44 42 56.03 - vertical turbine pumps - engineers comments & spco responses approved

8/15/2019 44 42 56.03 - Vertical Turbine Pumps - Engineers Comments & SPCO Responses APPROVED

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476399_Submittal 14C Comments

SUBMITTAL REVIEW COMMENTS

DATE: 9/18/14 PROJECT: Thomas E. Taylor HSPS and StoneHill PS Improvements Project

SUBMITTAL

NO.:14C PROJECT NUMBER: 476399

SPECIFICATION

SECTION:44 42 56.03 PAGE: Page 1 of 1

SUBMITTAL TYPE: SHOP DRAWINGS SAMPLE

1. APPROVED 3. PARTIAL APPROVAL, RESUBMIT AS NOTED

2. APPROVED AS NOTED 4. REVISE AND RESUBMIT

5. INFORMATIONAL

Item: Taylor HSPS VTP Full Submittal

NO. COMMENT

RELATED

SPEC PARA./

DRAWING

REVIEWER’S

INITIALS

1. The supplemental attachment submitted (and attached to these comments)

addresses our comments. There are no further comments.TN


2/306

SMITH

PUMP

COMPANY, INC.

301 &B I

(800) 2998909 (254) 7760377

, 76712

FA (254) 7760023

TORSIONAL FREQUENCY ANALYSIS

PROJECT 169737-01

For

Dake ConstructionOn the

Upper Trinity Regional Water DistrictRTWS Thomas E. Taylor

Service Pump Station

VERTICAL TURBINEPUMP P-06-02-09

May 07, 2014

Revision A - June 18, 2014Revision B – Aug. 25, 2014Revision C – Sept. 5, 2014


3/306

1

H .

,

. .

F 1 & 1

. (J)

(K) .

1 6 1200

705 2.

1 FEE F27E2 AGE. I

155.68 2.

1:

.

I (2)

(/)

C

1 19090268 /

2 C/

3 /

4 /

5 /

6 /

7 /

8 /

9


4/306

2

1:

J=705 2

=19100000 /

=1050000 /

=540000 /

=1050000 /

J= 3.39 2

J=1.06 2

J=156 2

J=0.545 2

=1050000 /

J=0.545 2

J=0.545 2

J=0.545 2

J=0.545 2

=1050000 /

=1050000 /

=2880000 /


5/306

3

.

. H

.

I G .

416 11.2E+06 I.

= ∙ = ∙ = ℎ = = =

∙()∙

= 8.6 516 C

:

(C) :

2:

. F (C H)

1 516/8.6 I

2 8728/914 I

3 16750/1754 I

4 25898/2712 I

.

F 2

.


6/306

4

20% .

, .

1 .

.

. (CF) EC1698,

880

CF .


7/306

5

2:


8/306

6

&

E

= 10,800 = ∙ ∙ ∙ ∙ ∙ ∙ ′ = 0.797 = = 0.779 = = 0.577 = = 1.00 = = 0.67 = − = 0.75 = 99.9% ′ = 60,000 = − = 75,000 = ℎ ∙ 0.75

= 218 = = 10,876 =

= ∙ = ∙∙∙

− = +

= ∙ 1 −

416 .

2.688, .

G 100% 900 .

H, 100% 780 . E

F

. A

. A G 782 .

E 27E .

G .


9/306

7

F , 516

650 19% . D 50%

975 . 218

7% . E G 5.7 516

, .

.

. F 99.9% 0.75. B

, 0.67.

3.0.

. I ,

. H G 4.0 1.5 .

3.0 .

G

G . 32630 ;

218 2%. G 2.02

; G 6.0 .

. A F 3A.

3: &


10/306

8

E

= 6,426 = ∙ ∙ ∙ ∙ ∙ ∙ ′ = 0.886 = = 0.736 = = 0.577 = = 1.00 = = 0.67 = − = 0.75 = 99.9% ′ = 34,000 = − = 50,250 = ℎ ∙ 0.75 = 73 = = 3,628 =

= ∙ = ∙∙∙

− = +

= ∙ 1 −

3.875 ,

.

E F

. A

. G 4.0 782 .

3.0.

G

G . 10885 ;

218 2%. G 4.0 . . A F 3B.


11/306

9

3:


12/306

10

.

H

. I ,

.

.

F 4 . E

.

4:

F 5 8 . , .

.

.

8E+11

7E+11

6E+11

5E+11

4E+11

3E+11

2E+11

1E+11

0

1E+11

2E+11

0 500 1000 1500 2000 2500 3000

,

, /


13/306

11

5: 1

: 516 (53.97 /)

6: 2

: 8728 (914.01 /)

4

3.5

3

2.5

2

1.5

1

0.5

0

0.5

1

1.5

1 2 3 4 5 6 7

,

8.59

500

400

300

200

100

0

100

1 2 3 4 5 6 7

,

145.47


14/306

12

7: 3

: 16750 (1754.01 /)

8: 4

: 25898 (2712.01 /)

20% .

.

1500

1000

500

0

500

1000

1500

1 2 3 4 5 6 7

,

279.16

4000

3000

2000

1000

0

1000

2000

3000

4000

1 2 3 4 5 6 7

,

431.63


15/306

13

(1) , E.J., ,C (1958).

(2) , J.E., , C.., B, .G., , GH,

E (2004).


16/306

1

Jason Popko

From: Granger SmithSent: Thursday, September 18, 2014 5:38 PM

To: Jason Popko; Larry WingoCc: Neal McCaigSubject: FW: Smith Pump responses to engineer's comments for Thomas Taylor UTRWD Vertical Pump Submittal Rev. 2

Jason, Larry,

I spoke with Tony Naimey today, and reviewed Larry’s revised torsional analysis.

He was satisfied with the changes to Figure 2 (i.e. extend interference lines to ‘0’).

Once he understood that the torsional analysis included the motor in the Campbell diagram model, he dropped the

requirement for performing the torsional analysis on the motor shaft.

Bottom line

is

we

have

little

risk

if

we

release

the

fabrications

to

the

shop

now.

Things To Do

Send a formal submittal for approval responding to the engineer requests, and including the revised analysis.

Release the fabrications to the shop.

Regards,

Granger

L.

Granger

Smith,

P.E.

SMITH PUMP COMPANY, INC.

301 M&B Industrial | Woodway, TX 76712

o 254.776.0377 | c 254.744.3143 | f 254.776.0023

www.smithpump.com

From: Granger SmithSent: Thursday, September 18, 2014 12:15 PMTo: Tony Naimey ([email protected])Cc: Larry Wingo; Beatriz Dongell ([email protected])Subject: FW: Smith Pump responses to engineer's comments for Thomas Taylor UTRWD Vertical PumpSubmittal Rev. 2

Tony,

We are running out of project time on this project because I haven’t started making the column and head

fabrications. So, to expedite resolving and satisfying you requests I am reaching out to you. I am asking for an

informal forum whereby Smith Pump can finish responding the CH2MHill comments.

As such, please see the entire e‐mail thread below. Our modeler, Larry Wingo has complied with your require to

extend the interference lines in the Figure 2 diagram (see attached revised torsional analysis). To be clear, I

have also included that revised diagram below.


17/306

2

We think the above figure along with the added dialogue in the revised report satisfies your first need (restated

below from Brigit).

We are working on issuing a response to your submittal revision. Upon discussing the submittal

comments with our VTP technologist, we would like to see a supplemental Figure 2A as an additional

drawing that expands the Figure 2 Torsional Resonance Interference Diagram for an expanded

interference diagram of an operational speed range of 0‐1600 rpm. The figure currently shows only 800‐

1600 rpm. Please let me know if you have any questions about this request.

Our questions come from the second request which came from Brigit or Beatriz (I’m not sure) by phone to our

Jason

(restated

2

nd

hand

below)…

Larry, the engineer just called me and said he wants you to also do the same thing for the motor

shaft. He said we can submit this as supplemental data to the last resubmittal.

The figure that we think applies to this request is included in the attached revised torsional analysis, and also

below…


18/306

3

Can you describe exactly what you need for the motor shaft review?

Regards,

Granger

L.

Granger

Smith,

P.E.

SMITH PUMP COMPANY, INC.

301 M&B Industrial | Woodway, TX 76712

o 254.776.0377 | c 254.744.3143 | f 254.776.0023

www.smithpump.com


19/306

SMITH

PUMP

COMPANY, INC.

301 M&B Industrial(800) 299-8909 (254) 776-0377

Waco, Texas 76712FAX (254) 776-0023

SPCO responses to submittal review comments

Submittal No. 14BProject Number: 476399Specification: 44 42 56.03

1. Comment Response #10 (Flowserve will not have a vortex suppressor attachedduring any of the testing): Noted, since the suction vortex suppressor may not becompatible with the test tank. However, ensure pump suction hydraulics in the pumpmanufacturer's test bay meets the HIS requirements relative to suction hydraulics. Noresubmission required.

Comment confirmed. No action required.

2. Page 97: Reed Frequency Results: Pump Manufacturer shall perform an impact testto verify modal frequency locations upon installation of pump and motor at the projectsite. Pump manufacturer shall operate pump at steady state conditions at modal 5/6frequencies. The pump manufacturer shall measure and record vibration levels at thedischarge head. Once peak amplitudes have been established, the pump manufacturershall maintain steady state conditions for a period of not less than five minutes.Measured vibration limits shall validate that reed frequencies of the pump/motorstructure do not exceed the maximum specified values. If it is determined during fieldmeasurements that the pump/motor exceeds the maximum permissible vibration limits,the pump manufacturer shall be responsible for modifying the pumping unit structure as

necessary for compliance with the project specification requirements.

Smith Pump will do field testing at modes 5 and 6 and make any required modifications.

3. Page 102: The lateral critical speed calculation report is not legible. Please reviseand resubmit.

This might have been caused by something in the Adobe program. I have removed theoriginal and replaced it with a new file and I have also attached a separate copy of thefile for your review. Please contact me via e-mail at [email protected] if this fileis not coming through and we will make other arrangements to get a legible document.


20/306

4. Page 108 (Response Comment #16): Torsional Endurance: Analysis shall beconducted for both the pump and motor shaft, respectively. Modified Goodman analysisshall include the Goodman line, Factor of Safety = 2 (UTS/2 on the x-axis andEndurance limit/2 on the y-axis.

Pump shaft critical cross section and material match the line shaft. Goodman analysisfor pump shaft is included in line shaft analysis. Goodman line Factor of Safety = 2 isadded to the chart.

Separate fatigue analysis for motor shaft has been conducted and added after line shaftfatigue analysis.

5. Page 108 (Response Comment #17): Indicate pump performance conditionsassociated with the calculated value for the mean stress and calculated value for thealternating stress. The modified Goodman diagram shall then demonstrate thatalternating stress combined to mean stress is below the Modified Goodman Line, Factor

of Safety = 2 for both the pump and motor shafts, respectively.

Fatigue analysis is conducted at maximum pump horsepower which occurs at fullspeed. This information is added to the report.

Goodman design factor is 2.02 with stress concentration; Goodman design factor is 6.0without stress concentration.

6. Vibration Switch: The submitted part number 376A-A3-C4-E does not meet thespecification in regards to the alarm contact. The contact shall be 10A SPDTMechanical Relay Contacts which is met on the start delay only model but not on themonitor and start model which is required for this project. Revise and resubmit.

We will drop the Robert Shaw vibration switch in favor of the Metrix 440DR. Seeattached document for your review.


21/306

476399_Submittal 14B Comments_final



SUBMITTAL

NO.:14B PROJECT NUMBER: 476399

SPECIFICATION



1. APPROVED 3. PARTIAL APPROVAL, RESUBMIT AS NOTED

2. APPROVED AS NOTED 4. REVISE AND RESUBMIT

5. INFORMATIONAL


NO. COMMENT

RELATED

SPEC PARA./

DRAWING

REVIEWER’S

INITIALS

1. Comment Response #10 (Flowserve will not have a vortex suppressor

attached during any of the testing): Noted, since the suction vortex suppressor

may not be compatible with the test tank. However, ensure pump suction

hydraulics in the pump manufacturer's test bay meets the HIS requirements

relative to suction hydraulics. No resubmission required.

TN

2. Page 97: Reed Frequency Results: Pump Manufacturer shall perform an

impact test to verify modal frequency locations upon installation of pump and

motor at the project site. Pump manufacturer shall operate pump at steady-

state conditions at modal 5/6 frequencies. The pump manufacturer shall

measure and record vibration levels at the discharge head. Once peak

amplitudes have been established, the pump manufacturer shall maintain

steady state conditions for a period of not less than five minutes. Measured

vibration limitits shall validate that reed frequency of the pump/motor

structure do not exceed the maximum spedified values. If it is determined

during field measurements that the pump/motor exceed the maximum

permissible vibration limits, the pump manufacturer shall be responsible formodifying the pumping unit structure as necessary for compliance with the

project specifiation requirements.

TN

3. Page 102: The lateral critical speed calculation report is not legible. Please

revise and resubmit.TN

4. Page 108 (Response Comment #16): Torsional Endurance: Analysis shall be

conducted for both the pump and motor shaft, respectively. Modified

Goodman analysis shall include the Goodman line, Factor of Safety = 2

(UTS/2 on the x-axis and Endurance limit/2 on the y-axis.

TN


22/306

476399_Submittal 14B Comments_final

5.Page 108 (Response Comment #17): Indicate pump performance conditions

associated with the calculated value for the mean stress and calculated value

for the alternating stress. The modified Goodman diagram shall then

demonstrate that alternating stress combined to mean stress is below the

Modified Goodman Line, Factor of Safety = 2 for both the pump and motor

shafts, respectively.

TN

6.Vibration Switch: The submitted part number 376A-A3-C4-E does not meet

the specification in regards to the alarm contact. The contact shall be 10A

SPDT Mechanical Relay Contacts which is met on the start delay only model

but not on the monitor and start model which is required for this project.

Revise and resubmit.

2.04 TH

7.


23/306

\\FILESVR\Shares\Apps\2001PROJECTS\VERTICAL TURBINE\[FLSVTP-UTRWD Thomas Taylor - 27EN #####

Shaft Critical Speed Calculations

The following is the equation used for calculating shaft critical speeds

( Fn above for Hinged/Hinged spans (H/H))

Fn = 1.40 x (H/H) ( for Fixed/Hinged spans (F/H)) Fn = 1.9 x (H/H) ( for Fixed/Fixed spans (F/F))

where:

I = moment of inertia of cross-section (0.05xD4) (in4)

E = modulus of Elasticity of material (lbs/in2) 25% This is the fire pump

g = acceleration due to gravity 386 inches/sec2 20% Input special specifie

L = Length of shaft between two consecutive bearings (in) = column length + length to bearing 20% Input special specifie

n = order of natural frequency or critical speed (1st or 2nd)

T = Axial thrust or force (lbs)

Fn = Natural frequency ( cycles/unit time ) also critical speed ( rev/unit time )

Fnn

L

g

w

E I n

L

T

30

2


24/306

Pump operating speed 1193

Modulus of Elasticity 29000000

Pump thrust 17038

Shaft Dia (D) 2 17/25

weight of shaft in lb/in 1.5795

Specified % OVER, from operating speed requirement 20% --use 20% if nothing is specified in specifications

Specified % UNDER, from operating speed requiremen 20% --use 20% if nothing is specified in specifications

Type Column Order of fn

20% over operating speed = 1432 rpm of Length Critical (RPM)

20% under operating speed = 954 rpm Span (in) Speed

Head flange to SB bearing F/H 34.25 1 15412

(hard bearing to rubber bearing) 2 61037

Max. Column Length (Input B64) H/H 54.75 1 4396

(rubber bearing to rubber bearing) 2 17150

Input 0 if Bearing Span type is not used.N/A = bearing span type not used in this pumping unitLengths for above table are nominal column lengths as used on the installation plan for submittalFor Fire Pumps, the specified % from operating speed requirements must be 25% above or below operatingspeed.

Potential critical speed problem - indicates that the critcal speed for the selected bearing span is

within specified critical speed range.


25/306

SMITH

PUMP

COMPANY, INC. 301 M&B Industrial

(800) 299‐8909 (254) 776‐0377

Waco, Texas 76712

FAX (254) 776‐0023

TORSIONAL FREQUENCY ANALYSIS

PROJECT 169737-01

For

Dake ConstructionOn the

Upper Trinity Regional Water DistrictRTWS Thomas E. Taylor

Service Pump Station

VERTICAL TURBINEPUMP P-06-02-09

May 07, 2014

Revision A - June 18, 2014Revision B – Aug. 25, 2014


26/306

Page | 1

TORSIONAL

FREQUENCY

ANALYSIS

METHOD

OF

CALCULATION

The torsional natural frequencies and the mode shapes of this rotating train were calculated

using a computer program based on the Holzer Tabulation method.

The system is modeled using mass moments of inertia for the impeller, the line shaft and

the motor. The motor is modeled with one mass moment of inertia.

INPUT

DATA

The mass‐elastic data in Figures 1 & Table 1 represents the rotor system arrangement

for the calculation. The polar mass moments of inertia (J‐values) and the torsional spring

constant (K‐values) are the used for the torsional natural frequency calculations.

The motor referenced in Table 1 is a 6 pole 1200 RPM motor operated at a variable

speed with rotor inertia of 705 lb‐ft2.

The pump

referenced

in

Table

1 is

a FLOWSERVE

FS

‐36ENM

‐‐2 STAGE.

It

has

five

vanes

and

total pump inertia of 155.68 lb‐ft2.

Table 1: Torsional Analysis Input Data

Span No. Polar Moment of

Inertia (lb‐ft2)

Torsional Stiffness

(in‐lb/rad)

Component

1 705 19090268 Motor/Motor Shaft

2 3.386117 539874 Motor Coupling/Top Shaft

3 1.061864 1051448 Top Shaft/Line Shaft

4 0.545222 1051448 Line Shaft/Line Shaft

5

0.545222

1051448 Line Shaft/Line

Shaft



8 0.545222 2878340 Line Shaft/Pump Shaft

9 155.68 Pump


27/306

Page | 2

Figure 1: Campbell Diagram

J=705 lb‐ft2

k=19100000 in‐lb/rad




J= 3.39 lb‐ft2

J=1.06 lb‐ft2

J=156 lb‐ft2

J=0.545 lb‐ft2


J=0.545 lb‐ft2

J=0.545 lb‐ft2

J=0.545 lb‐ft2

J=0.545 lb‐ft2



k=2880000 in

‐lb/rad


28/306

Page | 3

TORSIONAL

EXCITATION

FREQUENCY

The first

frequency

can

be

approximated

using

the

equation

below.

This

equation

simplifies the entire system down to two masses at the ends of a shaft that is acting as

spring. This number should be similar to the first frequency found using the Holzer

Tabulation method and acts as a check for the system.

In the following equation G is the modulus of rigidity and R is radius of the shaft. The

modulus of rigidity used for the 416SS shafting is 11.2E+06 PSI.

∙ ∙

∙∙

8.6 or 516 CPM TORSIONAL

ANALYSIS

RESULTS

Natural

frequencies

and

mode

shapes:

The calculated torsional natural frequencies (CPM) for this rotor train are listed below:

Table 2: Results

Mode No. Natural Frequency (CPM and Hz) Separation Margin

1 516/8.6 No Interference

2 8728/914 No Interference



The calculated separation margin was established by using the shaft excitation that has the

smallest separation margin with respect to a given natural frequency.

The interference diagram in Figure 2 shows the first three calculated natural frequencies and

potential excitation modes. The system is considered satisfactory if the torsional natural


29/306

Page | 4

frequencies are 20% away from potential excitation modes. There are no interference points

within the specified margin, but a fatigue analysis will still be performed.

Figure 2: Torsional Resonance Interference Diagram


30/306

Page | 5

TORSIONAL

ENDURANCE

EQUATIONS

–

LINESHAFTS

&

PUMP

SHAFT

Shear Endurance Strength

10,800 ∙ ∙ ∙ ∙ ∙ ∙ ′ 0.797 0.779 0.577 1.00 0.67 0.75 99.9% ′ 60,000 75,000 ∙ 0.75

218 10,876 ∙ ∙∙∙

∙ 1

Lineshafts and pump shaft are both 416 stainless steel. Top of the pump shaft is reduced to

lineshaft diameter, hence the same fatigue analysis applies to both.

Original Goodman

fatigue

calculations

conservatively

used

100%

of

the

motor’s

900

hp.

However, at 100% rpm and design head the pump only consumes 780 hp. Examination of

Flowserve’s bowl power curve shows that design head and flow are identical to maximum

horsepower consumed by the pump. A small amount of additional power is consumed by shaft

friction losses. Adjusting the Goodman equations for 782 hp increases design factor.

Miscellaneous factor previously covered reliability and other factors. Reliability is now broken

out as its own factor. For 99.9% reliability the factor is 0.75. Because reliability is now broken

out as its own factor, the miscellaneous factor changes to 0.67.

Stress concentration

factor

as

used

in

calculations

is

3.0.

This

accounts

for

the

stress

increase

found at keyways cut into shafts. In this case however, lineshafts are threaded and do not have

keyways. Hence Goodman design factor for lineshafts is 4.0 using stress concentration factor of

1.5 for threads. The top shaft does have a keyway at the three piece motor coupling and

requires the 3.0 stress concentration factor.


31/306

Page | 6

The stress analysis and fatigue evaluations were performed using a modified Goodman

equation and Gerber equation. Shaft stress is 32630 psi with stress concentration; alternating

stress is 218 psi using an amplitude ratio of 2%. Goodman design factor is 2.02 after stress

concentration;

Goodman

design

factor

is

6.0

without

stress

concentration.

These

values

are

acceptable. A chart of this data is shown in Figure 3A.

Figure 3A: Fatigue Life Chart – Lineshafts & Pump Shaft

TORSIONAL ENDURANCE EQUATIONS – MOTOR SHAFT

Shear Endurance Strength

6,426 ∙ ∙ ∙ ∙ ∙ ∙ ′

0.886 0.736

0.577

1.00 0.67 0.75 99.9% ′ 34,000 50,250 ∙ 0.75

73 3,628


32/306

Page | 7

∙ ∙∙

∙

∙ 1

Minimum motor shaft diameter is 3.875” at the coupling, that diameter is used in fatigue

calculations.

Examination of Flowserve’s bowl power curve shows that design head and flow are identical to

maximum horsepower consumed by the pump. A small amount of additional power is

consumed by shaft friction losses. Goodman design factor is 4.0 at 782 hp.

Stress concentration factor as used in calculations is 3.0.

The stress analysis and fatigue evaluations were performed using a modified Goodman

equation and Gerber equation. Motor shaft stress is 10885 psi with stress concentration;

alternating stress is 218 psi using an amplitude ratio of 2%. Goodman design factor is 4.0 after

stress concentration. These values are acceptable. A chart of this data is shown in Figure 3B.

Figure 3B: Fatigue Life Chart – Motor Shaft


33/306

Page | 8

ANGULAR

VELOCITY

vs.

TORQUE

The Holzer

method

for

finding

the

natural

frequencies

of

a rotating

assembly

requires

setting

up spring equations and making iterative changes to an assumed angular input velocity to find

values where residual motion at the other end of the assembly is zero. In other words, there is

no torque available to rotate anything that may be attached to the end of the last shaft. When

residual torque is zero the assembly is vibrating in resonance with the input frequency.

Figure 4 is a graph of these iterations. Each location where the plotted line crosses zero is a

natural frequency of the system.


34/306

Page | 9

Figure

4:

Angular

Velocity

vs

Torque

Figures 5 through 8 represent twisting of the shaft along its length at one natural frequency.

These plots show relative angular displacement, not lateral motion. The point where rotary

vibration is minimum is located where the angular displacement line crosses zero. Maximum

stress occurs where line slope is maximum.

‐8E+11

‐7E+11

‐6E+11

‐5E+11

‐4E+11

‐3E+11

‐2E+11

‐1E+11

0

1E+11

2E+11

0 500 1000 1500 2000 2500 3000

R e s i d u a l T o r q u e ,

U n i t l e s s

Angular Velocity, Radians/Sec


35/306

Page | 10

Figure

5:

1st

Mode

Shape:

516

CPM

(53.97

rad/sec)

Figure 6: 2nd

Mode Shape: 8728 CPM (914.01 rad/sec)

‐4

‐3.5

‐3

‐2.5

‐2

‐1.5

‐1

‐0.5

0

0.5

1

1.5

1 2 3 4 5 6 7

R e l a t i v e A n g u l a r D i s p l a c e m e n t

Shaft Sections, Motor to Bowl

8.59

Hz

‐500

‐400

‐300

‐200

‐100

0

100

1 2 3 4 5 6 7

R e l a t i v e A

n g u l a r D i s p l a c e m e n t


145.47

Hz


36/306

Page | 11

Figure

7:

3rd

Mode

Shape:

16750

CPM (1754.01 rad/sec)

Figure

8:

4rd

Mode

Shape:

25898

CPM (2712.01 rad/sec)

CONCULSION

There are no torsional excitation modes within 20% of this unit’s run speed. Shafting was

subjected to fatigue analysis and passed.

‐1500

‐1000

‐500

0

500

1000

1500

1 2 3 4 5 6 7

R e l a t i v e A n g u l a r D i s p l a c e m e n t


279.16

Hz

‐4000

‐3000

‐2000

‐1000

0

1000

2000

3000

4000

1 2 3 4 5 6 7

R e l a t i v e A n g u l a r D i s p l a c e m e

n t

Shaft

Sections,

Motor

to

Bowl

431.63

Hz


37/306

Page | 12

References

(1) Nestorides, E.J., A Handbook on Torsional Vibration,Cambridge Press (1958).

(2) Shigley, J.E., Mischke, C.R., Budynas, R.G., Mechanical Engineering Design, McGraw‐Hill,

Seventh Edition

(2004).


38/306

Da

440 /

Document 1

Rev. E (Dec 2

Overvi

Metrix 44

provide ec

vibration

use in non

hazardous

internal el

explosion‐

Div 1 haza

Options ar

electrome

to be used

machine u

provide a

discrete o

independ

discrete o

(pre‐shutd

separate 4

provided

to PLCs, D

control sy

trended.

Vibration

velocity u

an interna

housing, p

functionali

use an ext

* NOTE:

Haz

external sen

or SM6100 i

with a variet

7295 and ex

ash50 Elect

04730

013)

ew

and 450 elec

onomical, self

rotection. Th

‐hazardous as

areas. The 45

ctronics as th

proof enclosu

rdous areas.

e available for

chanical relay

in an auto‐sh

nder high vibr

ingle alarm se

tput. DR vers

nt alarm setp

tputs, allowin

own) and DA

‐20 mA propo

n all switch m

Ss, strip chart

tems where v

n both switch

its. The stand

l acceleromet

roviding comp

ty. The switc

ernal accelero

ardous area

appr

or is used with th

stead, which are

of external sens

losion‐proof wiri

et ronic Vib

ronic vibratio

‐contained, si

e 440 switch is

well as Class I

0 switch utiliz

e 440, but fea

e styles suitab

electronic (tri

outputs, allow

tdown circuit

ation conditio

tpoint and cor

ions provide t

ints and corr

g implementa

GER (shutdo

rtional output

odels, allowin

recorders, or

ibration levels

es is monitore

ard configurat

r mounted in

letely self ‐con

may also be

meter if desire

vals are

not

avail

e model 440. Con

approved for use i

r types when Me

g practices are u

ration S

switches

gle‐channel

suitable for

Div 2

s the same

ures

le for Class I

ac or FET) or

ing the switch

that trips the

s. SR version

responding

o

sponding

ion of ALERT

n) levels. A

is also

connection

other process

can be

d in RMS

ion consists o

ide the switch

tained

onfigured to

d.*

ble when

an

sider models 450

n hazardous area

rix sensor housin

ed.

itches

s

s

g

Ap

Vibr

of t

440 Switch

The 440 switc

approved for

Div 2 hazardo

enclosure car

rating and us

mounting pat

450 Switch

The 450 switc

internal elect

but uses an e

enclosure tha

approved use

areas. The sta

(4‐hole moun

only available

cover. The al

(2‐hole moun

only available

cover. Both e

carry NEMA 4

plicatio

ation switches

e following cr

Only one or t

required on

a

A fully self ‐co

required (sen

alarming, and

Sufficient roo

switch on the

and in the cor

vibration leve

h is CSA

use in

Class

I

us areas. Its

ries a NEMA 4

s a 3‐hole

tern.

h has the sam

onics as the 4

plosion‐proof

t permits CSA‐

in Class I Div1

ndard enclosu

ting pattern) i

with a solid

ernate enclos

ting pattern) i

with a windo

closure styles

X ratings.

s

are an attract

iteria apply:

o measurem

machine.

ntained appro

sing element,

outputs).

m exists to mo

machine in th

rect orientati

ls indicative of

e

0,

re

ure

ive solution w

nt points are

ach is desired

ignal conditio

unt a vibratio

e correct locat

n such that th

machinery

450

EXPL

ENCLOSU

450 (ALTERNA

PROOF EN

WINDO

440 (NEMA 4X

hen all

or

ning,

ion

e

(STANDARD

SION PROOF

E, SOLID COVE

TE EXPLOSION

CLOSURE,

COVER)

ENCLOSURE)

R)

81


39/306

Document 1

Rev. E (Dec 2

malfu

switc

The fe

syste

financ

A 4‐2

impra

or oth

monit

In situatio

cannot be

may be m

transmitte

external s

monitorin

Seismic

M440/450 e

for genera

on a wide

machinery

and 6,000

particularl

rolling‐ele

such mach

the bearin

substantia

transducedoes not o

related w

problems,

machine,

of seismic

protecting

the shaft v

to the me

given to th

before rel

measurem

Why Mea

When a d

vibration

velocity is

Accelerati

influenced

04730

013)

nctions will ac

mounting loc

atures of a m

are not nece

ially justified.

mA vibration

ctical because

er instrument

oring the tran

s where one

met, Metrix o

re appropriat

rs, single‐cha

nsor, and mul

systems.

easurements

lectronic vibra

l‐purpose seis

range of rotati

with rotative

rpm. Seismic

well‐suited f

ent bearings

ines is usually

g to the beari

l damping or a

s

are

also

ablriginate at the

ar and defect

piping resona

tc. Metrix do

measurement

machinery wi

ibration many

surement loc

e efficacy of s

ing substanti

ents.

ure Velocity?

cision has be

n the machin

often the best

n and displac

by the freque

Da

ually be meas

ation.

lti‐channel m

ssary and can

transmitter is

a PLC,

DCS,

S

ation is not av

mitter signal.

r more of the

fers other sol

e, such as vibr

nel monitors t

ti‐channel API

tion switches

ic vibration

ng and recipr

speeds betwe

measurement

or machines t

because shaft

transmitted d

g housing, wit

ttenuation. Se

to

measure

v shaft, such as

, footing/ fou

ces that are c

es not recom

s as the sole

h fluid‐film b

not be faithfu

tion. Though

uch a monitori

lly or solely u

n made to mo

casing or sup

parameter to

ement levels a

ncy(ies) at wh

tasheet – 440 & 4

urable at the

nitoring

ot be

ndesirable or

ADA system,

ilable for

se criteria

tions that

ation

hat accept an

670‐complian

re intended

easurements

cating

n 120 rpm

are

at incorporat

vibration in

irectly throug

hout

ismic

ibration

that

bearing‐

dation

oupled to the

end the use

eans of

arings where

lly transmitte

should be

ng strategy

on seismic

nitor seismic

port structure

use.

re heavily

ich the

50 Electronic Vibr

,

vibr

less

and

mat

to b

freq

Con“ov

app

relia

the

bea

shaf

Casi

to

seis

deciusu

casi

will

a m

ene

med

tran

the

bou

prox

mon

For

spee

vibr

mea

recosales

assis

asso

ation Switches

tion is occurr

influenced. T

displacement

hematically, s

e more consis

uencies than

sequently, bro

rall” or “unfilt

opriate for m

ble indicator

notable excep

ings, which ar

t‐observing pr

ng displaceme

ake directly,

ic velocity m

sion when

sel

lly be whethe

g acceleratio

often be more

re reliable in

gy over a bro

ium‐speed m

NOTE:

For machine

observing p

effective vib

ducers due to t

ttenuation of vi

dary. Accordin

imity probes an

itoring systems

achines with r

ds above 6,000

tion occurs, ac

surement than

mmended that

professional w

t with selection

ciated transmitt

ing, while velo

us, although a

measurement

ismic velocity

ent over a wi

ither displace

adband (som

ered”) velocit

onitoring man

f damaging vi

tion of machin

e usually bett

oximity probe

nt is not a pra

nd is typically

easurement.

cting a seismi

r to measure

. As noted a

appropriate

icator of dam

d frequency s

chinery.

s with fluid‐film

oximity probes

ration measure

he rotor dynam

ibratory energy

gly, Metrix reco

d associated 4‐

for such applica

lling element b

rpm, and/or wh

eleration may b

elocity. In such

ou consult

wit

ho can review y

of the proper t

er or monitorin

Pag

city levels are

cceleration, v

s are all inter‐

measuremen

e range of

ment or accel

times called

measureme

machines as

bratory energ

es that use flu

r addressed b

s.

ctical measur

just an integr

s such, the p

c measureme

asing velocity

ove, casing v

ecause it ten

aging vibrator

pectrum for l

bearings, shaft

will provide

mo

ments than seis

ics of the machi

through a fluid‐

mmends and pr

0 mA transmitt

tions.

earings and run

ere impulsive c

e a better

situations, it is

your nearest

our application

ansducer type

g system.

2 of 16

much

locity,

related

s tend

ration.

ts are

a

, with

id‐film

y

ment

ted

imary

t will

or

locity

s to be

w‐ to

‐

re

mic

ne and

film

ovides

ers or

ning

asing

etrix and

nd

82


40/306

Document 1

Rev. E (Dec 2

Featur

One o

The u

one f

applic

annu

and/o

appro

machi

with o

pre‐s

outpu

devic

limits

*The 4

over/u

LOCK

An op

suppr

startu

elevat

condit

specif

switc

allowi

rough

speed

or trip

or del

speed

affect

allowi

and tr

* NOTE

cannot

availabl

Accep

When

the s

rathe

exter

applic

04730

013)

es and B

r two indepe

e of two setp

r SHUTDOWN

ations where i

ciate an ALER

r maintenanc

priate interve

ne reaches SH

nly a single se

utdown warn

t is connected

, and appropr

are program

0/450 switch pro

der) alarms.

UT (Power‐U

ional LOCKO

ssing alarm a

p conditions

ed compared

ions. When t

ied, applying (

suppresses al

ng the machin

running zone

/load without

s, and withou

ays that are su

of the machi

ed while the s

ng actual vibr

ended at all ti

: This delay is set

be adjusted in th

e upon

request

a

ts Internal or

ordered with

itch accepts a

than using an

al sensor opti

ations as it all

Da

enefits

dently adjust

ints* (one for

) is recommen

t is desirable t

condition to

personnel. T

tion to occur

UTDOWN leve

tpoint are not

ings unless the

to a PLC or ot

iate pre‐shutd

ed in the PLC.

ides only over‐ty

p Alarm Inhibi

T capability is

ctivation durin

hen vibration

o normal run

e LOCKOUT o

or cycling) po

arms for 20 s

e to accelerat

and reach

ope

generating sp

the need to a

itable for nor

e. The 4‐20m

itch is in LOC

tion levels to

es.

at the factory for

field. Other dela

Engineering

Spe

External Sens

the external s

n external acc

internal accel

on is recomm

ws the senso

tasheet – 440 & 4

ble setpoints

ALERT and

ded for

o remotely

operators

his allows

before the

ls. Switches

capable of

4‐20mA

er trending

own alarm

pe (not

t) capabilities

available for

g machine

levels may be

ing

ption is

er to the

conds*,

through its

rating

rious alarms

lter setpoints

al running

output is no

KOUT mode,

be displayed

0 seconds and

y times may be

ials.

r

nsor option,

elerometer

erometer. Th

nded for mos

to be

50 Electronic Vibr

ation Switches

mounted at t

orientation o

the larger mo

switch compa

vibration swit

convenient lo

Also, althoug

survive harsh

and corrosion

elevated tem

location. Use

temperatures

sensor locatio

vibration swit

When an exte

internal accel

completely se

the switch to

measurement

integrated ac

configuration

room at the

switch, when

allows the sw

serviced by pl

switch’s inerti

quality of the

RMS amplitu

True RMS det

amplitude of

choice for ma

overall vibrati

waveform wit

short‐duratio

the wavefor

trips on some

Easy to wire

VDE‐approve

accept #12 A

Terminals use

adjustable cla

provide secur

proof connec

e ideal meas

the machine,

unting footpri

red to a senso

ch to be moun

cation for vie

the

440/450

environments

, some machi

eratures at th

of an external

as high as 121

n and 88° C (1

ch location.

rnal sensor is

erometer can

lf ‐contained

o

be mounted d

location and

eleration (vel

is suitable wh

easurement l

the measure

itch to be con

ant personnel,

al mass will n

vibration mea

e detection

ection is used

he vibration s

ny machines a

on energy con

hout being ov

“spikes” that

and can lead

machines.

terminal stri

G wire.

screw‐

mping yoke to

e, vibration‐

ions.

Pag

rement locati

without conc

t of the vibra

r. It also allo

ted in a more

ing and servi

is packaged

to

of dust, moist

es may exhibi

e preferred s

sensor can all

° C (250° F) at

90° F) at the

not practical,

e specified fo

peration. This

irectly at the

onitor vibrat

city) units. T

en there is suf

ocation to mo

ent location s

eniently view

and when th

t compromis

surement.

to measure th

ignal. RMS is

s it is sensitive

tained in the

erly sensitive t

may be conta

to spurious al

s

3 of 16

on and

ern for

ion

s the

ing.

ure,

t

nsor

ow

the

n

r

allows

ion in

is

ficient

unt the

till

ed and

the

e

good

to the

o

ined in

rms or

83


41/306

Document 1

Rev. E (Dec 2

Simpl

o

o

o

o

o

Flexib

Discre

annu

switc

04730

013)

, intuitive op

Setpoint a

color‐code

between S

ALARM (yel

scale is

gra

percent) to

scale range

LEDs adjac

light imme

above its s

Independe

screws are

each setpo

3 seconds;

2‐15 secon

spurious vi

in false ala

persist abo

time delay

TEST positi

allowable s

activate LE

persist

lonALARM an

activate als

to be teste

le Discrete Ou

te outputs ar

ciate alarm co

as part of an

Da

eration

justment kno

to easily disti

UTDOWN (re

llow) settings.

uated in

in/s

quickly conve

.

nt to each adj

iately when a

tpoint1.

nt time delay

provided imm

nt knob. Pres

adjustable in t

s. Time delay

ration signals

ms – measure

e setpoint fo

o activate ala

on forces mini

etpoint; any vi

immediately

er

than

time

SHUTDOWN

o, allowing dis

.

tput Types

used to exter

nditions and t

auto‐shutdow

tasheet – 440 & 4

bs are

nguish

d) and

Adjustment

c (rather

than

switch full

ustment knob

reading is

djustment

ediately belo

et at factory t

he field from

s ensure that

do not result

ment must

duration of

rm circuitry.

mum

bration will

; if allowed to

elay,

the

utputs will

crete outputs

nally

o use the

n (i.e., trip)

50 Electronic Vibr

ation Switches

circuit. Switc

discrete outp

provide two d

and one for S

individually fi

time delays a

alarm or

clos

available disc

specified at ti

o Mechani

Mechani

most app

holding c

state, ha

used to s

Relays ar

o Triacs

Triacs ar

heavy AC

where m

very high

recomm

and are s

output w

PLC or D

o Solid‐Sta

Solid‐stat

applicati

will be

co

PLC or D

require n

smaller l

off state.

not used,

plated co

with mec

avoided.

Analog 4‐20

All switches c

proportional t

4mA= 0% of f

20mA = 100%

easy connecti

other instrum

display of vib

feature allow

es with one s

t. Switches

iscrete output

UTDOWN. T

ld‐configured

d separate sh

on

alarm).

A

ete output fo

me of orderin

al Relays

al relays are a

lications as th

urrent to rem

e no leakage

itch a large v

e SPDT and rat

specifically

in

loads such as

mentary inru

during startu

nded for most

pecifically disc

ill connect to l

S.

e (FET) Relay

e relays are d

ns where the

nnected to

a l

S. Unlike tria

o holding curr

akage current

Because mec

arcing, oxidat

ntacts, and ot

hanical relays

A output stan

me with an a

o vibration ve

ll scale (no vi

of full scale.

on to PLCs, SC

entation for tr

ation values.

users to easil

Pag

etpoint provid

ith two setpoi

s – one for AL

e outputs ca

to have separ

elf states (ope

y one

of

thre

mats can be

:

good choice f

y do not requ

in in a particu

urrent, and c

ariety of loads

ed for 10A.

tended for

sw

electric motor

sh current can

. They are no

other applica

ouraged whe

ight loads suc

signed prima

discrete outp

ight load,

such

s, solid‐state

nt and have

s (10 µA) whe

anical contact

ion, use of gol

er issues ass

and light load

dard

nalog 4‐20mA

locity where

ration) and

his output fa

DA systems,

ending and re

The “live zero

y distinguish

4 of 16

e one

nts

RM

be

ate

n on

e

or

ire any

lar

n be

.

itching

s

be

t

tions,

the

as a

ily for

t(s)

as a

elays

uch

n in the

s are

d‐

ciated

are

output

ilitates

and

mote

84


42/306

Document 1004730 Datasheet – 440 & 450 Electronic Vibration Switches Page 5 of 16

Rev. E (Dec 2013)

between no vibration (4mA) and no power or

loop discontinuity (0mA). The output also

provides its own power, eliminating the need for

external 24Vdc loop supplies and allowing use of

“sinking” type I/O modules at the PLC, DCS, strip

chart recorder, or other instrumentation.

Remote Reset

Terminals are provided for remote reset,

allowing operators to reset the switch and

acknowledge alarms without leaving their

station.

No moving parts, high accuracy/repeatability

Unlike mechanical vibration switches, electronic

switches have no moving parts and do not rely

on internal mechanical tolerances for

establishing setpoints or measuring vibration.

Setpoints can be established with far better

accuracy and repeatability, and much smaller

changes in vibration can be detected.

Velocity Monitoring

Unlike mechanical switches which are inherently

acceleration sensing devices and require large

changes in g‐forces to trip, Metrix electronic

vibration switches sense vibration velocity – a

more suitable measurement for most machines,

better able to detect both gross and subtle

changes in machinery condition. Velocity is

monitored over a wide frequency band from 2Hz

to 1000Hz.

Specifications

All specifications are at +25C (+77° F) unless

otherwise noted.

Freq. Range 2 – 1000 Hz (120 – 60000 rpm)

Amplitude

Range

See ordering option C (full scale

range)

Amplitude

Detector Type

RMS

Alarm Time

Delay

Field adjustable from 2‐15 seconds

(factory default setting = 3 sec)

Analog Output Type

4‐20mA (4mA=0% full scale,

20mA=100% full scale)

Accuracy

±10%

Max Allowable Load Resistance

450 ohms

Setpoints Adjustment Location

Internally Accessible

Accuracy

±10% of setting

Repeatability

±2% of setting

Range / Engineering Units

1.5 in/s models: 0.1 to 1.5 in/s

3.0 in/s models: 0.2 to 3.0 in/s

40 mm/s models: 3 to 40 mm/s

80 mm/s models: 6 to 80 mm/s

Number

DR models: 2 (alarm & shutdown)

SR models: one (shutdown only)

Power‐up

Timed Inhibit

(i.e., Lockout)

Optional (see ordering option H);

factory set at 20 seconds (non‐

adjustable); invoked at initial

power up or by interrupting power

to the switch Auto Reset Configurable; switch can be

configured with latching alarms

requiring manual reset or non‐

latching alarms that automatically

reset when vibration falls back

below setpoint(s)

Remote Reset Available via wiring terminals;

short terminals to

reset/acknowledge alarms.

Local Reset Model 440: Optional via local

pushbutton on switch housing (see ordering option F); remote reset

not available when local reset

specified. Local reset not

compatible with hazardous area

approvals.

Model 450: Local reset pushbutton

not available.

85


43/306


Rev. E (Dec 2013)

Contact

Ratings

Triacs

Continuous

Current

5A

Surge &

Overload (Duty

cycle


44/306


Rev. E (Dec 2013)

Elevation Limit 2,000 m (6562 ft) above sea level

Max. operating temperature must

be de‐rated 2% for every 305m

above 2000m

NOTE: Atmospheric pressure at elevations

≥ 2000m reduces heat dissipation and must

be

accounted

for

when

determining

max.

operating temperature.

Mounting Model 440:

3‐hole triangular pattern via

mounting bosses; uses ¼”

hardware; see Figure 1

Model 450 w/ solid cover (F≠9):

4‐hole square pattern; uses ¼”

hardware; see Figure 2.

Model 450 w/ lens cover (F=9):

4‐hole square pattern; uses ¼”

hardware; see Figure 2.

Agency

Certifications

Model 440:

CSA

Cl I Div 2 Grps B‐D

Model 450:

CSA

Class I Div 1 Grps B,C,D

Class II Div 1 Grps E,F,G

Class III

Weight Model 440: 1.6 kg (3.5 lbs)

Model 450: 2.7 kg (6.0 lbs)

87


45/306

Document 1

Rev. E (Dec 2

Orderi

440‐A‐BC

440 Electr

A

S

D

B

2

C

0 1

2

3

D

0

2

4

E

0

1

2

4

04730

013)

ng Infor

E‐FGHI1

nic Vibration S

Number o

One alarm

R Two alarm

Analog Pr

4‐20 mA(a

Scale Rang

0.1

–

1.5

in 0.2 – 3.0 in

3 – 40 mm

6 – 80 mm

Shutdown

Triac (5A,

Solid‐state

Electrome

Alarm Circ

None

Triac (5A,

Solid‐state

Electrome

Da

ation

witch

Alarm Setpoin

setpoint

setpoints

portional Outp

bsolute)4

e4

/sec

(RMS)

/sec (RMS)

/sec (RMS)

/sec (RMS)

Circuit Output5

PST)6

switch (170 mA

hanical relay (1

uit Output2,5

PST)6

switch (170 mA

hanical relay

(1

tasheet – 440 & 4

s2,3

ut

,6

, 250 Vpk)7

0A, SPDT)

, 250 Vpk)7

0A, SPDT)

50 Electronic Vibr

SEE

F

G

H

I

ation Switches

OTES ON FOLLO

Appro

0

CSA A

No

ext

No BN

2

No Ap

Extern

No BN

7

No Ap

No ext

Extern

8

No Ap

Extern

Extern

Input

0 115 Va

1

230 Va

2 24 Vdc

Power

0 None

2 20‐sec

Transd

0 Intern

5 Extern

ING PAGE

vals / External

provals (Class I,

ernal reset

push

C connector

rovals

al reset pushbut

C connector

rovals

ernal reset push

al BNC with 100

rovals

al reset pushbut

al BNC with 100

Power

c, 50/60 Hz

c, 50/60

Hz

‐up Timed Inhi

delay12

ucer Option

l Acceleromete

al Acceleromete

Pag

eset / BNC co

Div 2, Gps B‐D)

button

ton9

button

mV/g accel sig

ton9

mV/g accel sig

it (i.e., LOCKO

r

r13

8 of 16

nector8

al10

al10

T)11

88


46/306


Rev. E (Dec 2013)

MODEL 440 ORDERING INFORMATION NOTES:

1. Various other configurable options were available on

older Metrix or PMC/BETA 440 switches and may use

other digits and/or longer part numbers than those

shown here. Consult the factory when ordering spares

for (or replacing) such switches.

2. When a single alarm setpoint is ordered (A = SR), only a

shutdown circuit is provided and option E must be 0.

3. Some older switches may simply be labeled “S” instead

of “SR” and “D” instead of “DR”.

4. The analog proportional output (option B) is related to

scale range (option C) and will be 4mA when vibration

levels are at or below the bottom scale range. 4 mA =

bottom scale range and 20 mA = top scale range.

5.

For dual setpoint switches, the type of output for

shutdown and alarm circuits must be the same. For

example, a 440‐DR switch with a Triac shutdown circuit

(D=0) must also use a Triac alarm circuit (E=1).

6. Triac output types are recommended when switching

medium power rated AC devices such as motor starters,

contactors,

and

relays.

However,

triacs

require

a

50mA

holding current and exhibit a leakage current of 1mA.

7. Solid‐state switch output types are recommended for

connection to light loads such as discrete inputs on

PLCs or DCSs. This output type is easier to interface as

it has virtually no leakage current (10 µA or less), and

does not require any holding current. It also switches

AC or DC signals equally well.

8. Approvals are not available when an external reset

pushbutton and/or BNC connector and/or external

accelerometer is specified.

9. When an external reset pushbutton is supplied, the

remote reset terminals are not available for wiring.

10.

Although the switch monitors in RMS velocity units, the

signal at the optional BNC connector is unfiltered

100mV/g acceleration directly from the sensing

element.

11. The optional Power‐up Timed Inhibit (LOCKOUT)

feature is invoked by initial application of (or cycling)

primary power to the switch. This feature inhibits

alarms from activating for 20 seconds. This feature is

used primarily as a “startup delay” capability for

machines that exhibit elevated vibration levels during

startup relative to normal running levels. To invoke

the feature in this manner, power to the switch should

be applied (or cycled) concurrent with machine startup.

12.

20‐sec delay is factory set and not adjustable. Power‐

up Inhibit state is not annunciated externally and the

switch will automatically resume normal alarming

functions after 20 seconds have elapsed.

13.

The external sensor option is not compatible with

hazardous area approvals. Consider use of model 450

or SM6100 instead and mount external sensor in Metrix

explosion‐proof housing 7295‐002.

89


47/306

Document 1

Rev. E (Dec 2

Outlin

04730

013)

e Diagra

Da

s

Figure

(t

tasheet – 440 & 4

1 – Model 4

p cover rem

50 Electronic Vibr

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itch

Page 12 of 16

90


48/306

Document 1

Rev. E (Dec 2

Produ

Figure 4 ‐

Figure 6 –

p

04730

013)

t Photo

Model 440‐

Model 440

ushbutton (

Da

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ith optional

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50 Electronic Vibr

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odel 440 wit

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Page

ith standar

moved.

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(option F=7

15 of 16

dome cove

ffered

or 8)

91


49/306

Document 1

Rev. E (Dec 2

Metrix In

8824 Fall

Houston,

(281) 94

www.me

info@me

Trademarks

respective o

Data and

sp

notice.

© 2013 Met

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strument Co

brook Drive

TX 77064 US

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used herein are t

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50 Electronic Vibr

ation Switches Page 16 of 16

92


50/306

SMITH

PUMP

COMPANY, INC.

301 M&B Industrial(800) 299-8909 (254) 776-0377

Waco, Texas 76712FAX (254) 776-0023

SPCO responses to submittal review comments

Submittal No. 14AProject Number: 476399Specification: 44 42 56.03

1 Vibration Switch: Indicate which options are to be furnished. Ordering information partnumber on page 3 does not meet the Specification requirements. Revise and resubmit.44 42 56.03 Paragraph 2.04. TH

The cut sheet provided in the submittal is a general catalog sheet and not specific tothis or any project. The part number to be used on this specific project is as follows:376A-A3-C4-E. If there is another configuration that would be preferred please specify

exactly which options would be preferred on this project.

2 Footer correction: On pages 2 through 20 and any other page in the submittal thatincludes this error, the project title should be “Upper Trinity Regional Water DistrictThomas E. Taylor High Service Pump Station”.BB

Noted: Correction has been made

3 Page 4 (Table of Contents): Please clarify “may not be identical to the engineersspecifications” – Please disclose exactly what specification(s) will not match and why, at

the beginning of this submittal.BB

This is a general note in our submittal and does not reference any specific item, butshould apply to the whole submittal in general. All specific instances are clarified on thecomments and clarifications page.

4 CLARIFICATION: Page 12: Revision 1 Submittal Comment #3. In section 2.01.F.6.bsays Hermetically sealed switch, if noted. Confirmation was requested that hermeticallysealed is not required for this application. Hermetically sealed switch is not required forthis application.

TH

Noted


51/306

5 Based on last submittal response, all pump speed references should be consistentacross all instances and be 1193 rpm. Pages 29 and 33 of the submittal say 1185 rpm.BB

Noted, corrections have been made.

6 Test Procedure: Based on the flat pump curve between 8,000 and 11,000 rpm, duringpump testing, test at least at 1,000 gpm increments from 6,000 gpm to 16,000 gpm.BB

Noted

7 On the pump curve, the minimum continuous stable flow is identified; the maximumcontinuous stable flow should also be identified.BB

The run out flow (~16,000 GPM) would qualify as the maximum continuous stable flow.

8 On pump curve, bowl power is presumed to apply to the 20.61 in. rated diameterimpeller. Please confirm.BB

Confirmed

9 Confirm if FlowServe will be performing an NSPHr test.BB

Flowserve will not be preforming NSPHr testing.

10 Confirm if FlowServe will be testing with their suction strainer/vortex device.BB

The vortex suppressor will not be attached during any of the testing.

11 Testing Procedures: Procedure stated will be reading suction head with a ring on thesuction piping, which is not applicable for a VTP; should be measuring sump elevation.BB

Noted

12 Test Lab Layout: Alternate/optional location for control valve shown just upstream ofthe meter. This will not be allowed on test.BB

Noted


52/306

13 Page 83: Correct contractor name spelling on Discharge Head Engineering Analysisand Below Ground Dynamic Engineering Analysis; correct plant name spelling onTorsional Frequency Analysis and Discharge Head Reaction Loads pagesBB

Noted. Corrections made.

14 Motor is approved as submittedSH

Noted. Motor was released 6-19-14 for production.

15 Page 89 – Reed Frequency Results: Pump manufacturer shall proposemanufacturing modifications to change Modes 5 and 6 to be safely above the maximum1 X Mechanical running speed. VFD lockout of this frequency shall not be permitted.Reed frequencies of Modes 5 and 6 are too close to the maximum running speed of

pumps.BB

Noted. See attached revised analysis and additional information at end of analysis.

16 Page 97 – Figure 2: Include 2 X Mechanical excitation frequency and verify nointersection within the defined Low (-20%) and High (+20%) operating speed range.Provide transient torsional stress calculation where 1 X Mechanical critical speed withMode 1 and demonstrate resultant alternating stress is within the Modified GoodmanLine with2:1 FS.TN

Noted. See attached revised analysis.

17 Page 98 – Figure 3: Indicate full calculation regarding the mean and alternating shaftstresses. Also, include transient shaft stress for the 1 X Mechanical and first naturalfrequency of the shaft demonstrating that shaft stress is below the Modified GoodmanLine with 2 SF. Further, provide UTS of shaft material used to determine the shaftendurance (y-axis) and ultimate shear (x axis) for the Goodman Diagram. Lastly,provide separate plot for the motor shaft.TN

Noted. See attached revised analysis.


53/306

18 Page 104 – Base Reactions: Confirm axial load calculation incorporates additionalthrust from discharge piping associated with pipe stiffness and changes in diameterdownstream of the pump nozzle. Also, based on the structural Reed Frequency

Analysis and operating vibration limits verify nozzle loadings are within the maximumlimits stipulated above.

TN

Confirmed. See attached revised analysis.


54/306

Submittal 14A - VTP Full Comments



SUBMITTAL

NO.:14A PROJECT NUMBER: 476399

SPECIFICATION



1. REVIEWED 3. PARTIAL APPROVAL, RESUBMIT AS NOTED

2. REVIEWED AS NOTED 4. REVISE AND RESUBMIT

5. INFORMATIONAL


NO. COMMENT

RELATED

SPEC PARA./

DRAWING

REVIEWER’S

INITIALS

1 Vibration Switch: Indicate which options are to be furnished.

Ordering information part number on page 3 does not meet the

Specification requirements. Revise and resubmit.

44 42 56.03

Paragraph

2.04.

TH

2Footer correction: On pages 2 through 20 and any other page in the

submittal that includes this error, the project title should be “UpperTrinity Regional Water District Thomas E. Taylor High Service Pump

Station”.

BB

3Page 4 (Table of Contents): Please clarify “may not be identical to the

engineers specifications” – Please disclose exactly what specification(s)

will not match and why, at the beginning of this submittal.

BB

4CLARIFICATION: Page 12: Revision 1 Submittal Comment #3. In

section 2.01.F.6.b says Hermetically sealed switch, if noted.

Confirmation was requested that hermetically sealed is not required for

this application. Hermetically sealed switch is not required for this

application.

TH

5 Based on last submittal response, all pump speed references should be

consistent across all instances and be 1193 rpm. Pages 29 and 33 of the

submittal say 1185 rpm.

BB

6Test Procedure: Based on the flat pump curve between 8,000 and

11,000 rpm, during pump testing, test at least at 1,000 gpm increments

from 6,000 gpm to 16,000 gpm.

BB

7On the pump curve, the minimum continuous stable flow is identified;

the maximum continuous stable flow should also be identified.

BB


55/306

Submittal 14A - VTP Full Comments

8On pump curve, bowl power is presumed to apply to the 20.61 in.

rated diameter impeller. Please confirm.

BB

9Confirm if FlowServe will be performing an NSPHr test. BB

10Confirm if FlowServe will be testing with their suction strainer/vortex

device.

BB

11Testing Procedures: Procedure stated will be reading suction head with

a ring on the suction piping, which is not applicable for a VTP; should

be measuring sump elevation.

BB

12Test Lab Layout: Alternate/optional location for control valve shown

just upstream of the meter. This will not be allowed on test.

BB

13Page 83: Correct contractor name spelling on Discharge Head

Engineering Analysis and Below Ground Dynamic Engineering

Analysis; correct plant name spelling on Torsional Frequency Analysis

and Discharge Head Reaction Loads pages

BB

14Motor is approved as submitted SH

15Page 89 – Reed Frequency Results: Pump manufacturer shall propose

manufacturing modifications to change Modes 5 and 6 to be safely

above the maximum 1 X Mechanical running speed. VFD lockout of

this frequency shall not be permitted. Reed frequencies of Modes 5

and 6 are too close to the maximum running speed of pumps.

BB

16Page 97 – Figure 2: Include 2 X Mechanical excitation frequency and

verify no intersection within the defined Low (-20%) and High (+20%)

operating speed range. Provide transient torsional stress calculation

where 1 X Mechanical critical speed with Mode 1 and demonstrate

resultant alternating stress is within the Modified Goodman Line with

2:1 FS.

TN

17Page 98

44 42 56.03 - vertical turbine pumps - engineers comments & spco responses approved

Documents