 1971-10-07 1973-07-17 Continental Oil Co Hydraulic vibrator
US4020744A (en) * 1974-11-13 1977-05-03 Raymond International Inc. Control of hydraulically powered equipment
US4265331A (en) * 1975-10-15 1981-05-05 Leonard Willie B Fluidic repeater
US4147228A (en) * 1976-10-07 1979-04-03 Hydroacoustics Inc. Methods and apparatus for the generation and transmission of seismic signals
US4106586A (en) * 1977-06-06 1978-08-15 Continental Oil Company Hydraulic vibrator
US4143736A (en) * 1977-11-03 1979-03-13 Continental Oil Company Seismic transducer construction
MX151343A (es) * 1979-08-08 1984-11-12 Conoco Inc Mejoras en transductor de frecuencia para generar ondas sismicas
US4516230A (en) * 1981-04-17 1985-05-07 Western Geophysical Company Of America Protective drive-level limiter for an electro-hydraulic vibrator

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4114722A (en) * 1976-08-24 1978-09-19 Texas Instruments Incorporated Broadband seismic energy source
EP0024117A2 (fr) * 1979-08-08 1981-02-25 Conoco Phillips Company Plaque de base et boîtier d'un transducteur sismique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO8603015A1 *

Also Published As

Publication number Publication date
EP0202246A4 (fr) 1987-07-30
CA1254296A (fr) 1989-05-16
NO862757D0 (no) 1986-07-08
NO862757L (no) 1986-09-08
WO1986003015A1 (fr) 1986-05-22

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Inventor name: WISOTSKY, SERGE, S.