CA3092958A1 - Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump - Google Patents
Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump Download PDFInfo
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- CA3092958A1 CA3092958A1 CA3092958A CA3092958A CA3092958A1 CA 3092958 A1 CA3092958 A1 CA 3092958A1 CA 3092958 A CA3092958 A CA 3092958A CA 3092958 A CA3092958 A CA 3092958A CA 3092958 A1 CA3092958 A1 CA 3092958A1
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- flywheel
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- pump system
- torsional vibration
- vibration damper
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
ALONGSIDE TORSIONAL VIBRATION DAMPER ASSEMBLY FOR
SINGLE ACTING RECIPROCATING PUMP
Background Technical Field [0001] The present disclosure relates to single acting reciprocating pumps and, more specifically, to single mass flywheels and torsional vibration dampers for use with single acting reciprocating pumps.
Discussion of Related Art
As the reciprocating pump is cycled, movement of the slugs create pressure fluctuations within fluid downstream of the pump. This pressure fluctuation may create "hydraulic fluid pulsation" within the pump that is added to the operating pressure of the pump. The hydraulic fluid pulsation may be transferred upstream to driving equipment used to drive the pump in the form of torque output variances. The driving equipment may include one or more components including, but not limited to, a driveshaft, an engine, a transmission, or a gearbox.
Problematically, each reciprocating pumps operating in the field generally have their own torsional vibration frequency and amplitude profile that is dependent upon the selected operational pressure and rate. Another problem arises when a group of reciprocating pumps are Date Recue/Date Received 2020-09-11 connected to a common discharge line. In this operational scenario, reciprocating pumps may begin to synchronize such that the natural sinusoidal wave form of one pump will begin to mirror that of another pump from the group, which promotes pressure spikes and torsional distortion of even higher amplitude to pulsate through the drive lines.
Summary
i.e., to reduce or eliminate pump imposed high frequency/low amplitude and low frequency/high amplitude torsional vibrations.
Date Recue/Date Received 2020-09-11 Further, at least one torsional vibration dampener may be connected to the drive-train system to dampen the harmonic effects of the reciprocating pump. According to some embodiments, the at least one flywheel and the at least one torsional damper may not require electrical control to be able to function, but it is contemplated that electrical sensors and instrumentation may be present to monitor the condition of the drive line.
The vibration dampening assembly may include at least one flywheel that is operably connected to the input shaft and is configured to rotate therewith. The input shaft may include an input flange that is connected to the driveshaft. According to some embodiments, the at least one flywheel may comprise a first flywheel.
According to some embodiments, the at least one torsional vibration damper may comprise a first torsional vibration damper that may be connected to the input flange of the pump, may be connected to the output flange of the driving equipment, and/or may be connected to the first flywheel.
Date Recue/Date Received 2020-09-11
of the torque variance within the pump system as a result of hydraulic fluid pulsation within the pump. The first portion may be greater than, lesser than, or equal to the second portion. Sizing the flywheel may include sizing the first flywheel to have the first desired moment of inertia and sizing the second flywheel to have the second desired moment of inertia.
Furthermore, it is to be understood that the features of the various embodiments described herein are not mutually exclusive and may exist in various combinations and permutations.
Brief Description of the Drawings
3 according to an embodiment of the disclosure.
Date Recue/Date Received 2020-09-11
Detailed Description
In some embodiments, the driving equipment 100 includes a driveshaft, a transmission, a gearbox, or an engine, e.g., an internal combustion engine or a gas turbine engine. The driving equipment 100 includes an output shaft 110 that has an output flange 112. The driving equipment 100 is configured to rotate the output shaft 110 about a longitudinal axis thereof. The driving equipment 100 may include an engine and a transmission, gearbox, and/or power transfer case that may be configured to increase a torque and decrease a rotational speed of the output shaft 110 relative to a driveshaft of the engine or that may be configured to decrease a torque and increase a rotational speed of the output shaft Date Recue/Date Received 2020-09-11 110 relative to a driveshaft of the engine. The pump 300 includes in input shaft 310 having an input flange that is configure to receive input from the driving equipment 100 in the form of rotation of the input flange about a longitudinal axis of the input shaft 310.
Specifically, the hydraulic fluid pulsation results in torque variations in a crank/pinion mechanism of the pump 300 that are transferred upstream as torque output variations at the input shaft 310 of the pump 300. These torque output variations may create a torsional shock Ts at the output flange 112 of the output shaft 110. A single large torsional shock Ts may damage components of the driving equipment 100. In addition, an accumulation of minor or small torsional shocks Ts may decrease a service life of one or more of the com ponents of the driving equipment 100.
In one aspect, the at least one flywheel may comprise a flywheel 22 that is connected to the output flange 112 and disposed about the upstream portion 210 of the driveshaft 200.
In some embodiments, the flywheel 22 may be connected to the output flange 112 and be disposed about the output shaft 110.
KE = 1 - (I co) 2 (1) As noted above, the driving equipment 100 is configured to rotate at a constant angular velocity "w" such that with a known "KE" or a known moment of inertia "F' the other of the "KE" or the moment of inertia "F' may be calculated. In addition, the moment of inertia "F' of the flywheel 22 is dependent on the mass "m" and the radial dimensions of the flywheel 22 and may be expressed as:
m(ri2-Fr22) i = (2) where ri is a radius of rotation and r2 is a flywheel radius as shown in Figure 3. This equation assumes that the flywheel 22 is formed of a material having a uniform distribution of mass. In some embodiments, the flywheel 22 may have a non-uniform distribution of mass where the mass is concentrated away from the center of rotation to increase a moment of inertia "F' of the flywheel 22 for a given mass. It will be appreciated that the mass may be varied for a given a radius of rotation ri and a given a flywheel radius r2 by varying a thickness "h" of the flywheel 22 in a direction parallel an axis of rotation of the flywheel 22 as shown in Figure 4.
Date Recue/Date Received 2020-09-11
Initially, equation (1) is used to calculate a desired moment of inertia "I"
of the flywheel 22 solving for the "KE" of the torque variance created by the pressure spike Ps for a given angular velocity "w" of the flywheel 22. For example, the angular velocity "w"
of the output shaft 110 may be 152.4 radians/second with the "KE" of the torque variance created by the pressure spike Ps being 12,097 N-m. Solving equation (1) provides a desired moment of inertia "I" of the flywheel 22 as 1.047 kg m2.
Date Recue/Date Received 2020-09-11
may be manipulated such that the flywheel 22 has dimensions and a mass that are optimized for a particular application. Referring to Figure 4, for example and not meant to be limiting, a 10 kg flywheel with an outer radius "r2" of 0.45 m has the same moment of inertia as a 100 kg flywheel with an outer radius "r2" of 0.13 m such that either the 10 kg flywheel or the 100 kg flywheel would have the same "KE" to absorb the "KE"
of the torque variance created by the pressure spike Ps.
away from axis of rotation "AR" of the flywheel 22. It is important to choose a material for the flywheel 22 that is capable of withstanding the rotational stresses of the flywheel 22.
To determine the rotational stresses of the flywheel 22, the flywheel may be treated as a thick-walled cylinder to calculate the tangential and radial stresses thereof.
The calculations detailed below assume that the flywheel 22 has a uniform thickness "h", the flywheel radius "r2" is substantially larger than the thickness "h" (e.g., r2>5h), and the stresses are constant over the thickness "h". The tangential stress " ot" and radial stress " r" of the flywheel 22 may be expressed as follows:
r 2fr 2 \
Gt 19602 ( -v8 tr 12 r2 2 _ (r A2 )) rd 3+v "
(3) = 1,602 (3-v8 tr 2 r22 _ 2(r2\ _ (rd2)) rd (4) Date Recue/Date Received 2020-09-11 where p is a mass density (Iblin3) of the material of the flywheel 22, w is the angular velocity (rad/s) of the flywheel 22, and v is the Poisson's ratio of the flywheel 22. As shown in FIGURE 7, when the inner radius ri is 2.5 inches and the outer radius r2 is 8.52 inches the maximum tangential stress " ot" is 1027 psi at 2.5 inches from the axis of rotation and the maximum radial stress " or" is 255 psi at 4.5 inches from the axis of rotation.
Specifically, the flywheel 22 may be installed to the output flange 112 as described above or to the input flange of the pump as described below. For the purposes of this analysis, it will be assumed that the flywheel 22 is installed with a number of bolts 72 and nuts 76 as shown in Figure 8. To secure the flywheel 22 to the output flange 112 (Figure 1), each bolt 72 is passed through a bolt hole 70 defined through the flywheel 22 at a bolt radius "rB"
(Figure 6) from the axis of rotation "AR" of the flywheel 22. The planar stresses may be calculated as follows:
FB = (5) rB
Vs = ¨ (6) AB
FB
Vb = ¨ (7) hd where FB is a force (lbf) applied to the bolt 72, T is a torque (lb-ft) applied to the flywheel 22, AB is a bolt bearing stress area (in2) of the bolt 72, d is a diameter (ft) of the bolt hole 70, vs is a shear stress (psi) of each bolt 72, and Vb is a bearing stress on the flywheel 22/bolt hole 70 (psi).
Date Recue/Date Received 2020-09-11 being 1.54 inches and a diameter of each bolt hole being 1.06 inches, the bearing stress VB is 3,885 psi.
Examples of some suitable materials for the bolts 72 and the nuts 76 are Grade 8 carbon steel, Grade 5 carbon steel, or Grade G (8) steel; however, other suitable metals or other materials may also be used.
Examples of suitable torsional vibration dampers include, but are not limited to, a Geislinger Damper, a Geislinger Vdam p0, a Metaldyne Viscous Damper, a Kendrion Torsional Vibration Dampener, a Riverhawk Torsional Vibration Dampener, and the like.
Date Recue/Date Received 2020-09-11
of a single flywheel as detailed above with respect to the flywheel 22. In some embodiments, each of the first and second flywheel 22, 32 is sized to have a similar moment of inertia "r. In such embodiments, the first and second flywheel 22, 32 may have similar dimensions and mass or may have different dimensions and mass while having a similar moment of inertia "r. In other embodiments, the first flywheel 22 is configured to have a moment of inertia "F' different, e.g., greater than or lesser than, a moment of inertia "F' of the second flywheel 32.
The flywheel 22 is connected to the output flange 112 of the driving equipment 100 and the first torsional vibration damper 24 is connected to the flywheel 22. The second vibration damper 34 is connected to the input flange of the pump 300. Using first and second vibration dampers 24, 34 instead of a single vibration damper may allow for greater resistance to torsional resonance within the driving equipment 100 and/or for each of the first and second vibration dampers 24, 34 to have a reduced size compared to a single vibration damper.
As noted above, the first and second flywheels 22, 32 may be sized such that the sum of the "KE" of the flywheels 22, 32 is configured in a manner similar to the "KE"
of a single flywheel detailed above with respect to the flywheel 22. In addition, using first and second vibration dampers 24, 34 instead of a single vibration damper which may allow for greater resistance to torsional resonance within the driving equipment 100.
Date Recue/Date Received 2020-09-11
Claims (30)
a pump having an input shaft;
a driveshaft connected to the input shaft of the pump;
driving equipment including an output shaft having an output flange connected to the driveshaft and configured to rotate the driveshaft to rotate the input shaft of the pump therewith; and a vibration dampening assembly including:
one or more torsional vibration dampers operably connected to the input shaft and configured to reduce torsional resonance within the driving equipment or the pump;
one or more flywheels operably connected to the input shaft and configured to rotate therewith, the one or more flywheels also being configured to absorb a torque shock in the form of torque variance resulting from hydraulic fluid pulsation within the pump.
a pump having an input shaft;
a driveshaft connected to the input shaft of the pump;
driving equipment including an output shaft having an output flange connected to the driveshaft and configured to rotate the driveshaft to rotate the input shaft of the pump therewith; and a plurality of vibration dampening assemblies comprising:
a flywheel operably connected to the input shaft and configured to rotate therewith, and a torsional vibration damper operably connected to the input shaft, the plurality of vibration dampening assemblies being configured to reduce high frequency/low amplitude and low frequency/high amplitude torsional vibrations generated by operation of the pump.
the pump includes a single acting reciprocating pump; the flywheel includes a single mass flywheel; or the flywheel is connected to the output flange.
calculating a desired moment of inertia of the flywheel from kinetic energy "KE" of a torque variance within the pump system above a nominal torque of the pump system resulting from hydraulic fluid pulsation within the pump; and sizing the flywheel to have the desired moment of inertia from the calculated moment of inertia.
calculating a first desired moment of inertia of a first flywheel from a first portion of the kinetic energy "KE" of the torque variance within the pump system resulting from hydraulic fluid pulsation within the pump; and calculating a second desired moment of inertia of a second flywheel from a second portion of the kinetic energy "KE" of the torque variance within the pump system resulting from hydraulic fluid pulsation within the pump, wherein the first portion is greater than, lesser than, or equal to the second portion, wherein sizing the flywheel comprises sizing the first flywheel to have the first desired moment of inertia and sizing the second flywheel to have the second desired moment of inertia.
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201962899963P | 2019-09-13 | 2019-09-13 | |
US62/899,963 | 2019-09-13 | ||
US202062704560P | 2020-05-15 | 2020-05-15 | |
US62/704,560 | 2020-05-15 | ||
US16/948,291 | 2020-09-11 | ||
US16/948,291 US11015594B2 (en) | 2019-09-13 | 2020-09-11 | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
Publications (1)
Publication Number | Publication Date |
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CA3092958A1 true CA3092958A1 (en) | 2021-03-13 |
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ID=74865557
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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CA3092958A Pending CA3092958A1 (en) | 2019-09-13 | 2020-09-11 | Systems and method for use of single mass flywheel alongside torsional vibration damper assembly for single acting reciprocating pump |
Country Status (1)
Country | Link |
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CA (1) | CA3092958A1 (en) |
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2020
- 2020-09-11 CA CA3092958A patent/CA3092958A1/en active Pending
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