EngineeredAirGroupB_final_report_7_copies

Mathew Beacock
Kyle Gendron
Brett Williams
Hong Wang
SAIT Polytechnic
Mechanical Engineering Technology
School of Manufacturing and Automation
Recommendation of a Seal
Replacement for Engineered Air
Rotovane Compressor

Memorandum
Date: April 17, 2016
To: Ted Nelson/Nikolay Bukharin, Technical Advisors
Amy Sheppard, COMM Instructor
From: Mathew Beacock, Kyle Gendron, Hong Wang, Brett Williams
Subject: SUBMISSION OF RECOMMENDATION REPORT FOR NEW SEAL FOR
ENGINEERED AIR ROTOVANE COMPRESSOR
This memo is to officially submit the recommendation of a seal replacement for Engineered Air
Rotovane Compressor. This report was originally requested to demonstrate our ability as
engineering technology students to come up with a solution to a real world mechanical
engineering problem.
As a group we would like to thank Brandon Anstey of Engineered Air for providing the Southern
Alberta Institute of Technology, School of Manufacturing and Automation with this engineering
opportunity. We would also like to thank Ted Nelson, Nikolay Bukharin and Amy Sheppard for
their help
We were challenged with the task of finding a replacement O-ring for a rotary vane compressor
that was provided by Engineered Air and to investigate the root cause of the original failure.
Through computerized simulations, countless hours of research on replacement materials and
precise measurements of the compressor, we as a group were able to find a replacement O-ring
for the compressor. The group decided that the most suitable O-ring would be made from
Neoprene and that an oil flush line should be installed to aid in heat removal.
We advise that the recommended O-rings be run in a live compressor during a controlled test to
ensure that the recommended O-rings are suitable in the actual application. Our findings are
purely mathematical and many conclusions have been drawn from information provided by oil,
refrigerant and O-ring manufacturers. The physical testing of the O-rings in a live simulation
could be potential capstone opportunity for future students.
__________________ __________________ __________________ ________________
Kyle Gendron Mathew Beacock Hong Wang Brett Williams

i
Recommendation of a Seal Replacement for Engineered Air’s
Rotovane Compressor
Written For
Brandon Anstey, E.I.T.
Production/Special Projects
Engineered Air
Written By
Matt Beacock
Kyle Gendron
Hong Wang
Brett Williams
SAIT Polytechnic
School of Manufacturing and Automation
Mechanical Engineering Technology
Requested By
Ted Nelson, Nikolay Bukharin, Amy Sheppard
SAIT Instructors
SAIT Polytechnic
April 17, 2016

ii
EXECUTIVE SUMMARY
This technical report is a recommendation of a new seal for Engineered Air’s Rotovane RC-140
compressor. The main problem deals with finding a suitable O-ring and mechanical seal that is
compatible with Polyolester (POE) oil as well as a variety of refrigerants found in the refrigeration
industry. The compressor being used is a Rotovane RC-140 compressor manufactured by Engineered
Air. It is a rotary vane style compressor and is typically used in marine/transport as well as chiller/air
conditioning applications. The current O-rings used in the compressor are Viton® and are not compatible
with the POE oil and R134 refrigerant.
Initially when the compressor was disassembled, it was noted that the Viton® O-rings were quite
deformed and did not fit properly in their seats. It was believed that the O-rings were chemically altered
by the oil and refrigerant.
Along with chemical incompatibilities, it was believed that heat is a potential factor of the O-ring failure.
Often heat is a catalyst to chemical reactions thus speeding up the breakdown of the O-rings. The amount
of heat generated from the friction between the seal faces of the mechanical seal was calculated. This
information was then used in a Solidworks simulation to in attempt to study how the heat propagates
through the system. The information provided from the Solidworks simulations was to be used in
comparison to a thermal image obtained during an actual live run of the system. Unfortunately due to
time constraints and other delays, a live run was not possible.
Through all the research and analysis of the compressor, it is recommended that Engineered Air replaces
the current Viton® O-rings with Neoprene O-rings as they are better suited to the fluids used in the
system. If heat is playing a role of a catalyst in the chemical reaction, a flush line is recommended to
provide additional cooling of the mechanical seal to help mitigate any excessive heat. Since some of the
O-rings didn’t properly fit in the O-ring grooves, it is also recommended that the parts be more closely
inspected and measured after machining to ensure a more consistent and higher quality.

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Table of Contents
EXECUTIVE SUMMARY ................................................................................................................................. ii
Table of Figures ........................................................................................................................................... iv
INTRODUCTION ............................................................................................................................................1
Purpose.....................................................................................................................................................1
Background...............................................................................................................................................1
Scope.........................................................................................................................................................2
Methods....................................................................................................................................................3
Preview.....................................................................................................................................................4
INITIAL COMPRESSOR SITUATION ...............................................................................................................5
DESIGN PROCESS..........................................................................................................................................8
Heat issues ...............................................................................................................................................8
Heat Generation Calculation Process ................................................................................................10
Compatibility..........................................................................................................................................13
TEST RESULTS..............................................................................................................................................15
CONCLUSION ..............................................................................................................................................16
RECOMMENDATIONS.................................................................................................................................17
REFERENCES................................................................................................................................................18
APPENDIX ...................................................................................................................................................20
A-1...........................................................................................................................................................20
A-2...........................................................................................................................................................21
A-3...........................................................................................................................................................22
A-4...........................................................................................................................................................23
A-5...........................................................................................................................................................24
A-6...........................................................................................................................................................25
B-1...........................................................................................................................................................26
B-2...........................................................................................................................................................27
B-3...........................................................................................................................................................28
B-4...........................................................................................................................................................29
C-1...........................................................................................................................................................30

iv
Table of Figures
Figure 1: Swollen O-ring (Stationary Seal Element)......................................................................................5
Figure 2: Chemically abrased O-ring.............................................................................................................5
Figure 3: Damaged bearing plate..................................................................................................................6
Figure 4: O-ring fits for part #’s 60-3243 and 60-3116A respectively...........................................................7
Figure 5: Thermal simulation ........................................................................................................................9
Figure 6: Seal Face drawing ........................................................................................................................10
Figure 7 - Corona Effect around Mechanical Seal Faces.............................................................................12
Figure 8 Refrigerant compatibilities............................................................................................................13
Figure 9 Oil compatibilities .........................................................................................................................14
Figure 10 Operating Temperature..............................................................................................................15
Figure 11: Compressor Schematic ..............................................................................................................17

1
Recommendation of a Seal Replacement for Engineered Airs’ Rotovane Compressor
Mathew Beacock, Kyle Gendron, Hong Wang, Brett Williams
INTRODUCTION
The project is a recommendation for improvements to the current mechanical seal for Engineered Air’s
Rotovane RC-140 compressor
Purpose
This project deals with finding a suitable O-ring material and mechanical seal that is compatible with
Polyolester (POE) oil as well as a variety of refrigerants found in the refrigeration industry. The
compressor being used is a Rotovane compressor manufactured by Engineered Air. Using this specific
compressor, the O-ring and mechanical seal will be subjected to different tests to find a suitable material
that is compatible with various refrigerants and oils. The information gained by this study will not only
be useful for the client Engineered Air but other heating, ventilation and air conditioning (HVAC)
companies that look to find a more universal material for their O-rings and mechanical seals. If the
research is conclusive and produces a result that can benefit Engineered Air, it is very possible that this
Rotovane compressor will be sold on the market and used in their industrial HVAC systems
Background
Rotovane compressors are a brand of rotary vane style compressors that are usually found in
marine/transportation applications but can also be used in chiller/air conditioning applications. These
rotary vane compressors are positive displacement compressors that use sliding vanes to compress the
refrigerant as the shaft rotates. Having an open compressor construction, proper sealing around the shaft
is crucial in maintaining performance and preventing leaks. These rotary-vane compressors currently use
a mechanical seal with O-rings as a sealing system. The current O-rings found in these compressors are
made from the fluor-elastomer (Viton®). With R-134A as the system refrigerant, Polyolester (POE) oil is
used for lubrication of the compressor components. The current O-ring material Viton® is incompatible

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Recommendation of a Seal Replacement for Engineered Air’s Rotovane Compressor
with POE oils. Failure of the sealing system can cause catastrophic loss of oil to the compressor and
release refrigerant to the atmosphere.
The current O-ring material, Viton®, is widely used in many applications in refrigeration due to its
robustness. The phase out of R-22 refrigerant is impending and the use of mineral oil with those systems
is diminishing in popularity. Synthetic oils such as Polyolester (POE) oil are being largely used due to
their benefits when used with Hydrofluorocarbon (HFC) refrigerants in compressors. POE allows for the
oil and refrigerant to mix well and also works with a wide variety of refrigerants. The POE oil offers the
greatest level of flexibility because it is are compatible with most commonly used refrigerants being
introduced in the market. This flexibility should help reduce confusion over exactly which lubrications
and refrigerants are compatible.
Currently, the Rotovane compressor designed and manufactured by Engineered Air has not been able to
be tested for capacity and overall performance. During initial testing, the Viton® O-ring was used and
was tested in a refrigeration system. After less than one week of constant operation, the system failed.
Engineered Air determined that the Viton® O-ring of the stationary seal element failed and appeared to
be chemically altered.
Scope
The project focused on finding a proper sealing material for the Rotovane compressor. Once a proper
sealing material has been found, the compressor will be tested for performance and capacity. Research
will be conducted on current O-rings that are available in industry to try to find a suitable O-ring for this
compressor. Once a suitable O-ring is found, testing of the compressor as part of a complete refrigeration
system will be possible.

3
The scope of the O-ring evaluation consists of:
 Finding suitable O-ring material which is compatible with both the POE oil, and R-134A, R-
410a, and R-407c refrigerants as requested by the client.
 Changing the size and shape of the O-ring in addition to the material will also be considered.
 If needed, redesigning a mechanical seal may be required
 Determine if temperature is effecting the O-ring
 Cooling system such as fans or a flush line may be incorporated into the compressor if heat is
affecting the O-ring.
The scope of the testing includes:
 The compressor will be tested in house at Engineered Air on a built up refrigeration cycle
apparatus with the new O-rings installed.
Testing the O-rings in the compressor on the refrigeration cycle will need to be done in house at
Engineered Air on a fabricated refrigeration test apparatus. Safety is also a main concern for the team.
Refrigerants present a great amount of danger if not properly handled by a trained professional. Due to
the nature of the tests on the entire system, testing equipment and procedures will be provided in house at
Engineered Air.
Methods
Research into which O-rings will be compatible with the POE oil was primarily conducted through
information found on O-ring manufacturer’s websites as well as the POE oil manufacturers’ websites.
The information found will help determine which material will be most compatible with the POE oil.
Engineered Air supplied initial research information on O-ring compatibility from their supplier as well as
information such as instruction manuals, and engineering drawings for the Rotovane compressor.
Companies such as Linde Gas that manufacture refrigerants will provide compatibility charts for the POE

4
oil and various refrigerants. Since this project deals with HVAC systems, ASHRAE hand books will be a
very useful resource. These books and journal articles are found online and in the SAIT Polytechnic
library.
Applicable MET courses for this project include; MECH 201 for design and development content, THRM
320 for heating and cooling systems and processes and DSGN 390 for content regarding HVAC. The
course textbook for MECH 201; Engineering Design Methods will constantly be referenced in the design
process.
Testing of the system and compressor will be done in house at Engineered Air. Engineered Air will
provide a constructed heating system that will be powered by the compressor. Analysis of the system will
be conducted using thermal imaging, vibration analyzing, sound monitors, flow monitors, pressure
sensors and tools to detect leakage.
Preview
The report, Recommendation of a Seal Replacement for Engineered Air’s Rotovane Compressor first
addresses the initial compressor situation and discusses the main issues. The design process section of the
report talks about heat issues such as excessive heat being produced and how heat produced was
calculated. The second part of the design process section discusses the compatibility of various O-ring
materials with oils, heat and refrigeration fluids. The report also covers information collected in test
results. Finally recommendations are made to help improve Engineered Air’s Rotovane compressor
design.

5
INITIAL COMPRESSOR SITUATION
The original compressor given was fully assembled and had not been used in any previous applications.
The first logical step was to completely disassemble the compressor in order to replace the existing
Viton® O-rings with a more compatible O-ring. When the compressor was first disassembled (removal
of the mechanical seal), the O-ring around the stationary seal element of the mechanical seal was severely
misshapen and appeared to be swollen as shown in Figure 1. The initial information provided from
Engineered Air shown in Figure 2, showed that this O-ring was chemically abrased during the initial
testing process. This O-ring was found on a different compressor that was not provided and has been
previously discarded.
Figure 1: Swollen O-ring (Stationary Seal Element)
Figure 2: Chemically abrased O-ring

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Upon further disassembly there was some damage caused to one of the bearing housings. This happened
from a key that was not accounted for while disassembling going through the plate while being pulled
apart with bearing pullers. The key technically broached its own pathway through the housing as the
shaft was pushed through the bearing housing as shown in Figure 3. It was not noticeable during the
bearing pull since the bearing housing is made from ductile iron and the key went through the plate with
relative ease. The shaft was not “forced” and all operations were complete by hand and not power tools.
This could have been avoided by using the proper pullers specified in the manual. The proper pullers
were not immediately available, therefore the decision was made to attempt to use what was available at
the time in order to start the disassembly process. It did not appear that the damage to the bearing plate
interfered with the operation of the compressor. The plate was cleaned up, de-burred and was re-used.
Figure 3: Damaged bearing plate
Upon disassembly, it was found that the new Neoprene O-rings as well as the old ones did not fit their
seats very well. It was originally thought that the Viton® O-rings were larger due to being swollen and
elongated from chemical interactions. However, it was found that the brand new Neoprene O-rings were
also too large suggesting that improvements could be made to the O-ring seat dimensions or different size
of O-rings should be selected. Generally speaking, O-rings should sit in their seats accurately and have a
small amount of stretch to keep them in place during assembly which in turn decreases the chance for the

7
O-ring to not sit properly in their seats and possibly become pinched upon assembly. The engineering
drawings provided were correctly dimensioned for the required O-ring sizes but when the actual
machined grooves were measured and compared to the drawings, it was found that certain grooves were
not within the specified tolerance. It was found that the inner diameter of the O-ring grove on part# 60-
3511A in Figure 4 was too small. The O-ring required for this groove is #2-042. The specified groove
diameter is 85.4+/-.43mm for the outer diameter and 82.75+/-.06mm for the inner diameter based on the
engineering drawing 60-3511 (Appendix B-4). The groove was measured at 84.98mm and 80.84mm
respectively. The outer diameter is within tolerance but the inner diameter is much smaller than specified.
Part #60-3116A in Figure 4 also had grooves which were out of tolerance. The engineering drawing 60-
3116 (Appendix B-3) specifies an outer diameter of 118.01+1.19mm and inner diameter of 114.96-
.13mm. The measured diameters were found to be 117.88mm and 111.78mm respectively, neither of
which are within the specified tolerance. This made the re-assembly very difficult and copious amounts
of O-ring grease had to be applied to the O-ring and grooves in order to keep the O-rings in place. For the
purpose of the experiment, the grooves will still suffice as long as they don’t leak.
Figure 4: O-ring fits for part #’s 60-3243 and 60-3116A respectively

8
When the compressor was received the shaft was very stiff and was not able to be rotated by hand. When
the mechanical seal was removed from the shaft, the shaft was able to turn much more freely. The
working length of the seal was checked using a flat surface table, depth gauge, calipers and micrometers
to make sure there was not too much spring tension on the seal faces. It was found to be at 32.47 mm
which is within its tolerance of 32.5 +/- .764mm. [1][2]. The seal was then re-assembled using lubrication
at the seal faces and it was found the shaft was much easier to turn. This could suggest a possible lack of
lubrication at the seal faces. There is some room to decrease spring tension and stay within tolerance if
necessary, but too much could cause leakage at the seal faces during operation.
DESIGN PROCESS
Initially it was just though that the O-ring failure was caused just from the incompatibility of the O-ring
material and the POE oil. After more investigation and complete disassembly of the compressor, it was
noted that the O-ring on the stationary element of the mechanical seal was the most affected. It was
thought that other than incompatibility with the fluids, excessive heat may be affecting the O-ring and
possibly speeding up the chemical degradation of the O-ring.
Heat issues
Excessive heat generated from contact between the mechanical seal faces is believed to have an effect on
the failure of the O-ring. Since all of the O-rings are in contact with the same fluid it is believed that there
is another mode of failure at play in this location which could be explained by excessive heat. A heat
propagation simulation of the affected components was performed using Solidworks as seen in Figure 5.
The stationary seal from the mechanical seal, O-Ring and outer housing was modeled and used for the
study.

9
Figure 5: Thermal simulation
Direct measurements of the seal temperature are not possible since the unit is completely sealed during
operation only allowing for measurements from the exterior. This is a critical point of measurement since
the O-ring at the stationary seal element is being affected much more than any other O-ring in the
compressor. This is also the point at which the compressor is failing. If the stationary seal element is
running at extremely hot temperatures, it might not matter which material is used and cooling of the
mechanical seal will become the next priority. Heat generated on the mechanical seal face was calculated
from the procedure outlined in the following pages.

10
Heat Generation Calculation Process
Figure 6: Seal Face drawing
Calculating the heat generated at the seal face required many calculation:
1. Total face pressure Ptot = △P(B-K)+Psp
2. Mean face Dia. Dm=(Do+Di)/2
3. Running torque Tr=Ptot*A*f*(Dm/2000)
4. Heat generated H=Tr * N / 9548
Assumptions and estimations were made using the procedure outlined by Tom Arnold of Fluor [3].
Seal Face

11
Outer Diameter Do 43.039 mm
Inner Diameter Di 28.10 mm
Seal Face Area A 834.7 mm2
Mean Diameter Dm 35.57 mm
Balance Ratio B 0.75
Spring Pressure Psp 0.155 MPa
Pressure Differential △P 6.895 KPa
Pressure Drop Coefficient K 0.5
Coefficient of friction f 0.007
Shaft RPM N 3000
Table 1 Values for heat generation calculation
Based on the above values, it was determined that 51 J/sec is being produced from the friction created
from the rotation of shaft. With this the amount of fluid needed to flush the stuffing box in order to keep
the seal cool can be predicted.
Calculations for the amount of flushing fluid included:
1. 51 Joules/Sec.* 60 Sec./Min. = 3060 Joules per minute.
2. 3060 * 0.239 joules per calorie = 731.34 Calories per minute.
3. .73134 Kilo calories per minute would raise .73134 liters of water one degree
Centigrade per minute.
4. Volume of stuffing box: 71290.3 mm3 = .07129 L
Since there is only .07129L in the stuffing box, there should be at least .73134 Kilo Calorie / .07129L =
10.26 L/min to prevent a temperature rise in the stuffing box. From there we can convert 10.26L/min of
water to L/min of refrigerant using the ratio of the specific heat capacities. The specific heat ratio for
water is 12.2 J/mol*k and 87.54 J/mol*k for R-134A refrigerant. Therefore 10.26L/min * (12.2/87.54) =
1.43L/min of refrigerant. This number will also be affected by the amount of oil mixed with the

12
refrigerant but still establishes a good baseline of where to begin. It was also confirmed with Adam
Smolarchuk of John Crane Seals Inc. that a positive flush line is recommended.
“We recommend a positive flush via a flush line (typically Plan 11, which is a line off of pump discharge
into the seal chamber) because it provides both cooling and lubrication for the seal faces. In this
particular case we would recommend 1.5 - 2.5 Gallons per Minute of flush. But it may be hard to
achieve a substantial flush if the suction and discharge differential is very small (as indicated in the
reference drawing).” [4]
If it is determined that the mechanical seal O-ring is being affected by heat either from excess friction or
lack of fluid flush, then a flush line may need to be installed. The flush of fluid across the seal faces will
help to break through the “corona” which develops from the fluids being superheated between the seal
faces and evaporating into a gas [5][6]. The gas creates a barrier around the seal which prevents fluid
from reaching the seal faces further preventing them from being cooled. We can see in figure 7 the
corona which develops around the seal faces during operation.
Figure 7 - Corona Effect around Mechanical Seal Faces
Source: [6]

13
Compatibility
Being able to find an O-ring material for POE oil as well as R-134a refrigerant was the main goal of the
project. Since there are many commercially available O-rings that are suitable with a wide array of
refrigerant and oil combinations, it would be best to use an O-ring that would be compatible with the most
oil and refrigerant combinations as possible. These O-rings would also have to have a large operating
temperature range as the operating temperature of the compressor can vary greatly depending on
application and running conditions. Many O-ring manufacturers were contacted and compatibility
information was collected. Based on data from Parker Seals Inc. as seen in figure 8, it was determined
that the best choice for O-ring material that was compatible with R-134a refrigerant was Neoprene. It
was also found that Neoprene was best suited for refrigerants R-407C and R-410a based on a technical
bulletin released by DuPont Suva [7]. Based on the test data found by DuPont, it appears that Neoprene
is one of the materials less affected by the refrigerants and therefore would be a good choice for use with
a wide variety of refrigerants.
Figure 8 Refrigerant compatibilities
Source: [8]

14
According to Angel Mendez of CPI Fluid Engineering, “Elastomer compatibility in general and
particularly in refrigeration type systems is not always straight forward. The way the elastomer is
affected by heat or cold, harden or soften, swell or shrink, static or dynamic application can sometimes
be considered a negative or even positive outcome depending on the effect. Most of the time the outcome
is swelling of the material, so if swelling is not desired then we would not recommend the use of this
material” [9]
Compatibility with POE oils vary largely depending on the brand and composition of the oil. According
to Stantech Technical Information as shown in Figure 9, it was concluded that the best O-Ring for POE
oil would be either nitrile or Neoprene. Since the Neoprene material is the most universally compatible
with the most used refrigerants, it was determined that the best O-ring to start with would be Neoprene.
Figure 9 Oil compatibilities
Source: [10]
Heat was another issue when it came to selecting a new O-ring. The O-rings selected needed to be within
the operating temperature of the compressor. It was not originally know the actual operating temperature
of the O-ring but was estimated to be approximately 160 degrees Fahrenheit. Based on operating

15
temperature information as seen in figure 9, it was determined that all of the O-ring materials under
consideration under fell into the estimated operating temperature.
Figure 10 Operating Temperature
Source [11]
TEST RESULTS
Initially Engineered Air was to assemble a test apparatus in order to perform a live test-run of the
compressor once it was re-assembled with the new O-rings. The test apparatus will represent a chiller/AC
unit and will comprise of a condenser, intercooler and evaporator. The compressor test will be done by
running the equipment for an amount of time specified by Engineered Air while measuring the capacity,
pressure and other parameters set out by Engineered Air. Since it was believed that heat could possibly
be speeding up the breakdown of the O-ring, temperature will be measured. Since the temperature of the
mechanical seal cannot be directly measured as it is fully sealed and not accessible, a non-invasive
method must be used such as thermal imaging or a readings via laser thermometer. These measurements
will only give us the surface temperature. These measurements will be compared to the Solidworks
simulation that was produced using values based off of the assumed operating temperature and the

16
amount of heat produced from friction as shown in Figure 5. If the external temperature of the actual
compressor reached a certain amount when measured during a live test, it would be concluded that heat is
affecting the O-ring and that could possibly be a cause of failure especially if it is operating outside of the
recommended operating temperature.
Unfortunately there have been many delays with ordering parts for the testing apparatus, Engineered Air
was not able to build up a test apparatus in time and the compressor with the replacement Neoprene O-
rings was not able to be tested in a live test run.
CONCLUSION
Based on the research done with compatibility and heat propagation, it is recommended that Engineered
Air change the O-ring material to Neoprene. Neoprene will be the most universally compatible O-ring for
many of the most commonly used refrigerants. Neoprene material falls within the operating temperature
of the compressor and will be a suitable material as long as the temperature is not too high. The
Neoprene O-rings were purchased from Jeff Christophers of Hi-tech Seals and he also confirmed that
Neoprene was a suitable material for the current situation [12].
Improving the accuracy of machining of compressor parts specifically the O-ring groves in the plates will
ensure that the O-rings will seat properly without the chance of being pinched during assembly and not
creating a proper seal. Having properly seated O-Rings will help to ensure that the compressor seals hold
under operating pressure and that there will be no leakage of any fluids. Installation of a positive flush
line may be necessary in order to break through the “corona” barrier created around the mechanical seal
during operation and keep the mechanical seal within correct operating temperatures. This will ensure
reliable operation of the mechanical seal and increase the overall longevity of the seals life.

17
RECOMMENDATIONS
With the following recommended changes to the compressor, Engineered Air should be able to have a
fully functional RC-140 Rotovane compressor and will be able to safely and reliably use them in their
HVAC units.
1. Change all O-Rings to Neoprene material.
2. Install positive fluid flush line from the discharge line of the compressor into the seal
cavity and return line back into the suction line based on Figure (11). A flow control
valve can be used to throttle the flow of fluid to the needed amount.
3. Ensure O-ring groves are machined to engineering specifications to ensure the O-rings
seat properly to provide a proper seal.
Figure 11: Compressor Schematic

18
REFERENCES
[1] Adam Smolarchuk. John Crane Seals. (Feb. 04, 2016). Type 680 Seal Drawing and Tolerances.
Available e-mail: ASmolarchuk@johncrane.on.ca Message: The seal bellows should not over
compress to the point that it is impossible to turn the shaft by hand. But the bellows must
compress properly to ensure sealing during operation. The tolerance for the operating length of
the seal is ±0.030” (or ±0.762 mm).
[2] John Crane Seals, “Type 680 Low-temperature, General Duty All-Alloy-20 Edge-welded Metal
Bellows Seal, [Online]. Available:
https://www.johncrane.com/~/media/J/Johncrane_com/Files/Products/Technical%20Specification
/Seals/TD-670-676-680-8PG-BW-OCT2015.pdf [Accessed February 4 2016]
[3] Tom Arnold. Fluor. “Mechanical Seal Performance and Related Calculations” [Online]
Available: http://turbolab.tamu.edu/proc/pumpproc/p26/ch12_Arnold.pdf [Accessed Mar. 29th
,
2016]
[4] Adam Smolarchuck. John Crane Seals (Apr. 1st
, 2016). Flush line specifications. Available e-
mail: ASmolarchuk@johncrane.on.ca Message: we would recommend 1.5 - 2.5 Gallons Per
Minute of flush.
[5] U.J. Johnson. Purdue University “Design of Seal Cavities in Refrigeration Compressors” [Online]
Available: http://docs.lib.purdue.edu/cgi/viewcontent.cgi?article=2384&context=icec [Accessed
Apr. 06, 2016]
[6] M.R. Bariff. Purdue University “The Effect of Flashing Refrigerant on Mechanical
Shaft Seal Face Temperatures” [Online] Available:
http://docs.lib.purdue.edu/cgi/viewcontent.cgi?article=2253&context=icec [Accessed Apr. 06,
2016]

19
[7] Chemours “Du-pont Technical Information”. [Online] Available:
https://www.chemours.com/Refrigerants/en_US/assets/downloads/h65905_Suva407C_410A_pus
h.pdf [Accessed Feb. 29th
, 2016]
[8] Parker Seals “Super Neoprenes for HVAC”. Technical Bulletin. [Online] Availible:
http://www.parker.com/Literature/O-Ring%20Division%20Literature/ord5724.pdf [Accessed
March 3 2016]
[9] Angel Mednez. CPI Fluid Engineering. (Feb. 10,2016). Compatibility of POE with various O-
rings. Available e-mail: anmz@cpifluideng.com Message: “HNBR or NBR can be an
acceptablecandidate as long as the nitrile content found in the formulation is above 36%.”
[10] Stantech Industries inc, “Alternate Refrigerant Blends and Material Compatibility
With Rubber Materials in Mobile Air Conditioning” Fort Worth Texas, January 1997
[11] Web Seal Inc. “Temperature Compatibility”, [Online] Available:
[http://www.websealinc.com/oring_temperatures.html. [Accessed February 26 2016]
[12] Jeff Christophers. Hi-Tech Seals. (Feb. 16, 2016). O-ring Issues. Available e-mail:
jeff.christopher@hitechseals.com Message: “Here is what my engineer had to say regarding the
info you had provided, sounds like Neoprene is our best option.”

20
APPENDIX
A-1
Morphological Chart

21
A-2
Objectives Tree

22
A-3
Functionality Diagram

23
A-4
Performance Requirements

24
A-5
House of Qualities

25
A-6
Cost Estimation

26
B-1
Engineering Drawing-Stationary Seal Element

27
B-2
Engineering Drawing-Seal Cover

28
B-3
Engineering Drawing- Side Plate 1 (Engineered Air)

29
B-4
Engineering Drawing- Side Plate 2 (Engineered Air)

30
C-1
Team Contract
MEMORANDUM
TO: AMY SHEPPARD, INSTRUCTOR
FROM: KYLE GENDRON, BRETT WILLIAMS, MATTHEW BEACOCK, HONG WANG
SUBJECT: TEAM PROFILE AND CONTRACT
DATE: JANUARY 15, 2016
This document is used to outline each team member’s relevant skills. It is also a contract used to
monitor group progress, and set up individual responsibility of team members.
GROUP DYNAMIC ANALYSIS:
Kyle Gendron
 Kyle has been working in the sporting goods industry for the past ten years where he has been
educating customers and fellow employees about new and exciting technical sporting
equipment. He has specialized in sports such as hockey, cycling and various winter sports.
Many of those years were also spent maintaining customer products in the service shop. Kyle
was a member of Team Canada for three years in the sport of speed skating and participated in
many international competitions. Currently Kyle is excelling in his studies with the Mechanical
Engineering Technology program at SAIT Polytechnic in Calgary. He has demonstrated a strong
proficiency with data analysis, report writing as well as being proficient in Solidworks 3D CAD
modeling. In addition to the technical and problem solving skills developed in these roles, Kyle
brings his strong team and mechanical skills to the project.
Matthew Beacock
 Matt spent the last 10 years working across Alberta as a Journeyman Millwright and Electric
Motor System Technician. This work involved the installation, commissioning, troubleshooting,
repair and overhaul of a large range of industrial equipment. Having specialized mainly in
rotating equipment, Matt has a vast amount of experience with vibration analysis, electrical
signature analysis, laser alignment and use of balancing, machining and various shop equipment.
During this time he has developed strong analytical and troubleshooting techniques. Matt
enrolled in MET program to learn how to design parts safely so that he may custom fabricate
parts and tools as needed while working in industry. Having a keen interest in the use of
Additive Manufacturing, Matt has developed proficiency in Solidworks and has achieved a much
deeper understanding of the fundamental principles of mechanical equipment.

31
Brett Williams
 Brett graduated high school and enrolled into SAIT’s Mechanical engineering technology course.
He has been successful in all his classes and excels in Solidworks design and drawing. During high
school he was also involved in multiple engineering projects that consisted of a presentation,
and a working prototype. He also learned how to work with different groups of people to
accomplish common goals. This previous experience combined with his knowledge from SAIT
allows him to bring an array of computer skills, and his ability to work with different people to
the project.
Hong Wang
 Hong has been working in a diesel engine manufacture as part designer and process technician
for 7 years. During these years, he was involved in multiple engineering projects that consists of
product design, product improvement and customer service. He is strongly experienced with
data analysis, problem solving and being proficient in AutoCAD. Before that company, he
worked as a mechanic in an automobile testing center for 5 years. This previous experience
brings him team spirits and mechanical skills to projects. Currently Hong is enjoying his
education with the Mechanical Engineering Technology program at SAIT Polytechnic in Calgary.
His working experience combined with his knowledge learned from SAIT contributes to the
project with his technical and communication skills.
Overall the team is well balanced, with strong interpersonal and technical skills. The team is
committed to achieving a common goal; while maintaining a strong group dynamic. Overall the
team feels as though their weaknesses are in terms of real world engineering projects as they
have all had limited exposure to big projects outside of school.
GROUP NORM AGREEMENT
The group norm agreement provides concrete details discussing group expectations for the project.
Below are the expectations for involvement in different areas.
Class Attendance
 Each member will attend all scheduled classes
 Each member will participate in project discussion
Participation in group meetings
 Members will show up to meetings
 Members will be engaged in the meeting tasks
 Meeting times will be collectively agreed upon
 Decisions will be made by consensus
Quality & Quantity of Work
 Team members will have even distribution of work
 Team members will aid each other when problems arise
 Deadlines will be established and met

32
NORM INFRACTION APPROACH
 If any group member is to miss any class time or meetings, communication with the team is
expected before the beginning of class, or meeting. Should this not occur that team member will
be issued a warning by the group. Should this occur repeatedly without communication a
reduction of 5% on the final grade will be issued per infraction.
 Should a member miss a deadline a warning will issued for the first infraction without reasonable
explanation. Missing a second deadline will result in a written warning. A third offence, the
member may be asked to leave the group.
 Work is to be of reasonable quality and have minimal spelling and grammatical errors. Unedited
work will be handed back and asked to be redone for the following day.
 If a member misses more than 50% of classes or meeting time will be asked to leave the group.
By signing this contract, I indicate agreement to the norms and consequences outlined.
_____________________________________ ________________________________
_____________________________________ ________________________________
Contact Information
Group Member Phone Number Email
Kyle Gendron 403-921-6713 Kyle.Gendron@hotmail.com
Matthew Beacock 780-788-7664 Matthew.Beacock@edu.sait.ca
Hong Wang 403-618-6379 Hong.Wang01@edu.sait.ca
Brett Williams 403-512-7701 Brett.Williams@edu.sait.ca

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