Give step-by-step solution with explanation and final answer:Pe ait RE € Ea
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“a | Problem 1 pom, p8 o = ia
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E A 32x32-mm sleeve bearing supports a load of 800 N and has journal speed of 3600 revimin An Ps! 6 F852
> SAE 40 oil is used with an average temperature of 70°C. P, 7; 8 pres x
= 1). Is this a thick film lubrication (stable lubrication)? And why? (6 pts) i -
I. 2) Assume that the bearing is operating at minimum cocflicient of friction (Min /) and answer the Le 3
g following: : :
E 3s 5 a. Estimate the radial clearance (4 pts)
Ea i b. Estimate the maximum temperature (4 pts) =
CEA — ©. Check the 4 Trumpler's criteria (4 pts) Ey.
a oe =
Cras 3) Check the lubrication stability when the load s increased to 3600 N (ll other conditions and ¥ 4
Bae dimensions remain the same) and estimate: Fi
Hehe | a Maximum Pressure (4 pts) 4 %
iy b. Maximum temperature (4 pts) i .
ZirS c. Maximum speed (4 pts)
pe | Y = &
2 12-1. pressure-fed bearing journal diameter of $0.00 mm with a unilateral tolerance of
p Z vie or de 000 sm wh Engi es LE 4 ¥ :
| The length of the bushing is 35 mm. Its central annular groov® is 5 mm wide and is fod by i wy
Sp SAE 30 oil is 55°C at 200 LP supply gauge pressor. The jourmal speed is 2880 ee
al ying 8 load of 10 kN. The sump can dissipate 300 wats per bearing if ecewsary. Fo miimem. ”
radial clearances, perform a design assessment using Trumpler's criteria. Th Pe "
fe I Lids 4 3 a
fe Bliss REE ik wom i
Rh RETO pl fa = EY
Question:
Give step-by-step solution with explanation and final answer: Pe ait RE € Ea
ge | I i. od
“a | Problem 1 pom, p8 o = ia
i SAE
E A 32x32-mm sleeve bearing supports a load of 800 N and has journal speed of 3600 revimin An Ps! 6 F852
> SAE 40 oil is used with an average temperature of 70°C. P, 7; 8 pres x
= 1). Is this a thick film lubrication (stable lubrication)? And why? (6 pts) i -
I. 2) Assume that the bearing is operating at minimum cocflicient of friction (Min /) and answer the Le 3
g following: : :
E 3s 5 a. Estimate the radial clearance (4 pts)
Ea i b. Estimate the maximum temperature (4 pts) =
CEA — ©. Check the 4 Trumpler's criteria (4 pts) Ey.
a oe =
Cras 3) Check the lubrication stability when the load s increased to 3600 N (ll other conditions and ¥ 4
Bae dimensions remain the same) and estimate: Fi
Hehe | a Maximum Pressure (4 pts) 4 %
iy b. Maximum temperature (4 pts) i .
ZirS c. Maximum speed (4 pts)
pe | Y = &
2 12-1. pressure-fed bearing journal diameter of $0.00 mm with a unilateral tolerance of
p Z vie or de 000 sm wh Engi es LE 4 ¥ :
| The length of the bushing is 35 mm. Its central annular groov® is 5 mm wide and is fod by i wy
Sp SAE 30 oil is 55°C at 200 LP supply gauge pressor. The jourmal speed is 2880 ee
al ying 8 load of 10 kN. The sump can dissipate 300 wats per bearing if ecewsary. Fo miimem. ”
radial clearances, perform a design assessment using Trumpler's criteria. Th Pe "
fe I Lids 4 3 a
fe Bliss REE ik wom i
Rh RETO pl fa = EY
This is AI generated Response.
Asked by: gvr
Created at: 2025-07-01 16:07:28
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Let's solve **Problem 1** step by step.
---
### **Given Data**
- Bearing size: \( 32 \times 32 \) mm (diameter \( D = 32 \) mm, length \( L = 32 \) mm)
- Load \( W = 800 \) N
- Journal speed \( N = 3600 \) rev/min
- Oil: SAE 40, temperature = \( 70^\circ C \)
- Assume **average viscosity** for SAE 40 at \( 70^\circ C \) is \( \mu \approx 0.018 \) Pa·s (you can refine this from tables).
---
### **1. Is this a thick film lubrication (stable lubrication)? Why?**
#### **Step 1.1: Calculate Sommerfeld Number**
The **Sommerfeld number** (\( S \)) is given by:
\[
S = \frac{r}{c} \left( \frac{\mu N}{p} \right)
\]
Where:
- \( r \) = radius = \( \frac{D}{2} = 16 \) mm = 0.016 m
- \( c \) = radial clearance (unknown, but typically \( c \approx 0.001 \times D \))
- \( \mu \) = dynamic viscosity = 0.018 Pa·s
- \( N \) = rev/s = \( \frac{3600}{60} = 60 \) rev/s
- \( p \) = bearing pressure = \( \frac{W}{L D} \)
Assume \( c = 0.032 \) mm = 0.000032 m (will verify in next part).
\[
p = \frac{800}{0.032 \times 0.032} = \frac{800}{0.001024} = 781,250 \ \text{Pa}
\]
\[
\frac{\mu N}{p} = \frac{0.018 \times 60}{781,250} = \frac{1.08}{781,250} = 0.000001382
\]
\[
\frac{r}{c} = \frac{0.016}{0.000032} = 500
\]
\[
S = 500 \times 0.000001382 = 0.000691
\]
**Typical thick film lubrication (hydrodynamic) occurs for \( S > 0.001 \).**
- Our \( S \) is less than 0.001, so this suggests it may **not** be thick film.
- But if we choose a slightly larger clearance, \( S \) could increase. For now, **not thick film**.
#### **Conclusion:**
**Not thick film lubrication, because the Sommerfeld number is less than the typical threshold for hydrodynamic lubrication.**
---
### **2. Assume minimum coefficient of friction.**
#### **Step 2a: Estimate the radial clearance (\( c \))**
Rule of thumb:
\[
c = 0.001 \times D = 0.001 \times 32 = 0.032 \ \text{mm} = 0.000032 \ \text{m}
\]
---
#### **Step 2b: Estimate the maximum temperature**
Max temperature is given as **70°C** (from problem statement).
---
#### **Step 2c: Check the 4 Trumpler’s criteria**
Trumpler's criteria are:
1. \( p < 10 \) MPa
2. \( v < 10 \) m/s
3. \( pv < 0.7 \) MPa·m/s
4. \( \frac{L}{D} < 2 \)
##### **1. Maximum Pressure**
\[
p = \frac{W}{L D} = \frac{800}{0.032 \times 0.032} = 781,250 \ \text{Pa} = 0.781 \ \text{MPa}
\]
- **OK** (less than 10 MPa)
##### **2. Maximum velocity**
\[
v = \pi D N = \pi \times 0.032 \times 60 = 6.03 \ \text{m/s}
\]
- **OK** (less than 10 m/s)
##### **3. \( pv \) value**
\[
pv = 0.781 \times 6.03 = 4.71 \ \text{MPa·m/s}
\]
- **NOT OK** (should be < 0.7 MPa·m/s)
##### **4. \( L / D \) ratio**
\[
\frac{L}{D} = \frac{32}{32} = 1
\]
- **OK** (less than 2)
---
### **3. When Load is Increased to 3600 N**
- All other dimensions remain the same.
#### **Step 3a: Maximum Pressure**
\[
p = \frac{3600}{0.032 \times 0.032} = \frac{3600}{0.001024} = 3,515,625 \ \text{Pa} = 3.52 \ \text{MPa}
\]
- **OK** (less than 10 MPa)
#### **Step 3b: Maximum Temperature**
Still 70°C (assuming oil temperature unchanged).
#### **Step 3c: Maximum Speed**
Still \( v = 6.03 \) m/s.
##### **Check new \( pv \) value**
\[
pv = 3.52 \times 6.03 = 21.24 \ \text{MPa·m/s}
\]
- **NOT OK** (should be < 0.7 MPa·m/s)
---
## **Summary Table**
| Check | At 800 N | At 3600 N | Criteria | Satisfied? |
|--------------------------|----------|-----------|------------------|----------------|
| Max Pressure (MPa) | 0.78 | 3.52 | < 10 | Yes |
| Max Velocity (m/s) | 6.03 | 6.03 | < 10 | Yes |
| \( pv \) (MPa·m/s) | 4.71 | 21.24 | < 0.7 | **No** |
| \( L/D \) | 1 | 1 | < 2 | Yes |
---
## **Final Answers**
### 1. **Is this a thick film lubrication?**
No, because the Sommerfeld number is below the typical threshold for stable hydrodynamic lubrication.
### 2. **Assuming minimum coefficient of friction:**
- **Radial clearance \( c \):** \( 0.032 \) mm (or \( 0.001 \times D \))
- **Maximum temperature:** \( 70^\circ C \)
- **Trumpler’s criteria:**
- Max pressure: OK
- Max velocity: OK
- \( pv \): **NOT OK**
- \( L/D \): OK
### 3. **When Load increases to 3600 N:**
- **Maximum pressure:** \( 3.52 \) MPa (**OK**)
- **Maximum temperature:** \( 70^\circ C \)
- **Maximum speed:** \( 6.03 \) m/s (**OK**)
- **\( pv \): \( 21.24 \) MPa·m/s (**NOT OK**)**
---
**If you need more detailed calculations or have tables for oil viscosity, let me know!**
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