DEPARTMENT OF MECHANICAL ENGINEERING BHARATH UNIVERSITY CHENNAI-600073 OCTOBER 2010 BONAFIDE CERTIFICATE
Certified that this project report “SIX BAR SLIDER CRANK POWER HAMMER MECHANISM” is the bonafide work of “YEMMINA MADHUSUDHAN” who carried out the project work under my supervision.
Dr. T.J. PRABHU
JOSE ANANTH VINO. V
HEAD OF THE DEPARTMENT
GUIDE
Mechanical Department
PROFESSOR
BHARATH UNIVERSITY
Mechanical Department
173, Agaram road, Selaiyur, Chennai 73.
BHARATH UNIVERSITY 173, Agaram road, Selaiyur, Chennai 73
AIM: To design and fabricate a simple mechanical operated power hammer by applying the principle of kinematic arrangement and machine design concepts.
1.
1.1
INTRODUCTION TO MECHANISMS
Concept of degrees of freedom
In the design or analysis of a mechanism, one of the most important concern is the number of degrees of freedom (also called movability) of the mechanism. It is defined as the number of input parameters (usually pair variables) which must be independently controlled in order to bring the mechanism into a useful engineering purpose.
Degrees of Freedom of a Rigid Body in a Plane The degrees of freedom (DOF) of a rigid body are defined as the number of independent movements it has. Figure 1.2 shows a rigid body in a plane. To determine the DOF of this body we must consider how many distinct ways the bar can be moved. In a two dimensional plane such as this computer screen, there are 3 DOF. The bar can be translated along the x axis, translated along the y axis, and rotated about its centroid.
Fig 1.2
fig 1.3
3
Degrees of Freedom of a Rigid Body in Space An unrestrained rigid body in space has six degrees of freedom: three translating motions along the x, y and z axes and three rotary motions around the x, y and z axes respectively in the as shown in the fig 1.3 1.4
Kutzbach Criterion Equation Consider a plane mechanism with number of links. Since in a mechanism,
one of the links is to be fixed, therefore the number of movable links will be ( -1) and thus the total number of degrees of freedom will be 3(n-1) before they are connected to any other link. In general, a mechanism with number of links connected by j number of binary joints or lower pairs (i.e. single degree of freedom pairs) and h number of higher pairs (i.e. two degree of freedom pairs), then the number of degrees of freedom of a mechanism is given by n = 3( -1)-2j-h This equation is called Kutzbach criterion for the movability of a mechanism having plane motion. If there are no two degree of freedom pairs (i.e. higher pairs), then h= 0, substituting h= 0 in equation 1, we have n=3( -1)-2j
1.5
Four bar chain mechanism The simplest and the basic kinematic chain is a four bar chain or quadratic
cycle chain, as shown in below fig. It consists of four links p, q, l and s, each of them forms a turning pair. The four links may be of different lengths. According to Grasshof’s law for a four bar mechanism, the sum of the shortest and longest link lengths should not be greater than the sum of the remaining two link lengths if there is to be continuous relative motion between the two links.
4
According to Grasshof’s law for a four bar mechanism, the sum of the shortest and longest link lengths should not be greater than the sum of the remaining two link lengths if there is to be continuous relative motion between the two links. A very important consideration in designing a mechanism is to ensure that the input crank makes a complete revolution relative to the other links. The mechanism in which no link makes a complete revolution will not be useful. In a four bar chain, one of the links, in particular the shortest link, will make a complete revolution relative to the other three links, if it satisfies the Grasshof’s law. Such a link is known as crank or driver. 1.6
Single Slider Crank Mechanism A single slider crank chain is a modification of the basic four bar chain. It
consists of one sliding pair and three turning pair. It is, usually, found in reciprocating steam engine mechanism. This type of mechanism converts rotary motion into reciprocating motion and vice versa. In single slider crank chain, as shown in below fig the links 1 and 2, links 2 and 3, and links 3 and 4 form three turning pairs while the links 4 and 1 form a sliding pair.
5
The link 1 corresponds to the frame of the engine, which is fixed. The link 2 corresponds to the crank; link 3 corresponds to the connecting rod and link 4 corresponds to cross- head. As the crank rotates the cross-head reciprocates in the guides and thus the piston reciprocates in the cylinder.
2.
Study of Power Hammers
Until now we have confined ourselves to study of hand tools used in smithy work. They certainly perform very well so far as the hand- forging is concerned, but their use for satisfactory production is limited to small forging only. It would not be difficult to understand that the intensity of blows, however great one may try to achieve through hand hammering, will not be sufficient enough to effect the proper plastic flow in a medium sized or heavy forging. For this, a power hammer is usually employed. The capacity of these hammers is given by the total weight of their falling parts i.e., tup or ram and die. A 200 kg hammer will be one of which the falling parts weigh 200 kg. The heavier these parts and greater the height from which they fall. The higher will be intensity of blow the hammer will provide. Power hammers in common use are of different types e.g. spring power hammers, pneumatic power hammers, Steam hammers and Drop or Forge hammers and six bar slider crank power hammers. These hammers are named partly after their construction, partly according to their way of operation. Apart from these, a large number of forging presses and
6
machines are used in forging work. In the following articles these hammers and machines will be discussed in detail.
2.1
Types of Power Hammers
2.1.1
Helve hammer Helve hammers are well adapted for general engineering work where the size
of the stock is changed frequently. They consist of a horizontal wooden helve, pivoted at one end with a hammer at the other end. An adjustable eccentric raises the hammer which when falls strikes a blow. They are made in sizes from 5 to 200kg. 2.1.2
Trip Hammer Trip hammers have a vertically reciprocating ram that is actuated by toggle
connection driven by a rotating shaft at the top of the hammer. Trip hammers are also built in sizes from 5 to 200 kg. The stroke range of both helve and trip hammers ranges from about 400 per minute for small sizes to about 175 for large size.
2.1.3
Lever-Spring Hammer They are mechanical driven hammers with a practically constant lift and an
insignificantly variable striking power. It only increases with increasing operating speed and thus has increases number of strokes per minute. The ram is driven from rocking lever acting on an elastic rod. The rocking lever consists of a leaf spring so that an elastic drive is brought about. They are suitable for drawing out and flattening small forgings produced in large numbers. Their disadvantage is the frequent breaking of springs due to vibrations when in operations. Spring hammers are built with rams weighing from 30 to 250 kg. The number of strokes varies from 200 to 40 blows per minute.
2.1.4
Pneumatic hammer
7
The hammer has two cylinders compressor cylinder and ram cylinder. Piston of the compressor cylinder compresses air, and delivers it to the ram cylinder where it actuates the piston which is integral with ram delivering the blows to the work. The reciprocation of the compression piston is obtained from a crank drive which is powered from a motor through a reducing gear. The air distribution device between the two cylinders consists of rotary valves with ports through which air passes into the ram cylinder, below and above the piston, alternately. This drives the ram up and down respectively.
2.1.5 Hydraulic hammer In this hammers instead of air oil was used. The cost hydraulic hammer is high as compared to the pneumatic hammers. Hydraulic hammer is used in high force applications. These are noise less.
3.
PRESENT SCENARIO OF POWER HAMMER AND MECHANISMS
3.1
Power hammers Unfortunately, using presently available power hammers and formers can
subject users to a number of inherent disadvantages. Generally, presently available power hammers and formers are expensive and may cost on the order of tens of thousands of dollars putting them out of reach of all but the largest metalworking operators. Presently, available power hammers and formers tend to be bulky and occupy large footprints making them unsuitable for small-scale operations. In addition, presently available power hammers and formers can require precise, custom machined die sets, which may be unusable with other machinery, in order to provide proper operational clearance. Finally, presently available power hammers and formers can be operated by linkage drives that have the capacity to literally destroy the machines if proper die set-ups and clearances are not maintained.
8
Recent research of power hammer The present disclosure addresses a power hammer assembly providing users with the metal forming advantages associated with power machinery at a reduced expense and in a smaller footprint than presently available power hammer systems. In general, the power hammer assembly of the present invention provides threedimensional shaping capabilities, which have application in the forming of custom metal products such as, for example, customized motorcycle and automotive parts. The power hammer assembly of the present disclosure can be fabricated and assembled in a kit fashion with commonly available tools to reduce costs. Alternatively, the power hammer assembly of the present disclosure can be purchased in an assembled configuration. In one aspect, a power hammer assembly of the present disclosure provides powered forming capabilities while remaining economical with respect to performance, vibration, and footprint size and acquisition costs. In some embodiments, the power hammer assembly can comprise a power assembly for providing a single stroke speed and/or a single set stroke with respect to the striking of die assemblies against a piece of metal. In some embodiments, the power hammer assembly of the present invention can comprise a larger throat area and/or a larger die gap than presently available power hammers to facilitate ease of use. In some embodiments, the power hammer assembly of the present invention can comprise adjustment features allowing for the use of die sets of varying configurations such as, for example, shank size, shank length or alternatively, die sets fabricated for use with other machinery. In some embodiments, the power hammer assembly of the present invention can comprise a belt transmission assembly designed to slip in the event of die interference during set-up or operation so as to avoid damaging the power hammer assembly. In some embodiments the power hammer assembly of the present invention includes fine adjustment means for spacing between the upper and lower die. 3.2
Mechanism
Four bar parallel linkage mechanism for toe movement
9
In recent research the four bar linkage mechanism is used for the humanoid robots for the free movement of their toe. Using this mechanism the major part of the force acts on the non-movable portion of this link rather then on the toe tip. Because of this it is possible to decrease the constraint on the joint. At the same time the following multiple roles of the toe are expected. One it to generate a large kicking force at the toe pad and another is to maintain multiple contact with the floor by the toe joint control.
4.
SIX BAR SLIDER CRANK POWER HAMMER MECHANISM
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4.1
Construction As shown in above diagram it consists of 5 links, and one fixed link. The five
links are crank (link 1), link 3. Connecting rod (link 4), Crank (link 5) and Ram die (link 2).Column can be considered as a fixed link. The link 1 rotates about a turning pair F, it is rotated by a pin joint axis, the link 3 and link 1 is connected by a turning pair E. The connecting rod (link 4) and link 3 are connected by a turning pair D. The crank (link 5) is fixed at a turning pair A and oscillates about the pin joint axis. Crank (link 5) and connecting rod (link 4) are connected by a turning pair B. Ram Die (link 2) and connecting rod (link 4) are connected by a sliding pair C. Ram Die and composite bush are connected by a sliding pair G. Crank (link1) is joined at turning pair F to the column and also crank (link 5) is joined at turning pair A. Column is welded to the base, vice (not shown in above fig) is fitted to the column for holding the work piece. All the links, Column, Base and Vice are made up of Mild Steel, they are rigid enough to absorb the vibrations and shocks produced during work. Composite bush is made up of two materials outer one is of Mild Steel and the liner is made up of Gun Metal to prevent from wear, tear and corrosion resistance. A handle is provided at point E, with the help of the handle the crank (link 1) is rotated.
4.2
Working Principle The Crank (link 1) rotates at a fixed axis at F it is joined to link 3. As the link
1 is rotated the motion is transmitted to the link 3 which is connected at point E. The motion is further transmitted to the connecting rod which is joined with the link 3 at D. Finally the connecting rod transmits the motion to the Ram Die (link 2) which reciprocates at a fixed path G. The Connecting rod (link 4) and Ram Die (link 2) are connected at C, Where a slot is provided for getting a straight line motion of the ram Die. The crank (link 5) is provided for oscillating the connecting rod at a fixed path.
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4.3
Manufacturing Process
4.3.1 Cranks (link 1 and 5) A mild steel material of the required dimension is cut on the power hack saw machine. After cutting process is over the fillet is provided over the edges by using a hand grinder. After a drill of diameter 6 mm is made. Finally the filing was done on the bench vice.
4.3.2 Connecting Rod A mild steel material of the required dimension is cut on the power hack saw machine. After cutting process is over the fillet is provided over the edges by using a hand grinder, after providing fillets drilling operation of required diameter is done after completing this process now we proceed towards milling the slot of 65 x 8 x 6 mm3 by using an end mill cutter. Finally filing was done on bench vice to remove unnecessary sharp corners.
4.3.3 Ram die Mild steel material of required dimension is cut on power hack saw. The material was fixed on the chuck in a lathe machine for doing facing and turning operations. Polishing was done for good surface finish. Chamfers were made for removing sharp corners. A hole was drilled at the end of the ram of the required size for fixing the slider pin. A slot was milled on the rod to insert the connecting rod in the slot and fixing it in the slider pin. At the other end of the ram a hole of required size was made and then later it was taped at the same end to make the fixing adjustment of the punch with the help of a screw.
4.3.4 Composite Bush
12
It was manufactured by two different materials one of Mild steel and other was liner made up of Gun metal. The outer one is made up of Mild steel on which facing and turning operations were done on a lathe and then the inner one was made up of Gun metal on which facing and turning were carried out of the required size then the liner was inserted in the outer bush by the application of a press fit.
4.3.5 Column The Column is made up of Mild Steel of required dimension. First the marking for the holes to fix the links were done on the column. The outer profile was marked and then made to cut on a gas cutter, and then it was milled to the required size and then finally chamfering was done to remove unnecessary sharp corners and edges. Drills were drilled on the column for bearings, turning pairs F and A. Then the composite bush was welded on the column. Vice was fitted on the column by the application of welded joints for holding the work piece.
4.4
Determination of Degrees of Freedom The formula for finding the degree of freedom from the Kutzbach equation is
given below n = 3( -1)-2j-h Where, n = Degree of freedom = no of links
j = no of lower pairs h = no of higher pairs Links: a)
Fixed link
b)
Crank (link 1)
c)
Crank (link 5)
d)
Link 3
13
e)
Connecting Rod
f)
Ram Die
Therefore, number of links = 6 Lower pairs: a)
Turning pair F
b)
Turning pair E
c)
Turning pair D
d)
Turning pair A
e)
Turning pair B
f)
Sliding pair C
g)
Sliding pair G
Therefore, number of lower pairs = 7 Number of higher pairs = 0 Therefore,
n = 3( -1)-2j-h h=o n = 3( -1) -2j n = 3(6-1) -2 x 7 n=3x5–2x7 n = 15 – 14 n=1
Therefore, the mechanism has single degree of freedom.
4.5
Applications
4.5.1 Forging Forging refers as the process of plastically deforming metals or alloys to a specific shape by a compressive force exerted by some external agency like hammer, Press, rolls, or by an upsetting machine of some kind. The portion of a work in which forging is done is termed the forge and the work is mainly performed by means of
14
heavy hammers, forging machines, and presses. Forging processes are among the most important manufacturing techniques since forging is used in small tools, railroad equipment, automobile, and aviation industries. A number of operations are used to change the shape of the raw material to the finished form. The typical forging operations are: 1.
Upsetting.
2.
Fullering.
3.
Drawing down.
4.
Setting down.
5.
Punching.
6.
Bending.
7.
Welding.
8.
Cutting.
All these operations are carried out with the metal in a heated condition, which must be maintained by taking a ‘fresh’ heat when the work shows sign of getting cold. Forging Processes The processes of reducing a metal billet between flat-dies or in a closedimpression die to obtain a part of predetermined size and shape are called smith forging and impression-die forging respectively. Depending on the equipments utilized they are further sub-divided as hand forging, hammer forging, press forging, drop forging, mechanical press forging, upset or machine forging. In general, the methods of forging may be classified as follows:
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FORGING PROCESS IMPRESSION DIE
SMITH
Hand
Drop
Power
Press
Machine
Hammer
Press
4.5.2 Press Press working involves production of final component from sheet metal in cold condition. The machine which is used to apply the required pressure of force in a short duration is called press. The press consists of a frame, supporting bed and ram. The ram is equipped with special punches and moves towards and into the die block which is attached to a rigid body. The punch and die block assemble are generally referred to as a die set or simply die. A disadvantage of press working is that the operations are carried out at room temperature and the metal is less deformable of strain hardening. Classification of Presses Presses are classified in various ways as listed below. (i)
Mechanical press.
(ii) Hydraulic press.
16
Press Tool Operations A large number of operations can be performed by using press tools, and all press tool operations can be broadly classified into two types. 1. Cutting operations. (i)
Blanking,
(ii)
Piercing
(iii)
Lancing,
(iv)
Cutting off and Parting,
(v)
Notching,
(vi)
Shaving, and
(vii)
Trimming.
2. Shaping operations (i)
Forming (embossing, Beading and Cutting, Bulging etc.),
(ii)
Drawing, and
(iii)
Bending. II.
1.
DESIGN CALCULATIONS
Determination of length of the links For evaluating the length of the links we made prototype, Length of the links
is proportionally taken according to the diagram of the Six bar Slider crank Power hammer mechanism. By checking the movability after more and more trails of link lengths we finalized the dimensions as shown below 1.
crank (link 1)
=
120mm
2.
Ram die link2
=
420mm
3.
link3
=
440mm
4.
connecting rod(link4) =
655mm
17
5.
2.
crank (link 5)
=
120mm
Design calculation for finding the width and thickness of the
links This mechanism is designed for applying a compressive force of 0.6 tonnes for forging or press operation.
Minimum cross sectional area required to transmit is 0.6 tonnes load (A): load permisible shear stress
=
p [σ]
mm 2
taking M.S for link design yield sress (σ y )
= 300 N / mm 2
adopting factor of safety
=
permisible
shear stress [σ]
4
= 300/4 p = [σ ]
minimum area required ∴Effective area (A)
= 80mm
= 75 N/mm =
2
6000/75
2
The formula for the minimum effective area is obtained as bt – (dt) it can be observed in the link as in the fig2.1
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Fig 2.1 In fig 2.1 hatched portions indicates minimum effective cross sectional area in the entire mechanism. We know that stress is inversely proportional to the area, so the minimum area leads to increase the stress. So it is always preferred to design any machine by taking minimum cross sectional area as effective area. Effective
area (A)
=
bt - (d × t) mm
b
=
d
= thickness of the link in mm = diameter of pin hole in mm
2
where, t ∴Effective
breadth of the link in mm
area (A) = 80mm
For safe design bt - (d ×t) ≥80 mm 2
19
2
From the design of bolt we obtained diameter of pin as 6mm, by keeping the diameter of pin constant and by trail and error method we obtained the breadth and thickness of the link as 20mm and 6mm respectively.
3.
Design calculation for bolt diameter
3.1
Calculation of Stress Concentration
Stress concentration factor is given by, Kt =
Maximum stress Nominal stress
Nominal stress is given by, σ nom =
p (w - a)h
The below diagram is for the finite width plate with a transverse hole.
We know that width of the plate W = 20mm Thickness of the plate h = 6mm Nominal stress is given by, σ nom =
p (w - a)h
Where,
20
P = tensile force = 0.6 tonne = 0.6 × 1000 × 9.81 = 5886N Therefore, σ nom =
5886 (20 - a)6
Kt =
σ max σ nom
σ nom =
σ max kt
5886 150 = ( 20 −a)6 2. 3 5886 = 65.22 (120 − 6a)
5886 = 65.22(120-6a) 5886 = 7826.5 – 391.32a 5886 – 7826.5 = - 391.32a - 1940.5 = - 391.32a Therefore
a=
1940 .5 391 .32
a = d (diameter) = 4.99mm Due to dynamic characteristics of links the diameter of pin is selected as 6 mm.
3.2
Calculation for bearing stress.
For M.S material
σy =
300 N/ mm 2
Factor of safety = 2 Permissible bearing of crushing stress = ( σ b ) =
21
σy n
= 300/2 = 150N/ mm 2 Bearing stress ( σ b ) ≥
p d +n
P = 0.6 + 1000 × 9.81N d = 6mm t = 6mm n=2 (σb )
≥
0.6 ×1000 ×9.81 6 ×6 ×2
≥ 81.75 N/ mm 2 The bearing stress is greater than 81.75 N/ mm 2 , so the design is satisfactory.
4
Design for punching operation
Permissible shear stress is given by, τ y = 0.6σy
= 0.6
× 300
= 180 N/ mm 2 τy ≥
load shear area
τy ≥
6000 shear area
Shear area for punching operation can be observed from above diagram is π dt Where,
d = diameter of blanking or piercing hole in mm. t = the thickness of the blank in mm.
22
Shear area = π dt =
6000 180
π dt = 33.3 mm 2 Therefore
t=
33 .3 π ×7
t = 1.5mm
.III OPERATION SHEETS 1.
CRANK (LINK 1)
23
Description
: Crank 1
Part No
:1
Material
: Mild Steel.
Required size
: 120mm x 20mm x 6mm
SL. NO
MACHINE
OPERATION
TOOL
GAUGE
Vernier 1
Power saw
Cutting
Hacksaw
caliper, steel rule
Grinding
2
Grinding
Fillet
3
Drilling
Drill φ 6 x 6
Drill bit
4
Drilling
Drill φ 6 x 6
Drill bit
5
Bench vice
Filing
Flat file
2. Description
: Die
Part No
:2
wheel
RAM DIE
24
Vernier caliper Vernier caliper
Material
: Mild Steel.
Required size
: φ 20mm x 420mm
SL. NO
MACHINE
OPERATION
1
Power saw
Cutting
2
Lathe
Facing
3
Lathe
4
Drilling
5
Drilling
6
Tapping
7
Milling
TOOL Hacksaw
Vernier caliper,
blade
steel rule
Single point cutting tool
Drilling φ10x2
GAUGE
Vernier caliper
Drill φ 20
Vernier caliper
Drill φ 4.5 x 5
Drill φ 4.5
Vernier caliper
Drill φ 6 x 6
Drill φ 6
Vernier caliper
5
M6 internal thread
End mill
Slot
3. Description
: LINK 3
Part No
:3
Tap
cutter
LINK 3
25
Vernier caliper
Material
: Mild Steel.
Required size
: 440mm x 20mm x 6mm
SL. NO
MACHINE
OPERATION
TOOL
GAUGE
Vernier 1
Power saw
Cutting
Hacksaw
caliper, steel rule
Grinding
2
Grinding
Fillet
3
Drilling
Drill φ 6 x 6
Drill bit
4
Drilling
Drill φ 6 x 6
Drill bit
5
Bench vice
Filing
Flat file
4.
wheel
CONNECTING ROD
Description
: Connecting Rod
Part No
:4
Material
: Mild Steel.
Required size
: 655mm x 20mm x 6mm
26
Vernier caliper Vernier caliper
SL. NO
MACHINE
OPERATION
TOOL
GAUGE
Vernier 1
Power saw
Cutting
Hacksaw
caliper, steel rule
Grinding
2
Grinding
Fillet
3
Drilling
Drill φ 6 x 6
Drill bit
4
Drilling
Drill φ 6 x 6
Drill bit
5
Milling
Slot
End mill cutter
6
Bench vice
Filing
Flat file
5.
wheel
CRANK (LINK 5)
Description
: Crank (link 5)
Part No
:5
Material
: Mild Steel.
27
Vernier caliper Vernier caliper
Vernier caliper
Required size
SL. NO
: 120mm x 20mm x 6mm
MACHINE
OPERATION
TOOL
GAUGE
Vernier 1
Power saw
Cutting
Hacksaw
caliper, steel rule
Grinding
2
Grinding
Fillet
3
Drilling
Drill φ 6 x 6
Drill bit
4
Drilling
Drill φ 6 x 6
Drill bit
5
Bench vice
Filing
Flat file
6.
wheel
COMPOSITE BUSH
Description
: composite bush
Part No
:6
28
Vernier caliper Vernier caliper
Bush.
6.1
Material
: Mild steel
Required size
: φ 38mmx 100mm
SL. NO 1
6.2
MACHINE Power saw
OPERATION Cutting
TOOL Hacksaw
caliper,
Single point
steel rule Vernier
2
Lathe
Facing
3
Lathe
Drill φ 25
Drill bit
4
Lathe
Reaming
Reamer
cutting tool
Liner
Material
: Gun metal
Required size
: φ 25mm x 105mm
29
GAUGE Vernier
caliper Vernier caliper Vernier caliper
SL. NO 1
MACHINE Power saw
OPERATION Cutting
2
Lathe
Facing
3 4
Lathe Lathe
Drill φ 25 Reaming
5
Lathe
Step turning
7.
COST ESTIMATION
7.1
Cost of Standard components
TOOL
GAUGE Vernier
Hacksaw
caliper,
Single point
steel rule Vernier
cutting tool Drill bit Reamer Single point
caliper Micrometer Micrometer Vernier
cutting tool
caliper
Name of component
Quantity
Cost/piece
Cost in Rupees
Bearing (6mm) M6 bolt and nut
4 5
15 8
60 40
30
½ inch bolt and nut M5 Countersunk bolt and nut M6 Countersunk bolt and nut
1
26
26
8
1.5
12
2
3
6
TOTAL COST
7.2
144
Material Cost
Name of component
Quantity
Cost in Rupees
M.S Flat for links
1
150
M.S Rod for ram
1
100
M.S sheet for base
1
2000
Bush (M.S and gunmetal)
1
156
TOTAL COST
7.3
2406
Machining Cost Machine Lathe Drilling Gas Cutting Welding Milling Total Cost
Cost in Rupees 500 300 170 200 660 1830
31
7.4
Total Cost of Six bar Slider Crank Power Hammer Mechanism
Particulars Transportation and Allowances Painting and Name Plate Cost of Standard Components Material Cost Machining Cost Total Cost
Cost in Rupees 1220 800 144 2406 1830 6400
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PART AND ASSEMBLY DRAWINGS
33
