Portable, internal combustion-engined tool and method of driving its piston

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a portable, internal combustion-engined tool, in particular, to a setting tool for driving fastening elements in different objects, and to a method of driving the piston of such a tool.

2. Description of the Prior Act

A tool of the above-described type and a method of driving its piston is disclosed DE 40 32 202 A1. The known tool has a combustion chamber which is separated in two chamber sections arranged one after another with a separation plate having a plurality of through-openings. Upon expansion of the chamber section, air-fuel gas mixture is aspirated therein. The air-fuel gas mixtures in the chamber sections may have, respectively, different air/fuel gas rations. The combustion of the air-fuel gas mixture is started in a first, remote from the piston, chamber section with an electrical spark, and a flame front starts to spread, in this chamber section, from the center out with a relatively slow velocity. The flame front pushes the non-combusted air-fuel gas mixture away from itself, and the non-combusted air-fuel gas mixture penetrates through the openings in the separation plate into adjacent chamber section, causing there turbulence and precompression of the air-fuel gas mixture that fills this chamber section. When the flame front reaches the through-openings of the separation plate, the flame, due to the relatively narrow cross-section of the openings, penetrate into the adjacent, main chamber section in form of flame jets, creating their further turbulence. The mixed, turbulent air-fuel gas mixture in the another, main chamber section is then ignited over the entire surface of the flame jets, and burns with a very high speed. This results in a sharp increase in the effectiveness of combustion in the main chamber section, as cooling losses remain small.

After the fastening element has been driven in, and the air-fuel gas mixture in the main chamber section, which adjoining the piston, has burnt, the piston can be brought into its initial position again as a result of underpressure behind the piston which results from cooling down of the exhaust gas or the flue gas which remains in the combustion chamber and in the expansion volume of the guide cylinder. Thereafter, the exhaust gas is vented out of the combustion chamber, and a new portion of the air-fuel gas mixture is aspirated into the combustion chamber upon next expansion of the chamber sections. The air-fuel gas mixture is fed into the chamber sections having different sizes and is fed from one chamber section into another.

In conventional tools, the fuel gas in a liquid form is fed through a conduit into a pre-evaporation chamber and is mixed their with air in accordance with a desired mixture ratio. Then, the air-fuel gas mixture is fed from the pre-evaporation chamber through a conduit into the tool combustion chamber at the beginning of the setting process, i.e., upon pressing the tool against an object. The air-fuel gas mixture is fed into the combustion chamber as a result of a suction effect produced by the expansion of the combustion chamber sections. As the pre-evaporation chamber is exposed to the surrounding temperature and pressure, different air-fuel gas mixtures can be formed in the pre-evaporation chamber dependent on the parameters of the temperature and pressure. Accordingly, it is not always insured that air-fuel gas mixture fed into the combustion chamber has a desired mixture ratio. It can occur that the air-fuel gas mixture in the chamber section, which contains the ignition device, is too lean, which reduces the possibility of ignition of the mixture and thereby, the operational reliability of the tool. A too lean air-fuel gas mixture in the main chamber can lead to a reduced effectiveness.

On the other hand, with conventional tools, in particular, at low temperatures and a rapidly repeated setting process, there exists a danger that the fuel gas, which is fed into the pre-evaporation chamber in a liquid form, cannot be adequately evaporated. This results in building of ice in the gas conduit leading to the pre-evaporation chamber, and it cannot be excluded that fuel gas will remain in the pre-evaporation chamber. This again would result in a lean mixture ratio of the air-fuel gas mixture and would result in problems discussed above. Further, at the next setting process, the fluid flue gas, which accumulates in the pre-evaporation chamber, can evaporate, and as a result, taking into account the newly fed amount of the fuel gas, a too rich mixture ratio would be obtained, which can lead to fluctuation of the operational characteristics of the tools.

Accordingly, an object of the present invention is to provide a tool and a method of driving its piston which would insure a higher operational reliability of the tool and its better operational efficiency.

SUMMARY OF THE INVENTION

This and other objects of the present invention, which will become apparent hereinafter, are achieved by providing, a tool a combustion chamber of which is separated by a separation plate having through-openings into at least two, arranged one after another, chamber sections having each at least one separate inlet, and by providing a method according to which separately adjusted combustible gas mixtures are fed into the chamber sections through their respective inlets. As discussed, according to the inventive method, the combustible gas mixture is separately adjusted in each chamber section. This permits to obtain optimal mixture ratios of the combustible gas mixture in each chamber section. As a result, a reliable course of the setting process is insured, together with high efficiency of the tool. The combustible mixture can be formed, e.g., as a mixture of air and fuel gas, as a mixture of oxygen and fuel gas, or as any other suitable mixture.

Because of the separate adjustment of the combustible mixture in each chamber section, the mixture ratio of the air-fuel gas mixture fed into the chamber section containing the ignition device, can be adjusted so that a fatter mixture is fed into this chamber section than into the remaining chamber-sections, which insured that with each actuation of the ignition device, an ignition of the mixture in the ignition device-containing chamber section takes place. On the other hand, the air-fuel gas mixture in the main chamber section, which is adjacent to the piston can be made leaner or stoichiometric, independently of the mixture ratio in the fore-chamber section, whereby a constant, high-efficient combustion takes place in the main chamber section.

The adjustment of the air-fuel gas mixture in each chamber section is effected by commonly feeding air in all of the chamber sections and feeding a respective amount of fuel gas separately into each chamber section. With this adjustment, the number of valves, which control the feeding of media in all of the chamber sections, is reduced. In addition, because metering of only the fuel gas is required, the number of adjustment parameters is likewise reduced, which simplifies the metering process.

Advantageously, the supply of air in the chamber sections is effected by suction of the air as a result of expansion of the chamber sections. Thus, no separate air-supply devices are needed. Upon expansion of the chamber sections, the combustion chamber wall and the separation plate move away from the piston, and the air streams in the chamber section in the same direction the combustion chamber wall and the separation plate move or in opposite direction.

Preferably, the fuel gas is fed into the chamber sections in a liquid form. Thus, the fuel gas evaporates only in the chamber section. This is a significant advantage because the adjustment of the mixture ratio of the air-fuel gas mixture to a predetermined or desired value is insured even if an ice accumulation in the region of the valve takes places as a result of low environmental temperatures or of high repetition speed of the setting process. This is because the liquefied fuel gas, which was fed in a respective chamber section, has sufficient time to evaporate before the start of the ignition process.

Preferably, the amount of the fed fuel gas or the liquefied fuel gas is determined by a preliminary metering of the same. Thereby, a predetermined ratio is obtained. Temperature and pressure variations of the environment practically do not affect the metered amount of the liquefied fuel gas.

Preferably, the fuel gas is fed into respective chamber sections shortly before their complete expansion. The ignition process is initiated only after the complete expansion of the chamber sections. Thus, the time period between the time the fuel gas is delivered into the chamber sections and the time of the start of the ignition process is used for evaporation of the liquefied fuel gas.

An inventive, portable, internal combustion-engined tool, in particular a setting tool for driving in fastening elements, and having a combustion chamber divided in several chamber sections, which are arranged one after another, by at least one separation plate provided with a plurality of through-openings and in which a combustible gas mixture is combusted for driving a piston, is characterized in that each chamber section has at least one separate inlet for admitting a fuel gas. Thereby, as discussed above, a separate adjustment of the combustible gas mixture in each chamber section become possible.

Basically, each chamber section can have as many separate inlets as the number of separate gas components fed into the chamber section in order to obtain a desired mixture ratio. However, only one inlet can be provided for a chamber section for metering a single gas component when one or several other gas components are fed through one or several inlets common for all of the chamber sections.

According to the present invention, at least one separation plate is provided between the piston and the opposite combustion chamber wall. The plate and the movable chamber wall move transverse to their planes in opposite direction and, in the initial position of the piston, lie approximately on each other or on the piston.

This arrangement insures that after the return movement of the piston in its initial position, the combustion chamber can be freed of waste gases by displacing the separation plate and the movable combustion chamber wall toward the piston which displacement expels the waste gases from the space between the separation plate and the movable combustion chamber wall.

According to a further embodiment of the present invention, an aeration/deaeration valve is provided in a wall region of the combustion chamber on which the separation plate lies when it is adjacent to the piston. This valve can be used for evacuation of the waste gases from the combustion chamber on which the separation plate lies when it is adjacent to the piston. This valve can be used for evacuation of the waste gases from the combustion chamber when the combustion chamber collapses and for aeration of the combustion chamber during the movement of the movable combustion chamber wall and the separation plate away from the piston. Thus, a single valve is used for aeration and deaeration of the combustion chamber which simplifies the construction of the tool.

According to an alternative embodiment of the present invention, a deaeration valve is provided in a wall region of the combustion chamber on which the separation plate lies when it is adjacent to the piston, and an aeration valve is provided in the movable combustion chamber wall. When the movable combustion chamber wall moves away from the piston, the aeration valve opens, admitting air into the chamber sections. At this point in time, the deaeration valve is completely closed. Because both valves are located on opposite sides of the combustion chamber, there is no danger during rapidly repeating setting processes that upon the displacement of the movable combustion chamber wall away from the piston, the residual or waste gases in the deaeration valve would again penetrate into the combustion chamber through the aeration valve. The provision of the two valves also insures a more precise adjustment of the mixture ratios in the combustion chamber sections.

In order to be able to completely expand the chamber sections for admitting air therein, according to a further embodiment of the present invention, the movable combustion chamber wall, upon displacement away from the piston, engages a lug associated with the separation plate whereby the separation plate is likewise displaced by the drive mechanism. Thus, then the movable combustion chamber wall is displaced away from the piston, after a certain time period, it entrains the separation plate with it which leads to expansion of both chamber sections.

The drive mechanism for displacing the combustion chamber wall and the separation plate can include at least one rod-shaped actuation member fixedly connected with the movable combustion chamber wall and extending through the separation plate and from the combustion chamber toward the front end of the tool. A plurality of actuation members can be provided, evenly distributed over the circumference of the movable combustion chamber wall, with all of the actuation members being connected with each other by an actuation ring.

When a front-side pressing sleeve of the tool is pressed against an object and is displaced rearwardly, it actuates the actuation ring which result in displacement of the movable combustion chamber wall away from the piston which, in turn, entails aeration of the chamber section. The aeration/deaeration or only deaeration valve can be located in the region of the actuation ring and be actuated thereby, so that in the course of movement of the movable combustion chamber wall, a control of the valve takes place. This significantly simplifies the construction of the tool.

In order to be able to feed a liquefied fuel gas into the chamber sections, the inlets can be provided with different nozzles connected with a common metering valve. This permits to inject different amount of the fuel gas into the chamber sections which leads to different mixture ratios of the air-fuel gas mixtures in different chamber sections.

Alternatively, the inlets can be connected with different metering valves to achieve the same object. In this case, additional nozzles can be used for injecting the liquefied fuel gas in form of a mist, which accelerates the fuel gas evaporation.

According to a still further embodiment of the present invention, the metering valves are controlled in accordance with a position of the movable combustion chamber wall or the actuation ring. This insured, with single means, that he liquefied fuel gas has sufficient-time to evaporate before the combustion chamber reaches its end position.

The novel features of the present invention, which are considered as characteristic for the invention, are set forth in the appended claims. The invention itself, however, both as to its construction and its mode of operation, together with additional advantages and objects thereof, will be best understood from the following detailed description of preferred embodiments, when read with reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS:

The drawings show:

FIG. 1

an axial cross-sectional view of an internal combustion-engined tool with a collapsed combustion chamber;

FIG. 2

an axial cross-sectional view of the tool shown in

FIG. 1

with an expanded combustion chamber;

FIG. 3

an axial cross-sectional view of the tool shown in

FIG. 1

with an expanded combustion chamber with a modified actuation mechanism for delivery of fuel gas;

FIG. 4

an axial cross-sectional view of the tool shown in

FIG. 1

with a partially expanded combustion chamber and a modified aeration device;

FIG. 5

a side view of an ignition device of the combustion chamber shown in

FIGS. 1 through 4

;

FIG. 6

a cross-sectional view along line A—A in

FIG. 5

;

FIG. 7

a cross-sectional view along line A—A in

FIG. 5

at ignition;

FIG. 8

a plan view of a separation plate of the combustion chamber at ignition;

FIG. 9

a plan view of another embodiment of a separation plate of the combustion chamber;

FIG. 10

an axial cross-sectional view of the tool in the region of the combustion chamber provided with a separation plate shown in

FIG. 9

; and

FIG. 11

a longitudinal view of a tool in the region of the combustion chamber with the combustion chamber being closed.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

FIG. 1

shows a cross-sectional view of an internal combustion engined-setting tool for setting fastening elements in the region of the tool combustion chamber. As shown in

FIG. 1

, the setting tool has a cylindrical combustion chamber

1

with a cylindrical wall

2

and an annular bottom

3

with a central opening

4

. A guide cylinder

5

, which has a cylindrical wall

6

and a bottom

7

, adjoins the opening

4

in the bottom

3

of the combustion chamber

1

. A piston

8

is displaceably arranged in the guide cylinder

5

. The piston

8

consists of a piston plate

9

facing the combustion chamber

1

and a piston rod

10

extending from the center of the piston plate

9

. The piston rod

10

projects through an opening

11

formed in the bottom

7

of the guide cylinder

5

.

FIG. 1

shows a non-operational position of the setting tool in which the piston

8

is in its rearward off-position. The side of the piston plate

9

adjacent to the bottom

3

of the combustion chamber

1

is located closely adjacent to the bottom

3

, with the piston rod

10

projecting only slightly beyond the bottom

7

of the guide cylinder

5

. For sealing the cylinder chambers on opposite sides of the piston plate

9

from each other, sealing rings

12

,

13

are provided on the outer circumference of the piston plate

9

.

Inside of the combustion chamber

1

, there is provided a cylindrical plate

14

further to be called a movable combustion chamber wall or movable wall. The movable wall

14

is displaceable in the longitudinal direction of the combustion chamber

1

. For separating the chambers on opposite sides of the movable wall

14

, an annular sealing

15

is provided on the circumference of the movable wall

14

. The movable wall

14

has a central opening

16

, with an annular sealing

17

provided in the wall of the opening

16

.

Between the movable wall

14

and the annular bottom

3

of the combustion chamber

1

, there is provided a separation plate

18

. The separation plate

18

has a circular shape and an outer diameter corresponding to the inner diameter of the combustion chamber. The side of the separation plate

18

adjacent to the movable wall

14

is provided with a cylindrical lug

19

that projects through the central opening

16

in the movable wall

14

. The length of the lug

19

exceeds the thickness of the movable wall

14

in several times. The circumferential or annular sealing

17

sealingly engages the outer circumference of the cylindrical lug

19

. At its free end, the cylindrical lug

19

is provided with a shoulder

20

the outer diameter of which exceeds the outer diameter of the lug

19

and the inner diameter of the opening

16

of the movable wall

14

. Thus, upon moving away from the bottom

3

of the combustion chamber

1

, the movable wall

14

, in a while, engages the shoulder

20

of the lug

19

and lifts the separation plate

18

with it. Thus, the movable wall

14

and the separation plate

15

become spaced a predetermined distance which is determined by the position of the shoulder

20

. In this way, the movable wall

14

and the separation plate

18

form a so called fore-chamber, which forms a first combustion chamber section of the combustion chamber

1

. The fore-chamber section is designated with a reference numeral

21

and is clearly shown in FIG.

2

. After the movable wall

14

engages the shoulder

20

, the movable wall

14

and the separation plate

18

are displaced together, and a further second combustion chamber section is formed between the separation plate

18

and the bottom

3

and/or the piston plate

9

. This second chamber section forms a main chamber. It is designated with a reference numeral

22

and is likewise clearly shown in FIG.

2

.

For displacing the movable wall

14

, there are provided several, e.g., three actuation or drive rods

23

uniformly distributed along the circumference of the movable wall

14

and fixedly connected therewith. Only one of the drive rods

23

is shown in FIG.

1

. The drive rods

23

extend parallel to the axis of the combustion chamber

1

and outside of the cylindrical wall

6

of the guide cylinder

5

. The drive rods

23

extend through openings

24

, respectively, formed in the separation plate

18

and through corresponding openings

25

formed in the bottom

3

of the combustion chamber

1

. Each of the openings

25

is provided with a circumferential seal

26

located in the surface defining the opening

25

for sealing the combustion chamber

1

from outside. The movable wall

14

is connected with drive rods

23

by, e.g., screws

27

which extend through the movable wall

14

and are screwed into the drive rods

23

. The free ends of the drive rods

23

are connected with each other by an actuation or drive ring

28

which is arranged concentrically with the combustion chamber axis and which circumscribes the guide cylinder

5

. The drive ring

28

is connected with the drive rods

23

by screws

29

which extend through the drive ring

28

and are screwed into the drive rods

23

through end surfaces of the free ends of respective drive rods

23

. Each of the drive rods

23

supports a compression spring

30

extending between the bottom

3

of the combustion chamber

1

and the drive ring

28

. The compression springs

30

are designed for pulling the movable wall

14

toward the bottom

3

.

In the region of the bottom of the combustion chamber, there is further provided a ventilation opening

31

into which a valve tappet

32

is sealingly extendable. With the ventilation opening

31

being open, the valve tappet

32

is located outside of the combustion chamber

1

or beneath the bottom

3

of the combustion chamber

1

. The valve tappet

32

is supported outside of the combustion chamber

1

by a shoulder

33

secured on the guide cylinder

5

. The shoulder

33

has an opening

34

through which a stub

35

, which is secured to the bottom side of the valve tappet

32

, extends. At the free end of the stub

35

, there is provided a shoulder

36

, and a compression spring

37

is arranged between the shoulder

36

and the shoulder

33

. The compression spring

37

is designed for pulling the valve tappet

32

toward the shoulder

33

to keep the ventilation opening

31

open. The cylindrical stub

35

lies in the displacement path of the drive ring

28

and is impacted by the drive ring

28

when the later is displaced toward the bottom

3

of the combustion chamber

1

. At a predetermined axial position, the drive ring

28

engages the stub

35

pushing it upward, so that the valve tappet

32

closes the ventilation opening

31

.

A plurality of further openings

38

are distributed over the circumference of the separation plate

18

at the same distance from the combustion chamber axis. In the lower end of the guide cylinder

5

, there are formed a plurality of outlet openings

39

for evacuating air from the guide cylinder

5

when the piston

8

is displaced toward the bottom

7

of the guide cylinder

5

. At the lower end of the guide cylinder

5

, there is provided damping means

40

for damping the movement of the piston

8

. When the piston

8

passes past the openings

39

, an exhaust gas can escape through the openings

39

.

Two radial, axially spaced openings

41

and

42

are formed in the cylindrical wall

2

of the combustion chamber

1

. Two outlet nipples

43

,

44

extend into the radial openings

41

,

42

, respectively, from outside. The nipples

43

,

44

form part of metering valves (not shown in detail) of a metering head

45

. A liquefied fuel gas is delivered to metering valves located in the metering head

45

from a bottle

46

. The metering valves provide for flow of a predetermined amount of the liquefied fuel gas through the outlet nipples

43

,

44

when the metering head

45

is pressed against the cylindrical wall

2

of the combustion chamber

1

, and the outlet nipples

43

,

44

are pushed inward, opening the respective metering valves. To provide for the inward movement of the outlet nipples

43

,

44

, the radial openings

41

,

42

narrow toward the interior of the combustion chamber

1

, providing stops for the outlet nipples

43

,

44

. The pressing of the metering head

45

against the cylindrical wall

2

is effected with a stirrup

47

pivotable at a hinge point

48

on the cylindrical wall

2

. One end

49

of the stirrup

47

is impacted by the movable wall

14

, and the stirrup is pivoted in such a way that its another end

50

is pressed against the metering head

45

to press the later toward the cylindrical wall

2

. The movable wall

14

engages the end

49

of the stirrup

47

shortly before the partial chamber

21

reaches its end position. The metering head

45

and the bottle

46

, once connected with each other, remain permanently connected. The system

45

/

46

can, e.g., tilt about an axle provided in the bottom region of the bottle

46

.

FIG. 2

shows the setting tool with the combustion chamber

1

in its expanded condition, i.e., with the expanded fore-chamber section

21

and main chamber section

22

. The displaced positions of the movable wall

14

and the separation plate

18

are established when the driving ring

28

impacts the shoulder

36

, closing the valve

31

/

32

. The opening

31

and the valve tappet

32

have conical circumferential surfaces narrowing in the direction of the combustion chamber

1

, so that a stop is formed. As it has been discussed previously, the distance of the separation plate

18

from the movable wall

14

is determined by the distance of the shoulder

20

from the separation plate

18

. In this position of the movable wall

14

and the separation plate

18

, the radial openings

41

,

42

lie against the fore-chamber section

21

and the main chamber section

22

, respectively.

The lug

19

forms, in its region adjacent to the separation plate

18

, an ignition cage

51

for receiving an ignition element

52

. The ignition element

52

serves for generating an electrical spark for the ignition of the air-fuel gas mixture in the fore-chamber

21

. As it will be described in more detail below, the ignition device

52

is located in the central region of the cage

51

having openings

53

formed in the cage circumference. Through this openings

53

, a laminar flame front exit from the ignition cage

51

into the fore-chamber.

Below, the operation of the setting tool, shown in

FIGS. 1-2

, will be described in detail.

FIG. 1

shows the condition of the combustion chamber

1

in the off-position of the setting tool. The combustion chamber

1

is completely collapsed, with the separation plate lying on the bottom

3

of the combustion chamber

1

and the movable wall

14

lying on the separation plate

18

. The piston

8

is in its rearward off-position so that practically no space remains between the piston

8

and the separation plate

18

if one would disregard a small clearance therebetween. The position, in which the movable wall

14

lies on the separation plate

18

, results from the compressing spring

30

biasing the drive ring

28

away from the bottom

3

, and the ring

28

pulls with it the movable wall

14

via the drive rods

23

. In this position, the drive ring

28

is spaced from the shoulder

36

of the valve tappent

32

, and the compression spring

37

keeps the valve tappet

32

outside of the opening

31

so that the opening

31

remains open. The system metering head

45

/bottle

46

is pivoted away from the wall

2

of the combustion chamber

1

, with the outlet nipples

43

,

44

being released and the metering valve (no shown) being open.

When in this condition, the setting tool is pressed with its front point against an object, the fastening element should be driven in. A mechanism, not shown, applies pressure to the drive ring

28

displacing it in the direction of the bottom

3

of the combustion chamber

1

. This takes place simultaneously with the setting tool being pressed against the object. Upon displacement of the drive ring

28

toward the bottom

3

, the movable wall

14

is lifted of the separation plate

18

and, after engaging the shoulder

20

, lifts the separation plate

18

with it. Upon engagement of the shoulder

20

by the movable wall

14

, the fore-chamber section

21

is completely expanded but does not yet occupy its operational position inside the combustion chamber

1

. During the expansion of the fore-chamber section

21

, the air can already been aspirated into the fore-chamber section

21

through the ventilation opening

31

and through one or more of openings

38

formed in the separation plate

18

and overlapping the ventilation opening

31

.

Upon the setting tool being further pressed against the object, the drive ring

28

is moved closer to the bottom

3

, and the movable wall

14

is moved further upward, lifting the separation plate

18

from the bottom

3

. As a result, the main chamber section

22

likewise expands and is aerated through the ventilation opening

31

, with the fore-chamber section

21

being aerated through all of the openings

38

.

When the movable wall

14

and the separation plate

18

, in their movement upward, move past the radial openings

41

,

42

, in principle, the injection of metered amounts of liquefied fuel gas into the fore-chamber

21

section and the main chamber section

22

can begin. The injection starts when the movable wall engages the end

49

of the stirrup

47

which pivots in a clockwise direction about the pivot point

48

, with the other stirrup end

50

pressing the metering head

45

toward the cylindrical wall

2

. Upon the metering head

45

being pressed against the cylindrical wall

2

, the outlet nipples

43

,

44

move inward, opening the respective metering valves. The liquefied gas is injected into the fore-chamber

21

and the main chamber section

22

. Thereafter, a further lifting of the movable wall

14

and the separation wall

18

is necessary to bring them into their end positions in which they are locked. The possible residual pivotal movement of the stirrup

27

is compensated by the outlet nipples

43

,

44

being moved a small distance further inward into the metering head

45

.

In the last part of the displacement of the moving wall

14

and the separation plate

18

to their end positions, the valve tappet

2

is pushed into the opening

31

, closing the same, as a result of the drive ring

28

engaging the shoulder

36

.

The positions of the movable wall

14

and the separation plate

18

in the completely expanded condition of the fore-chamber section

21

and the main chamber section

22

is shown in FIG.

2

. In these positions, the movable wall

14

and the separation plate

18

can be locked. The locking takes place upon actuation of an appropriate lever or trigger of the setting tool. Upon actuation of the trigger, the movable wall

14

and the separation plate

18

become locked. The locking of the separation plate

18

and the movable wall

14

-can be effected by locking of the drive ring

28

. Shortly after the locking of the movable wall

14

and the separation plate

18

, a ignition spark is generated by the actuation of the ignition element

52

inside the cage

51

. A mixture of air and the fuel gas, which was formed in each of the chambers sections

21

and

22

, is ignited. First, the mixture starts to burn luminary in the fore-chamber section

21

, and the flame front spreads rather slowly in a direction of the openings

38

. The unconsumable air-fuel gas mixture is displaced ahead and enters, through the openings

38

, the main section chamber

22

, creating there turbulence and precompression. When the flame front reaches the openings

38

, it enters the main chamber section

22

, due to the reduced cross-section of the openings

38

, in the form of flame jets, creating there a further turbulence. The thoroughly mixed, turbulent air-fuel gas mixture in the main chamber section

22

is ignited over the entire surface of the flame jets. It bums with a high speed which significally increases the combustion efficiency.

The combustible mixture impacts the piston

8

, which moves with a high speed toward the bottom

7

of the guide cylinder

5

, forcing the air from the guide cylinder

5

out through the openings

39

. Upon the piston plate

9

passing the openings

39

, the exhaust gas is discharged therethrough. The piston rod

10

effects setting of the fastening element. After setting or following the combustion of the air-fuel gas mixture, the piston

8

is brought to its initial position, which is shown in

FIG. 2

, as a result of thermal feedback produced by cooling of the flue gases which remain in the combustion chamber

1

and the guide cylinder

5

. As a result of cooling of the flue gases, an underpressure is created behind the piston

8

which provides for return of the piston

8

to its initial position. The combustion chamber

1

should remain sealed until the piston

8

reaches its initial position.

After return of the piston

8

to its initial position, the movable wall

14

and the separation plate

18

are unlocked. The compression springs

30

bias the drive ring

28

away from the bottom

3

of the combustion chamber

1

, and the drive ring

28

releases the valve tappet

32

, and the compression spring

39

pushes the valve tappet

32

out of the opening

31

, opening same. Upon being displaced away from the bottom

3

by the compression springs

30

, the drive ring

28

pulls the movable wall

14

with it toward the bottom

3

. Later, as the drive ring

28

moves further away from the bottom

3

, the movable wall

14

abuts the separation plate

18

, pushing it toward the bottom

3

. Upon movement of the movable wall

14

and the separation plate

18

toward the bottom

3

, the exhaust gases in the fore-chamber section

21

are pushed through the openings

38

in the separation plate

18

into the main chamber section

22

and therefrom, together with the exhaust gases formed in the main chamber section

22

, through the opening

31

outside. Finally, the separation plate

18

lies again on the bottom

3

, and the movable wall

14

lies on the separation plate

18

. The combustion chamber

1

becomes completely collapsed and free of exhaust gases. The aeration process can start again.

FIG. 3

shows, in principle, the same arrangement as

FIGS. 1-2

and, therefore, a detailed description of it is not necessary. The arrangement of

FIG. 3

differs from that of

FIGS. 1-2

in that the system metering head

45

a

/bottle

46

is not tiltable but rather the system metering value

45

b

/bottle

46

is displaceable in the longitudinal direction of the combustion chamber

1

. To this end, a driver

46

a

connects the bottle

46

with the drive ring

28

in the last portion of the displacement path of the drive ring

28

in the direction in which the displacement of the driving

28

results in the expansion of the combustion chamber

1

.

In the arrangement shown in

FIG. 3

, the metering head

45

a

is fixedly connected wit the combustion chamber

1

and has two outlet nipples

43

,

44

extending from a delivery channel

45

c

and connected with the radial openings

41

,

42

. The metering valve

45

b

is fixed by secured on the bottle

46

and is supplied with a fuel gas therefrom. When the driver

46

a

engages the bottle

46

in the last portion of the displacement path of the drive ring

28

, it lifts the bottle

46

, together with the metering value

45

b

, and the metering valve

45

b

is pushed against the metering head

45

a

and becomes open. The flue gas flows toward the radial openings

41

,

42

and is ejected therefrom in a form of a mist. To provide for different amount of the air-fuel gas mixture in the fore-chamber section

21

and the main chamber section

22

, the openings

41

,

42

can have different outlet cross-sections or be provided with corresponding nozzles.

In the embodiments shown in

FIGS. 1-3

, the valve

31

/

32

serves as an aeration/dearation valve.

The arrangement shown in

FIG. 4

is again substantially corresponds to the arrangement shown in

FIGS. 1-2

and again does not require a detailed explanation. The arrangement of

FIG. 4

differs from that of

FIGS. 1-2

in that the valve tappet

32

is permanently biased into the opening

31

by the compression spring

37

, closing the opening

31

. To this end, the compression spring

37

is supported on the cylindrical stub

35

and against the bottom side of the valve tappet

32

and the shoulder

33

secured to the guide cylinder

5

. The stub

35

extends through the opening

34

in the shoulder

33

. Thus, the valve

31

/

32

is formed as a pure dearation valve.

The aeration valve is designated with a reference numeral

54

and is located in the movable wall

14

. When upon the displacement of the movable wall

14

and the separation wall

18

, the fore-chamber section

21

and the main chamber section

22

dearation, the ventilation valve

31

/

32

remain closed, and the aeration valve

54

remains open as a result of underpressure in the chambers

21

and

22

. The air enters the chamber sections

21

,

22

through the ventilation valve

54

. Otherwise, the process remains the same as described above. The aeration valve

54

is formed as a return valve that must be kept closed in its initial position by an appropriate mechanism during the return stroke of the piston

8

. This is achieved, e.g., by providing the movable wall

14

with a boss

55

which is sealingly inserted in the opening

56

formed in a cover wall

54

of the combustion chamber

1

. Thereby, the aeration valve

54

which also functions as a return valve, is closed by the cover wall

57

when underpressure is created in the interior of the combustion chamber

1

for enabling return of the piston

8

in its initial position.

The aeration or return valve

54

remains closed when the air-fuel gas mixture in the combustion chamber

1

is ignited. The deaeration valve

31

/

32

likewise remain closed as the drive ring

28

abuts the stud

35

from beneath, preventing the movement of the valve tappet

32

out of the opening

31

. Only, after the unlocking of the drive ring

28

, the drive ring

28

can move away from the bottom

3

, pulling with it the movable wall

14

and the separation plate

18

, and the exhaust gases are vented outwardly through the value

31

/

32

which opens under the pressure of the exhaust gases.

FIG. 5

shows the structure of the ignition cage

51

. In the expanded condition of the fore-chamber section

21

, the cage

51

is located between the movable wall

14

and the separation plate

18

, as shown in FIG.

5

. The ignition cage has a cylindrical shape with a hollow space inside in which the ignition element

52

is located. In the shown embodiment of the cage, the cylindrical wall of the cage

51

has four openings

53

having a somewhat elongated shape and a longitudinal extent of which is transverse to the movable wall

14

and the separation plate

18

. Each opening

53

is defined by respective opposite surfaces

53

a

, and the width of the openings

53

, at least in their middle region, is such that adjacent wall surfaces

53

a

of adjacent openings

53

form a right angle with each other. In this way, the flame front, which spreads from the center of the ignition cage

51

parallel to the movable wall

14

and the separation plate

18

, can never strike an inner wall surface of the cage that extends transverse to the spreading direction of the flame front. The advantage of this consists in that the flame front is never reflected back to the cage center. This is also favorable for a better laminar flow outside the cage which becomes gradually restored shortly after the flame front leaves the cage

51

. The arrangement of the openings

53

and flame propagation are shown in

FIGS. 6-8

. In particular

FIG. 8

shows a plan view of the separation plate

18

and a cross-sectional view of the cage

51

taken parallel to the separation plate

18

. The flame front F becomes again laminar when it reaches the openings

38

of the separation plate

18

. As an ignition element

52

, e.g., a spark plug can be used. Another embodiment of the setting tool according to the present invention is shown in

FIGS. 9-10

. In this embodiment, the separation plate

18

has two rows of openings. The separation plate

18

has a circular shape, and the two rows are arranged concentrically with respect to the separation plate center. The inner openings

38

form the inner row

58

and have a relatively small diameter. The return flow openings

60

form the second, outer row

59

and have a diameter somewhat greater than that of openings

38

. The remaining structure is similar to that of

FIGS. 1-4

.

Provision of two rows of openings

58

and

59

accelerates ignition of the air-fuel gas mixture in the main chamber

22

and generally improves efficiency of the combustion process.

As it has already been discussed above, after the ignition of the air-fuel gas mixture in the fore-chamber section

21

, a laminar flame front F is formed. The flame front F spreads relatively slow to the circumferential edge of the fore-chamber section

21

. This flame front reaches the first row

58

of the openings

38

very quickly and provides for ignition in the main chamber section

22

. The position of the first row

58

of the opening

38

is so selected that only that volume of the air-fuel gas mixture is burned in the fore-chamber section

21

, which is necessary for forming of flame jets with a predetermined energy necessary to produce a sufficient turbulence in the main chamber section

22

when the flame jets penetrate through the openings

38

into the main chamber section

22

. The turbulent combustion in the main chamber section

22

causes a flow of a portion of the unconsumable gases from the main chamber section

22

back through the second row

59

of the openings

60

into side regions of the fore-chamber

21

. The air-fuel gas mixture in the side regions of the fore-chamber

21

burns likewise turbulently and simultaneously with the combustion process in the main chamber section

22

. This insured that the combustion in the side regions of the fore-chamber section

21

also contributes to the operation of the piston

8

.

In a particular embodiment of the present invention, the diameters of the first and second rows

58

and

59

constitute, respectively, 55% and 85% of the diameter of the separation plate

18

. The diameters of the openings

38

and the openings

60

constitute, respectively, 2.6% and 3.8% of the diameter of the separation plate

18

.

FIG. 11

shows the locking arrangement of the combustion chamber in a setting tool in which the return displacement of the piston is caused by created thermal conditions. In

FIG. 11

, the like elements are designated with the same reference numerals as in

FIGS. 1-4

.

As shown in

FIG. 11

, a contact member

61

is provided on the circumference of the drive ring

28

. The contact member

61

has a stop surface extending in the direction toward the front end of the setting tool. This stop surface is inclined, and the inclination is such that it tapers outwardly toward the front end of the setting tool. Parallel to this surface, in the path of the contact member

61

, there is located a blocking section

62

of a blocking member

63

. The blocking member

63

so pivots about a pivot axis

64

that it can pivot out of the displacement path of the contact member

61

by a spring

65

. The displacement path of the contact member

61

extends parallel to the piston rod

10

.

In

FIG. 11

, the fore-chamber section

21

and the main chamber section

22

are completely expanded and are filled with an air-fuel gas mixture. Upon actuation of the trigger, the combustion chamber

1

is locked by the arm-shaped blocking member

63

, and the combustion is initiated in the combustion chamber

1

. The forces that act on the movable wall

14

in the underpressure phase, are transmitted through the drive rods

23

to the drive ring

28

and provide for displacement of the drive ring

28

in the direction of arrow P. The angle between the surface of the contact member

61

and the blocking section

62

of the blocking member

63

is so selected that the locking force acting on the drive ring

28

is directly proportional to the force acting on the movable wall

14

or the drive rods

23

as a result of underpressure, i.e., the greater is the force acting on the movable wall

14

the greater is the locking force applied to or acting on the drive ring

28

. Only when the underpressure tapers off, i.e., when the piston

8

occupies its rearward initial position, the blocking section

62

can be disengaged from the contact member

61

by the restoring spring

65

. Only then, the compression spring

30

provides for collapsing of the combustion chamber

1

and opening of the ventilation value

31

/

32

, as shown in

FIGS. 1 and 4

. In the example discussed above, a pressure-controlled unlocking of the combustion chamber

1

takes place because the displacement path of the contact member

61

becomes free only after the drop of underpressure in the combustion chamber

1

. Therefore, no additional pulling means is necessary for delaying collapse of the combustion chamber

1

and/or opening of an inlet/outlet valve until the piston returns to its initial position. The time of the collapse of the combustion chamber is self-controlled, i.e., the collapse takes place always only then when the underpressure in the combustion chamber

1

become balanced, and independently of tool temperature. The piston itself always completely returns to its rearward, initial position.

Though the present invention was shown and described with references to the preferred embodiments, such are embodiments, such are merely illustrative of the present invention and are not to be construed as a limitation thereof and various modifications of the present invention will be apparent to those skilled in the art. It is therefore not intended that the present invention be limited to the disclosed embodiments or details thereof, and the present invention includes all variations and/or alternative embodiments within the spirit and scope of the present invention as defined b the appended claims.

Number	Name	Date	Kind
1936229	Easthope et al.	Nov 1933	A
3983858	Sevald	Oct 1976	A
4284055	Wakeman	Aug 1981	A
5465702	Ferrenberg	Nov 1995	A
5540191	Clarke	Jul 1996	A
5632255	Ferrenberg	May 1997	A
6019072	Phillips et al.	Feb 2000	A
6199520	Warren	Mar 2001	B1
6209511	Goto et al.	Apr 2001	B1
6260519	Phillips	Jul 2001	B1

Portable, internal combustion-engined tool and method of driving its piston

Information

Patent Number

Date Filed

Date Issued

Inventors

Original Assignees

Examiners

Agents

CPC

US Classifications

Field of Search

US

International Classifications

Abstract

Description

Claims

Priority Claims (1)

US Referenced Citations (10)