`
`Case 6:12—cv—00799—JRG Document 124-4 Filed 03/07/14 Page 1 of 46 Page|D #: 3717Case 6:12—cv—00799—JRG Document 124-4 Filed 03/07/14 Page 1 of 46 Page|D #: 3717
`
`EXHIBIT 4
`
`
`
`EXHIBIT 4EXHIBIT 4
`
`
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 2 of 46 PageID #: 3718
`111111111111111111111111111111111111111111111111111111111111111111111111111
`US005373745A
`5,373,745
`[11] Patent Number:
`[45] Date of Patent: Dec. 20, 1994
`
`United States Patent [19]
`Cage
`
`[54] SINGLE PATH RADIAL MODE CORIOLIS
`MASS FLOW RATE METER
`Inventor: Donald R. Cage, Longmont, Colo.
`(75]
`(73] Assignee: Direct Measurement Corporation,
`Longmont, Colo.
`[21] Appl. No.: 167,719
`(22] Filed:
`Dec. 15, 1993
`
`Related U.S. Application Data
`(63] Continuation of Ser. No. 843,519, May 8, 1992, aban-
`doned, and Ser. No. 651,301, Feb. 5, 1991, abandoned.
`Int. CI.s ................................................ GOlF 1/78
`(51]
`(52] U.S. CI ................................ 73/861.37; 73/861.18
`[58] Field of Search ............ 73/861.37, 861.38, 861.18
`(56]
`Refereaces Cited
`U.S. PATENT DOCUMENTS
`Re. 31,450 11/1983 Smith .................................... 861!73
`3,927,565 12/1975 Pavlin ............................... 73/861.38
`4,109,524 8/1978 Smith .................................... 194/73
`4,420,983 12/1983 Langdon .......................... 73/861.18
`4,422,338 12/1983 Smith .................................... 861/73
`4,491,025 1/1985 Smith et al ............................ 861/73
`4,622,858 11/1986 Mizerak ................................ 861/73
`4,628,744 12/1986 Lew ...................................... 861/73
`4,653,332 3/1987 Simonsen .............................. 861/73
`4,680,974 7/1987 Simonsen et al ...................... 861/73
`4,691,578 9/1987 Herzl ..................................... 861/73
`4,716,771
`l/1988 Kane ..................................... 861/73
`4,728,243 3/1988 Friedland et al . .................... 861/73
`4,733,569 3/1988 Kelsey .............................. 73/861.38
`4,756,197 7/1988 Herzl ..................................... 861/73
`4,756,198 7/1988 Levien .................................. 861/73
`4,768,384 9/1988 Flecken et al ........................ 861/73
`4,776,220 10/1988 Lew ...................................... 861/73
`4,793,191 12/1988 Flecken et al . ....................... 861/73
`
`l/1989 Lew ...................................... 861/73
`4,798,091
`4,81l,606 3/1989 Hasegawa et al .................... 861/73
`4,823,614 4/ 1989 Dahlin ................................... 861/73
`4,831,885 5/1989 Dahlin ................................... 861/73
`4,852,410 8/ 1989 Corwon et al ........................ 861/73
`4,856,346 8/1989 Kane ..................................... 861/73
`l/1990 Mattar et al . ......................... 861/73
`4,891,991
`4,934,195_ 6/1990 Hussain ................................. 861/73
`4,949,583 8/1990 Lang et al . .
`5,024,104 6/1991 Dames .
`
`FOREIGN PATENT DOCUMENTS
`8607340 5/ 1986 France .
`8814606.5 11/1988 Germany .
`0272758 12/ 1987 Italy .
`62-180741 7/ 1987 Japan .
`1008617 3/ 1983 U.S.S.R. ........................... 73/ 861.37
`
`Primary Examiner-Walter E. Snow
`Assistant Examiner-Raymond Y. Mah
`Attorney, Agent, or Firm-Konneker Bush Hitt &
`Chwang
`
`[57]
`ABSTRACT
`A flow meter apparatus for measuring the mass flow
`rate of a fluid using the Coriolis principle. A single
`straight flow conduit is employed which is vibrated in a
`radial-mode of vibration. Coriolis forces are thereby
`produced along the walls of the flow conduit which
`deform the conduit's cross-sectional shape as a function
`of mass flow rate. Additional embodiments are dis(cid:173)
`closed employing vibration of selected portions of the
`flow conduit walls. In addition, a method is described to
`determine the pressure and the density of a fluid by
`simultaneously vibrating a flow conduit in two modes
`of vibration and thereby determining pressure and den(cid:173)
`sity based on changes in each frequency.
`38 Claims, 27 Drawing Sheets
`
`23
`
`28
`
`MM0636063
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 3 of 46 PageID #: 3719
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 1 of 27
`
`5,373,745
`
`FIG. 1
`
`MM0636064
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 4 of 46 PageID #: 3720
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 2 of 27
`
`5,373,745
`
`MM0636065
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 5 of 46 PageID #: 3721
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 3 of 27
`
`5,373,745
`
`CXJ
`C\1
`
`MM0636066
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 6 of 46 PageID #: 3722
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 4 of 27
`
`5,373,745
`
`MM0636067
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 7 of 46 PageID #: 3723
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 5 of 27
`
`5,373,745
`
`3 - -
`
`FIG 5
`
`6
`
`3 - -
`
`FIG 6
`
`6
`
`3 - -
`
`5
`
`FIG 7
`
`6
`
`4
`
`4
`
`4
`
`1
`
`1
`
`MM0636068
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 8 of 46 PageID #: 3724
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 6 of 27
`
`5,373,745
`
`FORCE
`
`CORIOLIS FORCE DISTRffiUTION
`ALONG TOP SURFACE OF CONDUIT
`
`----1[>
`
`CORIOIJS FORCE DISTRffiUTION
`ALONG BOTTOM SURFACE OF CONDUIT
`
`FIG 8
`
`3
`
`FIG 9
`
`MM0636069
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 9 of 46 PageID #: 3725
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 7 of 27
`
`5,373,745
`
`3 - -
`
`FIG 9A
`
`3-~
`
`FIG 9B
`
`6
`
`3 - -
`
`FIG 9C
`
`4
`
`4
`
`- - - -8
`
`4
`
`1
`
`1
`
`MM0636070
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 10 of 46 PageID #: 3726
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 8 of 27
`
`5,373,745
`
`1
`
`.
`
`I
`I
`
`, ....
`FIG 10
`... /-·
`I -·-·-·~
`\ "
`I
`'
`'
`I
`I
`'
`I
`\
`/ ...
`\
`-\
`\·-·-·-·-J
`,_/
`'
`
`/
`
`1
`
`FIG 11
`
`FIG 12
`
`FIG 13
`
`MM0636071
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 11 of 46 PageID #: 3727
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 9 of 27
`
`5,373,745
`
`SIGNALS IN PHASE
`WITH NO FLOW RATE
`
`FIG
`
`14
`
`16
`
`15
`
`~'
`
`--'---
`
`,, ,
`/"
`
`/ ,
`I ,
`
`SIGNALS SHIFI'
`WITH FLOW RATE
`
`FIG 15
`
`MM0636072
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 12 of 46 PageID #: 3728
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 10 of 27
`
`5,373,745
`
`15
`
`16
`
`DETERWINE
`FLOW
`RATE
`
`18
`
`DRIVE
`CIRCUIT
`
`9
`
`17
`
`30
`
`RTD
`
`RTD
`
`41
`
`FIG 16
`
`25-~
`
`23
`
`28
`
`FIG 17
`
`MM0636073
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 13 of 46 PageID #: 3729
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 11 of 27
`
`5,373,745
`
`25
`
`28
`
`FIG 18
`
`28
`
`20
`
`21E
`
`21D
`
`FIG 19
`
`MM0636074
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 14 of 46 PageID #: 3730
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 12 of 27
`
`5,373,745
`
`FREQUENCY
`RESPONSE
`CURVE
`
`0--- -----------~---------------------
`/
`DRIVE FREQUENCY
`1 1
`RESPONSE FREQUENCY
`
`FIG 20
`
`TOP SURFACE
`FORCE PROFILE
`
`BO'M'ON SURFACE
`FORCE PROFILE
`
`FIG 21
`
`MM0636075
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 15 of 46 PageID #: 3731
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 13 of 27
`
`5,373,745
`
`40
`
`39
`
`38
`
`34
`
`38
`
`35
`
`/.,.. _/.,_
`
`, .~ ·-·-- .....
`
`/
`
`/
`
`/
`
`16
`
`/
`
`/
`
`'
`'
`' ·
`
`'
`., _
`,
`,
`
`/
`
`/
`
`/
`
`,
`,
`,
`,
`
`/
`
`37
`
`36
`
`/ ,
`
`FIG 22
`, .... -.............
`...... ,
`'
`'
`'
`'
`'
`'
`'
`'
`'
`'
`
`FIG 23A
`
`FIG 23B
`
`MM0636076
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 16 of 46 PageID #: 3732
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 14 of 27
`
`5,373,745
`
`FIG 24
`
`1
`
`MM0636077
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 17 of 46 PageID #: 3733
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 15 of 27
`
`5,373,745
`
`117--
`
`118
`
`111
`
`112
`
`160
`
`161
`
`109
`
`128
`
`121
`
`114
`X
`116 y~
`
`115
`
`104
`
`FIG. 25
`
`129
`
`MM0636078
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 18 of 46 PageID #: 3734
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 16 of 27
`
`5,373,745
`
`130
`146
`
`TEMP
`
`112 (
`
`(
`
`115
`
`118
`
`(
`
`(
`121
`
`134
`
`PROCESSOR
`
`MASS FLOW RATE
`PRESSURE
`DENSITY
`TEMP
`VISCOSITY
`USER
`DEFINED
`
`Q:
`
`~ ra:t
`
`~
`0
`Q ~
`
`165
`
`144
`
`PRIMARY
`DRIVE
`
`136
`
`145
`
`SECONDARY
`DRIVE
`
`137
`
`139
`
`138
`FIG. 26
`
`166
`
`MM0636079
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 19 of 46 PageID #: 3735
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 17 of 27
`
`5,373,745
`
`FIG. 27
`
`MM0636080
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 20 of 46 PageID #: 3736
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 18 of 27
`
`5,373,745
`
`153
`
`FIG. 29
`
`---152
`
`154
`
`155
`
`FIG. 30
`
`MM0636081
`
`157
`
`158--
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 21 of 46 PageID #: 3737
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 19 of 27
`
`5,373,745
`
`Lz
`
`104---
`
`Lz
`
`104---
`
`104--
`
`101
`
`FIG. 31
`
`101
`
`FIG. 32
`
`--101
`
`FIG. 33
`
`MM0636082
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 22 of 46 PageID #: 3738
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 20 of 27
`
`5,373,745
`
`153
`
`FIG. 34
`
`153
`
`FIG. 35
`
`153
`
`FIG. 36
`
`MM0636083
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 23 of 46 PageID #: 3739
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 21 of 27
`
`5,373,745
`
`155
`
`FIG. 37
`
`155
`
`FIG. 38
`
`155
`
`FIG. 39
`
`MM0636084
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 24 of 46 PageID #: 3740
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 22 of 27
`
`5,373,745
`
`----163
`
`112 - - -
`
`160
`
`161-~
`
`y~
`
`FIG. 40
`
`162
`
`MM0636085
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 25 of 46 PageID #: 3741
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 23 of 27
`
`5,373,745
`
`108
`
`101---
`
`117
`
`111
`
`160
`
`161
`
`109
`
`126
`
`120
`
`104
`
`114 y~
`
`107
`
`105
`
`FIG. 41
`
`129
`
`MM0636086
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 26 of 46 PageID #: 3742
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 24 of 27
`
`5,373,745
`
`200
`
`Lx
`
`FIG. 42
`
`FIG. 43
`
`202
`
`202
`
`203
`
`FIG. 44
`
`FIG. 45
`
`201
`
`MM0636087
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 27 of 46 PageID #: 3743
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 25 of 27
`
`5,373,745
`
`168
`
`101
`
`168
`
`L
`
`L
`
`168
`
`FIG. 46
`
`106
`
`FIG. 47
`
`168
`
`FIG. 48
`
`FIG. 49
`
`MM0636088
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 28 of 46 PageID #: 3744
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 26 of 27
`
`5,373,745
`
`FIG. 50
`
`PRESSURE
`
`DENSITY
`
`Primary
`
`FIG. 52
`
`TEMPERATURE
`
`MM0636089
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 29 of 46 PageID #: 3745
`
`U.S. Patent
`
`Dec. 20, 1994
`
`Sheet 27 of 27
`
`5,373,745
`
`179 ,-----.,*"[ ..... --,======[>
`
`173
`
`FIG. 53
`
`181
`
`FIG. 54
`
`FIG. 55
`
`MM0636090
`
`
`
`Case 6:12-cv-00799-JRG Document 124-4 Filed 03/07/14 Page 30 of 46 PageID #: 3746
`
`1
`
`.§,373,745
`
`2
`number of problems which preclude the use of Coriolis
`technology in many applications that would benefit
`from its use.
`Among the problems caused by the flow splitters and
`5 curved flow conduits are: (1) excessive fluid pressure(cid:173)
`drop caused by turbulence and drag forces as the fluid
`passes through the flow splitters and curves of the de(cid:173)
`vice, (2) difficulty in lining or plating the inner surface
`of geometries having flow splitters and curved flow
`10 conduits, with corrosive resistant materials, (3) inability
`to meet food and pharmaceutical industry sanitary re(cid:173)
`quirements such as polished surface fmish, non-pluga(cid:173)
`ble, self-draining, and visually inspectable, (4) difficulty
`in designing a case to surround dual curved flow con-
`15 duits which can contain high rated pressures, (5) diffi(cid:173)
`culty in designing flow meters for 6" diameter and
`larger pipelines and (6) difficulty in reducing the cost of
`current designs due to the added value of flow splitters,
`dual flow conduits and curved flow conduit fabrication.
`It is therefore recognized that a Coriolis mass flow
`rate meter employing a single straight flow conduit
`would be a tremendous advancement in the art. It is the
`object of the present invention therefore to disclose a
`means whereby a Coriolis mass flow rate meter can be
`created using a single straight flow conduit thereby
`eliminating the problems caused by flow splitters, dual
`flow paths and curved conduits while retaining the
`current advantages of balance and symmetry.
`
`SINGLE PATH RADIAL MODE CORIOLIS MASS
`FLOW RATE METER
`
`RELATED APPLICATION
`This is a continuation of application Ser. No.
`07/843,519, abandoned filed May 8, 1992 and Ser. No.
`07/651,301, filed Feb. 5, 1991 now abandoned.
`
`TECHNICAL FIELD OF THE INVENTION
`This invention relates to Coriolis mass flow rate me(cid:173)
`ters and, in particular, to Coriolis mass flow rate meters
`using a single straight flow conduit to measure mass
`flow rate.
`
`SUMMARY OF THE INVENTION
`
`BACKGROUND OF THE INVENTION
`In the art of Coriolis mass flow rate meters it is well
`known that a vibrating flow conduit carrying mass flow
`causes Coriolis forces which deflect the flow conduit
`away from its nomial vibration path proportionally 20
`related to mass flow rate. These deflections or their
`effects can then be measured as an accurate indication
`of mass flow rate.
`This effect was first made commercially successful by
`Micro Motion Inc. of Boulder Colo. Early designs em- 25
`ployed a single vibrating U-shaped flow conduit which
`was cantilever mounted from a base. With nothing to
`counter-balance the vibration of the flow conduit, the
`design was highly sensitive to mounting conditions and
`so was redesigned to employ another mounted vibrating 30
`arrangement which acted as a counter-balance for the
`The foregoing has outlined rather broadly the fea-
`flow conduit similar to that disclosed in their U.S. Pat.
`tures and technical advantages of the present invention
`Nos. Re. 31,450 and 4,422,338 to Smith. Problems oc-
`in order that the detailed description of the invention
`curred however since changes in the specific gravity of
`the process-fluid were not matched by changes on the 35 that follows may be better understood. Additional fea-
`tures and advantages of the invention will be described
`counter-balance, an unbalanced condition could result
`causing errors. Significant improvement was later made
`hereinafter which form the subject of the claims of the
`invention. It should be_ appreciated by. those s~ed in
`by replacing the counter-balance arrangement by an-
`other U-shaped flow conduit identical to the first and
`t~e art that the concep~10n ~d the spectfi~ embodrm_ent
`splitting the flow into parallel paths, flowing through 40 ~:bsclosed ~a~ be readily utiltzed as a basts ~or modtfy-
`both conduits simultaneously. This parallel path Corio-
`mg or destgmng other struc~res ~or carrymg out the
`lis mass flow rate meter (U.S. Pat. No. 4,491,025 to
`sam~ purposes ofth~ pre~nt mventlon. It should ~so be
`Smith et al.) solves this balance problem and has thus
`realized by those skilled m the art that such eqwvalent
`become the premier method of mass flow measurement
`constructions do not depart from the spirit and scope of
`in industry today.
`45 the invention as set forth in the appended claims.
`Many other flow conduit geometries have been in-
`According to the object of the present invention, a
`vented which offer various performance enhancements
`Coriolis mass flow rate meter is herein provided utiliz-
`er alternatives. Examples of different flow conduit ge-
`ing a single straight flow conduit and a unique vibration
`ometries are the dualS-tubes of U.S. Pat. Nos. 4,798,091
`method thereby eliminating the problems caused by
`and 4,776,220 to Lew, the omega shaped tubes of U.S. 50 flow splitters and curved flow conduits while retaining
`the current advantages of balance and symmetry.
`Pat. No. 4,852,410 to Corwon et al., the B-shapes tubes
`of U.S. Pat. No. 4,891,991 to Mattar et al., the helically
`The basic operation of a commercially available Con-
`wound flow conduits of U.S. Pat. No. 4,756,198 to
`olis mass flow rate meter according to current art will
`Levien, figure-S shaped flow conduits of U.S. Pat. No.
`now be described. Normally two process-fluid filled
`4,716,771 to Kane, the dual straight tubes of U.S. Pat. 55 flow conduits are employed in a parallel-path or serial(cid:173)
`· path configuration. The two flow conduits form a hal-
`No. 4,680,974 to Simonsen et al. and others. All of these
`geometries employ the basic concept of two parallel
`anced resonant system and as such are forced to vibrate
`flow conduits vibrating in opposition to one another to
`in a prescribed oscillatory bending-mode of vibration. If
`create a balanced resonant vibrating system.
`the process-fluid is flowing, the combination of fluid
`Although the parallel path Corio lis mass . flow rate 60 motion and conduit vibration causes Corio lis forces
`meter has been a tremendous commercial success, sev-
`which deflect the conduits away from their normal (no
`eral problems remain. Most of these problems are a
`flow) paths of vibration proportionally related to mass
`consequence of using flow splitters and two parallel
`flow rate. These deflections, or their effects, are then
`flow conduits in order to maintain a balanced resonant
`measured as an accurate indication of mass flow rate.
`system. In addition, most designs employ flow conduits 65 As previously described, only one flow conduit is
`that are curved into various shapes as previously de-
`necessary for measuring mass flow rate in this manner.
`scribed to enhance the sensitivity of the device to mass
`However, to achieve the superior performance afforded
`flow rate. These two common design features cause a
`by a balanced resonant system, it's necessary to counter-
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`conduit of a Coriolis mass flow rate meter, a single
`straight flow conduit is employed, fixedly attached at
`both ends, and vibrated in a radial-mode of vibration
`where the wall of the flow conduit translates and/or
`rotates away from its" rest position in an oscillatory
`manner, and the center-line of the flow conduit remains
`essentially unchanged. The combination of fluid motion
`and radial-mode vibration causes a Coriolis force distri(cid:173)
`bution along the moving wall of the flow conduit which
`10 alters the cross-sectional shape of the conduit as a func(cid:173)
`tion of mass flow rate. This altered shape or its effects,
`are then measured as an accurate indication of mass
`flow rate. Since this radial mode of vibration causes
`substantially no net reaction forces where the conduits
`are mounted, a balanced resonant system Coriolis mass
`flow rate meter is thereby created with no flow split-
`ters, curved flow conduits, or counter-balance devices.
`In addition, a unique non-intrusive method is em(cid:173)
`ployed to determine the pressure and the density of the
`fluid inside the flow conduit by simultaneously vibrat(cid:173)
`ing the flow conduit in two modes of vibration. The
`values of the frequencies of the two modes of vibration
`are functionally related to both the fluid density and the
`pressure difference between the inside and the outside
`of the flow conduit.
`Due to the unique operation of the invention, and its
`ability to directly measure mass flow rate, fluid density,
`temperature and pressure, virtually any defmed static or
`dynamic fluid parameter can be calculated such as fluid
`state, viscosity, quality, compressibility, energy flow
`rate, net flow rate, etc.
`As an alternate to using a radial-mode of vibration
`involving the entire wall of the flow conduit as previ(cid:173)
`ously described, a portion of the flow conduit perimeter
`can be vibrated as necessary to generate Coriolis forces.
`This method is well suited for use in flow conduits of
`very large size and non-circular shapes where vibration
`of the entire conduit is not practical. This method is also
`well suited to flow conduits formed into bulk materials
`thus having several rigid sides incapable of entire(cid:173)
`perimeter radial mode vibration, such as a flow conduit
`etched into silicon or quartz to form a micro flow me(cid:173)
`ter.
`The present invention solves the previously men(cid:173)
`tioned problems caused by flow splitters, curved flow
`conduits and imbalance and allows Coriolis mass flow
`meter technology to be used in areas such as sanitary
`applications, gas flow, air flow meters for weather sta(cid:173)
`tions, airplanes, low pressure air-duct systems, micro
`flow meters, liquid flow meters for residential, indus(cid:173)
`trial, oceanographic and shipboard use, and many more.
`
`3
`balance the reaction forces from the forced vibration,
`thus a second flow conduit is normally employed. For
`very small meter designs the mass and stiffness proper(cid:173)
`ties of the mounting conditions can be sufficiently great
`to counteract the reaction forces from the forced vibra- 5
`tion thereby allowing the use of only one flow conduit.
`Accordingly, Micro Motion Inc. presently offers only
`their two smallest flow meters, the model D6 (1/16"
`line size) and the model D12 (i" line size) in a single
`curved flow conduit configuration.
`A single straight flow conduit while solving the
`aforementioned problems caused by flow splitters and
`curved conduits, has therefore not been commercially
`successful in Coriolis mass flow rate meter designs,
`especially for large flow conduits. This failure is due to 15
`the inherent imbalance of a single straight flow conduit
`in any natural bending-modes of vibration. A straight
`flow conduit fixedly mounted at both ends has a number
`of natural bending-modes of vibration wherein the cen(cid:173)
`ter-line of the conduit deflects or rotates away from its 20
`rest position in a number of half sine-shaped waves
`along the length of the conduit. Higher frequency bend(cid:173)
`ing-modes involve increasing numbers of these half
`sine-shaped waves in integer multiples. Each of these
`bending-modes causes reaction forces applied to the 25
`conduit mounts creating balance and accuracy prob(cid:173)
`lems analogous to the single curved flow conduit mod-
`els previously described. A single straight tube design
`of this nature is disclosed in U.S. Pat. No. 4,823,614 to
`Dahlin, in which the flow tube cross-section is perma- 30
`nently deformed in several locations as shown in its
`FIGS. 2A-2D to enhance its bending in a "higher(cid:173)
`mode" such as its FIG. 3B. The higher modes of vibra(cid:173)
`tion as shown in the Dahlin patent FIGS. 3A-3E all
`show the flow conduit bending away from a straight 35
`line at its ends which will cause reaction torques and
`forces at the mounts. These reactions are not counter
`balanced and thus can create reaction forces as previ(cid:173)
`ously described. Dahlin states that this embodiment can
`be used in "average" sized pipes with average being 40
`defined as ! to ~ inch inside diameter. Although the
`reason for this size restriction is not explained, it is prob(cid:173)
`ably a consequence of imbalance from using a bending(cid:173)
`mode of vibration with no counter-balance apparatus.
`The unique advantages of the present invention ac- 45
`crue from the use of a single straight flow conduit in a
`radial-mode of vibration instead of a bending-mode as is
`currently used in the art. For clarity, the term "bending(cid:173)
`mode" is defined as a vibration mode wherein the cen(cid:173)
`ter-line or axis of the flow conduit translates and/or 50
`rotates away from its rest position in an oscillatory
`manner while the cross-sectional shape of the flow con(cid:173)
`duit remains essentially unchanged. By contrast, the
`term "radial-mode" is defined as a vibration mode
`wherein the center-line or axis of the flow conduit re- 55
`mains essentially unchanged while all or a part of the
`wall of the flow conduit translates and/or rotates away
`from its rest position in an oscillatory manner. Common
`examples of radial-modes of vibration are the natural
`vibration of a bell or wine glass. In these two. examples 60
`the fundamental radial-mode of vibration causes the
`normally round cross-sectional shape of the free end of
`the bell or wine glass to deflect into an oscillating ellip(cid:173)
`tical shape. Since the center-line or axis of this radial(cid:173)
`mode stays essentially unchanged, the stem (in the wine 65
`glass example) can be held without feeling or interfering
`with the vibration, exemplifying the absence of reaction
`forces at the mount. Applying this idea to the flow
`
`BRIEF DESCRIPTION OF THE DRAWINGS
`For a more complete understanding of the present
`invention, and the advantages thereof, reference is now
`made to the following descriptions taken in conjunction
`with the accompanying drawings, in which:
`FIG. 1 is a perspective view of one possible preferred
`exemplary embodiment of the present invention with a
`portion of the outer case cut away for viewing the appa(cid:173)
`ratus inside;
`FIG. 2 is a cross-sectional view of the embodiment of
`FIG. 1 showing the radial-mode vibration shape of the
`flow conduit where it has reached its peak deflection in
`the vertical direction;
`FIG. 3 is a cross-sectional view of the embodiment of
`FIG. 1 showing the radial-mode vibration shape of the
`flow conduit where it has reached its undeflected center
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`position. This is also representative of the flow con(cid:173)
`duits' rest position;
`FIG. 4 is a cross-sectional view of the embodiment of
`FIG. 1 showing the radial-mode vibration shape of the
`flow conduit where it has reached its peak deflection in 5
`the horizontal direction;
`FIG. 5 is a cross-sectional view along section A-A
`in FIG. 2 showing the elliptical cross-sectional shape of
`the flow conduit at its peak deflection in the vertical
`direction;
`FIG. 6 is a cross-sectional view along section A-A
`of FIG. 3 showing the circular cross-sectional shape of
`the flow conduit as it passes through. its undeflected
`center position;
`FIG. 7 is a cross-sectional view along section A-A 15
`in FIG. 4 showing the elliptical cross-sectional shape of
`the flow conduit at its peak deflection in the horizontal
`direction;
`FIG. 8 is a graph of the Coriolis force distribution 20
`that would be created along the top and bottom surfaces
`of the flow conduit from mass flow rate, as the flow
`conduit passes through its undeflected center position as
`in FIG. 3;
`FIG. 9 is a cross-sectional view similar to that of 25
`FIG. 3 showing greatly exaggerated representative
`deflections of the flow conduit resulting from the Cori(cid:173)
`olis force distribution shown in FIG. 8;
`FIG. 9A is a cross-sectional view along section B-B
`of FIG. 9 showing the deformation of the cross-sec- 30
`tional shape of the flow conduit (greatly exaggerated)
`due to Coriolis forces, as the flow conduit passes
`through its center (normally undeformed) position;
`FIG. 9B is a cross-sectional view along section A-A
`of FIG. 9 showing essentially no deformation of the 35
`cross-sectional shape of the flow conduit due to Corio lis
`forces, as the flow conduit passes through its center
`position;
`FIG. 9C is a cross-sectional view along section C-C
`of FIG. 9 showing the deformation of the cross-sec- 40
`tional shape of the flow conduit (greatly eXaggerated)
`due to Coriolis forces, as the flow conduit passes
`through its center (normally undeformed) position;
`FIG. 10 is a cross-sectional representation of the
`two-lobe radial-mode vibration of the flow conduit in 45
`the preferred exemplary embodiment of FIG. 1 shown
`with three sequential deflected shapes (peak vertical,
`undeflected, peak horizontal) superimposed on each
`other;
`FIG. 11 is a cross-sectional representation of an alter- 50
`nate radial-mode of vibration to that shown in FIG. 10
`with three sequential deflected shapes superimposed on
`each other;
`FIG. 12 is cross-sectional representation of an alter- 55
`nate radial-mode of vibration to that shown in FIG. 10
`with two sequential deflected shapes superimposed on
`each other;
`FIG. 13 is cross-sectional representation of an alter(cid:173)
`nate radial-mode of vibration to that shown in FIG. 10 60
`with two sequential deflected shapes superiniposed on
`each other;
`FIG. 14 is a representation of the time relationship of
`signals from the motion detectors of FIG. 1 with no
`fluid flowing through the flow conduit;
`FIG. 15 is a representation of the time relationship of
`signals from the motion detectors of FIG. 1 with fluid
`flowing through the flow conduit;
`
`65
`
`6
`FIG. 16 is a block diagram of one possible configura(cid:173)
`tion of circuit components used to measure mass flow
`rate according to the present invention;
`FIG. 17 is a perspective view of an alternate to the
`preferred exemplary embodiment of FIG. 1 using a
`vibrating flexible surface as part of a rectangular flow
`conduit perimeter to measure the mass flow rate in the
`conduit;
`FIG. 18 is a cross-sectional view through the embodi(cid:173)
`ment of FIG. 17 showing three sequential deflected
`shapes of the vibrating flexible surface with no fluid
`flow;
`FIG. 19 is a cross-sectional view through the embodi(cid:173)
`ment of FIG. 17 showing the deflected shape of the
`vibrating flexible surface due to Coriolis forces with
`fluid flowing through the flow conduit;
`FIG. 20 is a graph of the frequency response curve
`and is representative of the absolute value of equation
`No.1;
`FIG. 21 is a representation of the Coriolis force distri(cid:173)
`bution along the top and bott()m surfaces of the flow
`conduit resulting from driving the flow conduit in a
`mode shape similar to that shown in FIG. 9;
`FIG. 22 is an alternate exemplary embodiment of the
`present invention employing a flow conduit that has
`several rigid sides and a flexible surface that is vibrated;
`FIG. 23A is a representation of the signals from the
`motion detectors of FIG. 1, and their sum with one of
`the signals inverted and with no flow through the flow
`conduit;
`FIG. 23B is a representation of the signals from the
`motion detectors of FIG. 1, and their sum with one of
`the signals inverted and with flow through the flow
`conduit;
`FIG. 24 is a cross-sectional view of an exemplary
`stress decoupling joint used to eliminate axial stress
`from the flow conduit;
`FIG. 25 is an alternate exemplary embodiment of the
`present invention employing a plurality of motion de(cid:173)
`tectors, vibration isolation means, and axial stress reduc(cid:173)
`tion means;
`FIG. 26 is a block diagram of one possible configura(cid:173)
`tion of circuit components used to measure the mass
`flow rate of fluid and other parameters according to the
`present invention;
`FIG. 27 is a representation of various wave forms
`that can be attained at various points in the circuit of
`FIG. 26;
`FIG. 28 is a cross sectional view through the motion
`drivers of the embodiment of FIG. 25;
`FIG. 29 is an alternate arrangement of motion drivers
`to that shown in FIG. 28, using three motion drivers
`instead of two;
`FIG. 30 is an alternate arrangement of motion drivers
`to that shown in FIG. 28, using four motion drivers
`instead of two;
`FIG. 31 is a representation of the primary radial vi(cid:173)
`bration motion induced by the motion drivers on the
`embodiment of FIG. 25, at a point in time when the
`flow conduit is elliptically elongated in the vertical
`direction;
`FIG. 32 is a representation of the primary radial vi(cid:173)
`bration motion induced by the motion drivers on the
`embodiment of FIG. 25, at a point in time when the
`flow conduit is elliptically elongated in the horizontal
`direction;
`FIG. 33 is a representation of the secondary bending
`vibration motion induced by the motion drivers on the
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`conduit is passing through its normally circular central
`position after having been elliptically elongated in the
`Y-direction;
`FIG. 48 is an exemplary representation of the general
`5 shape of flow conduit deflection in the X-Yplane due to
`the Coriolis force distribution shown in FIG. 46, where
`the magnitude of the deflection is greatly exaggerated
`for clarity;
`FIG. 49 is an exemplary representation of the general
`10 shape of flow conduit deflection in t