Information
-
Patent Grant
-
6655570
-
Patent Number
6,655,570
-
Date Filed
Friday, May 4, 200123 years ago
-
Date Issued
Tuesday, December 2, 200320 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
- Soltis; Lisa M.
- Croll; Mark W.
- Breh; Donald J.
-
CPC
-
US Classifications
Field of Search
US
- 227 8
- 227 10
- 227 130
- 227 9
- 123 46 SC
-
International Classifications
-
Abstract
A constant volume metering chamber and valve assembly for use with a pressurized fluid supply containing a fluid is described for use in a power fastening tool. The assembly includes a first spring-biased valve and a second spring-biased valve. There is a metering chamber having an inlet and an outlet, so that the first spring-biased valve controls the inlet and the second spring-biased valve controls the outlet. An actuator assembly operates causes the first and second spring-biased valves to move in either a first valve sequence or a second valve sequence. The first valve sequence includes engaging the first spring-biased valve with the inlet, preventing flow of the fluid from the fluid supply into the metering chamber, followed by disengaging the second spring-biased valve from the outlet, allowing flow of the fluid from the metering chamber. The second valve sequence includes engaging the second spring-biased valve the said outlet, preventing flow of the fluid from the metering chamber, followed by disengaging the first spring-biased valve from the inlet, allowing flow of the fluid from the fluid supply into the metering chamber, such that fluid is prevented from flowing freely from the pressurized fluid supply through the inlet and the outlet of the metering chamber.
Description
BACKGROUND OF THE INVENTION
The present invention relates to a constant volume valve for a combustion-powered tool, such as a power framing tool. More specifically, it relates to a constant volume valve assembly that measures a volume of a fluid before allowing it to flow into a combustion chamber.
This invention also relates to a pneumatically powered, combustion-powered, or other rapidly acting, fastener-driving tool of a type utilizing collated fasteners. Typically, as exemplified in Nikolich U.S. Pat. Re. 32,452, Nikolich U.S. Pat. No. 4,522,162; Nikolich U.S. Pat. No. 4,483,474; Nikolich U.S. Pat. No. 4,403,722 and Wagdy U.S. Pat. No. 4,483,473, which are herein incorporated by reference, a combustion-powered, fastener-driving tool comprises a combustion chamber, which is defined by a cylinder body and by a valve sleeve arranged for opening and closing the combustion chamber. Generally, similar combustion-powered, nail- and staple-driving tools are available commercially from ITW-Paslode (a unit of Illinois Tool Works Inc.) of Vernon Hills, Ill., under its IMPULSE trademark.
In such a tool, it is beneficial to apply a constant force during the driving stroke to each fastener as it is driven into the workpiece. Measurement of the amount of fuel to the combustion-powered tool, or the amount of compressed gas to a pneumatically powered tool, helps provide a constant force. A combustion powered fastening tool is described in U.S. Pat. No. 4,721,240 to Cotta that measures fuel by opening a valve for a length of time defined by movement of a cam. Fuel passes through a fuel valve to a combustion chamber conduit, the amount of which is equal to the volume that passes through a needle valve during the time the fuel valve is open. Measurement of the flow of a fluid by time allows the amount of fluid supplied to the tool to vary as flow rates of the fluid change. As a fuel cylinder is emptied, the flow rate of the fluid changes as the cylinder pressure drops. Similarly, pressure or flow variations in a common supply of pneumatic fluid will also result in differences in the amount of power supplied on each charge of the cylinder.
Control of fuel into a combustion chamber by valve assemblies is shown in U.S. Pat. Nos. 655,996 and 1,293,858. Both references disclose a pressurized fluid inlet valve and fluid outlet valve that bracket a machine-supply passage. High-pressure fluid is fed to a machine to supply power via the inlet valve, and is discharged through the outlet valve when it returns from the machine following expulsion of its power. Neither reference teaches the use of such a system to supply a constant measurement of fluid. Further, following combustion of a fuel or expansion of a high-pressure fluid, the fluid is no longer useful to supply power to a tool and measurement at that point is ineffective.
U.S. Pat. No. 4,913,331 to Utsumi describes an apparatus that drives a piston with an internal combustion engine that utilizes a measuring chamber to dispense a constant volume of fuel. A fuel piston containing the measuring chamber is reciprocally moveable within a fuel cylinder. The fuel inlet channel and the fuel outlet channel are positioned such that the measuring chamber is filled and emptied by movement of the piston between the inlet and outlet channels. Seals are located on either side of the chamber between the fuel piston and the cylinder, preventing leakage of fuel from the pressurized fuel supply to the combustion chamber. Steady movement of the piston would cause rapid wear on these seals, since they are constantly in contact with the cylinder surface.
One operational drawback of conventional combustion-powered tools, is that when operated at relatively low temperatures, such as below 32° F., the pressure of the pressurized fuel falls, causing a greater pressure differential between the atmosphere and the fuel. At this lower pressure, the fuel does not dissipate as rapidly through the appropriate passageways and into the combustion chamber. This condition causes a delay in the combustion, which interferes with the operational efficiency of the tool.
It is, therefore, an object of this invention to provide an improved constant volume measurement of a fluid to an apparatus, such as a combustion-powered tool, to produce a constant driving force.
It is yet another object of this invention to provide an improved constant volume measurement of fluid in a compact space.
It is still another object of this invention to provide an improved constant volume valve assembly, whose seals are not constantly wearing against a sealing surface.
It is a further object of the present invention to provide an improved constant volume valve assembly that facilitates the movement of fuel even when fuel pressure drops, such as when the tool is exposed to low temperatures.
SUMMARY OF THE INVENTION
These and other objects are met or exceeded by the present device for metering a constant volume of fluid to provide constant energy to a tool. This apparatus is most useful in a portable fastening tool powered either pneumatically or by an internal combustion engine. In the preferred embodiment, configuration of the valves and control mechanism also provides a delay between the closing of one valve and the opening of another, ensuring that fluid is metered before moving downstream to the combustion chamber.
More specifically, the present invention provides a constant volume metering chamber and valve assembly for use with a pressurized fluid supply. The assembly includes housing defining a metering chamber having an inlet and an outlet. A first spring-biased valve is disposed in a housing to control fluid flow to the inlet. A second spring-biased valve is disposed in the housing to control fluid flow to the outlet. An actuator assembly is connected to the two valves, and is sequentially operable from a first position, in which the first spring-biased valve is open and the second spring-biased valve is closed, to a second position, in which the first and second spring-biased valves are both closed, and to a third position, in which the first spring-biased valve is closed and the second spring-biased valve is open. The valve assembly is configured and arranged so that a volume of fluid entering the chamber from the inlet in the first position is collected in the metering chamber, sealed within the metering chamber in the second position, and released from the metering chamber in the third position to provide a constant volume of fluid from each sequential movement of the actuator from the first position to the third position.
The present constant metering valve produces a constant driving force by a fastener-driving tool because it provides a consistent quantity and quality of fuel or hydraulic fluid each time the tool is fired. The fluid supply to the power tool of this invention is measured by volume, not by time, providing a more accurate and more consistent supply of power to the tool. As pressure varies, the fluid density changes in either system because the molecules become more or less densely packed. However, in a flow system, flow rates will also change if the pressure drop across the metering valve fluctuates. Change in flow rate will have no effect in a constant volume system as long as the constant volume chamber is filled in the time the inlet valve to the metering chamber is open.
Further, arrangement of the metering chamber and the spring-biased valves in the present invention leads to compact use of space, as would be useful in a compact, portable tool. Collinear placement of the valves and the oblique angle of the combustion chamber passageway features a shorter distance from the pressurized fluid supply to the combustion chamber, compared to other designs.
Using spring-biased valves to control fluid flow is also advantageous. The seat of the valve that forms the seal with the inlet and outlet of the metering chamber is in contact with the walls of the chamber only for a relatively short time. As the valves open and close, there is no constant rubbing of the seals with adjacent walls. This leads to longer life for the seals.
Another advantage of the present valve assembly is that a disk is preferably provided to at least one of the spring-biased valves which facilitates the flow of fuel into a combustion chamber passageway even in operational conditions when fuel flow is impaired, as when outside operational temperatures fall below freezing.
Still another feature of the present valve assembly is that the actuator assembly is configured to provide an inherent delay in the operation of the upper and lower spring-biased valves to ensure that a designated volume of fuel will be retained in the metering chamber before the lower valve releases the fuel to the combustion chamber. In the preferred embodiment, this delay is achieved in part by a deliberately loose mating engagement between a tongue of an actuator pivoting link arm and a notch in an actuator control arm. This loose engagement ensures that, while the pivoting link arm travels a continuous motion due to the engagement of the tool upon a workpiece, the actuator control arm is not continuously moved, resulting in a slight “pause” in the operation of the spring-biased valves. In this manner, the consistency of the volume of fuel temporarily held in the metering chamber is maintained.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1
is a back view of the present constant volume valve assembly as attached to a fuel canister;
FIG. 2
is a front vertical sectional view of the present constant volume valve assembly;
FIGS. 3A-3C
are a series of fragmentary sectional views of the present constant volume valve assembly depicting three valve positions as the actuator assembly moves through an operational sequence;
FIG. 4
is a fragmentary sectional view of the present constant volume valve shown equipped with a disk for facilitating the movement of fuel from the metering chamber into the combustion chamber; and
FIG. 5
is a fragmentary sectional view of an alternate embodiment of the present constant volume valve showing the sealing connection between the valve and the interior nozzle of a pressurized fuel cartridge.
DETAILED DESCRIPTION OF THE INVENTION
Referring to
FIGS. 1 and 2
, a constant volume valve assembly and metering chamber is, generally designated
10
. In the following description, the terms “upper” and “lower” refer to the assembly in the orientation shown in the drawings. However, it is contemplated that the present assembly may be used in a variety of positions as is well known in the art. The present valve assembly
10
is particularly useful in a pneumatic or combustion powered tool (not shown), having a valve housing
12
in which the fluid to be metered is injected under pressure. The valve assembly
10
provides a fixed amount of fuel to the combustion chamber (not shown) of the tool. Alternatively, it is contemplated that the present valve assembly
10
may also meter pressurized air, which expands to provide power, to the pneumatic tool. The present valve assembly
10
is usable in any tool or device that would benefit from a steady, uniform supply of a pressurized fluid.
The housing
12
of the valve assembly
10
includes at least two spring-biased valves, a first spring-biased valve
16
and a second spring-biased valve
18
that respectively control the fluid flow to an inlet
20
and an outlet
22
of a metering chamber
24
. The metering chamber
24
is defined by the housing
12
, and optionally has one or more ports in addition to the inlet
20
and outlet
22
, as will be discussed below. Neither the shape of the metering chamber
24
, nor the position of the inlet
20
or outlet
22
is particularly important. However, it is preferable to place the inlet
20
and the outlet
22
at diametrically opposed ends of the metering chamber
24
. In this configuration, the spring-biased valves
16
,
18
are preferably approximately axially collinear, conserving space. In this preferred configuration, fluid flow through the metering chamber
24
will flow from the inlet
20
to the outlet
22
, generally parallel to the axes of the spring-biased valves
16
,
18
.
The metering chamber
24
may be any type of chamber capable of providing a constant volume space for measurement of the fluid, meaning that the volume of fluid collected in the metering chamber is equal to the volume of fluid released from the metering chamber. While the fluid is sealed within the metering chamber
24
, the pressure remains constant. The metering chamber
24
may be a separate vessel or it may simply be a cavity
24
within the housing
12
. The housing
12
will generally also be used to support other components of the propulsion system, such as a pressurized fluid canister
28
(shown in
FIG. 1
) and the spring-biased valves
16
,
18
. Preferably, the metering chamber
24
is stationary relative to the housing
12
.
The volume of the metering chamber
24
while preferably fixed, is optionally adjustable by, for example, placement of a movable wall or opening of valves to additional chambers (not shown). However, its usefulness for metering purposes depends upon the ability of the chamber
24
to remain at a constant volume until some setting, valve or adjustment is purposely changed.
The spring-biased valves
16
,
18
each include a preferably conical seat
30
,
32
, a rod
34
,
36
, and a spring
38
,
40
, respectively. Although discussed in terms of the first spring-biased valve
16
, it is to be understood that the following description also applies to the corresponding parts of the second spring-biased valve
18
. The seat
30
is sized and configured to sealingly engage with the inlet
20
of the metering chamber
24
when the spring-biased valve
16
is in a closed position. Movement of the seat
30
between an open position and the closed position, is controlled by the rod
34
. Although the spring
38
is an economical method of biasing the valve, use of other biasing devices is contemplated. The spring
38
is used to bias the valve
16
toward the closed position. Each of the springs
38
,
40
has an anchored end
42
,
44
and a movable end
46
,
48
, respectively. The movable end
46
exerts a force against the seat
30
tending to move it in the direction of the metering chamber
24
by the force of the spring
40
pushing against the anchored end
42
. Although the anchored end
42
may be anchored directly to the housing
12
, preferably, the anchored end is seated within a compartment described in greater detail below.
Fluid is supplied to the housing
12
under pressure. It is generally desirable that the tool is portable, and in such a case, the fluid is delivered from the pressurized canister
28
that fits within or attaches to the tool. In the case where the tool is to be used in a shop or other location where a large supply of pressurized fluid is available, the fluid is preferably available to the tool through a hose or similar device (not shown). The valve assembly
10
of the present invention is useful in either of these situations, and use in either setting is contemplated. Since temperature and pressure affects the density of any fluid, these factors should be kept as constant as possible to minimize variation in the amount of fluid supplied.
Before entering the valve assembly
10
, the fluid preferably flows through a filter
50
(
FIG. 2
) to minimize unwanted contaminants. The filter
50
is preferably disposed at one end of a nipple
51
, which matingly and sealingly engages the canister
28
. After passing the filter
50
, the fuel travels into an upper passageway
52
. The upper passageway
52
leads from the source of the pressurized fluid, such as the pressurized canister
28
, to the inlet
20
of the metering chamber
24
. To achieve the most consistent amount of fluid, the upper passageway
52
is preferably sufficiently wide to consistently achieve supply pressure before closure of the first spring-biased valve
16
.
In some cases, it is desirable to provide an upper chamber
54
for accumulation of pressurized fluid. Where, for example, the flow rate of the fluid is low, fluid accumulates in the upper chamber
54
, providing a burst of fluid to enter the metering chamber
24
when the inlet
20
is opened. Fluid released from the metering chamber
24
flows into a lower chamber
56
. Metering is accomplished through opening and closing of the first and second spring-biased valves
16
,
18
by an actuator assembly
60
. The actuator assembly
60
is any mechanism capable of causing the opening and closing of the first and second spring-biased valves
16
,
18
in a particular sequence to allow measurement of the fluid in the metering chamber
24
. While a mechanical linkage is the preferred form of the actuator assembly
60
, a computer controlling one or more cams is an example of an acceptable alternative configuration.
In the preferred embodiment, the actuator assembly
60
includes a C-shaped actuator arm with an upper arm
62
, which is connected to the rod
34
of the first spring-biased valve
16
, and a lower arm
64
, which is connected to the rod
36
of the second spring-biased valve
18
. The upper arm
62
and the lower arm
64
are connected to each other by a control arm
66
(FIG.
1
). A notch
67
in the control arm
66
is engaged by a pivoting link arm
68
which is pivotally engaged to the housing
12
at a point
68
a
. The specific engagement between the link arm
68
and the notch
67
is via a tongue
69
. The control link arm
68
is operated through movement of the nosepiece valve linkage (not shown), the construction and operation of which is disclosed in the Nikolich patents incorporated by reference here.
An important feature of the present actuator assembly
60
is that a delay is created in the movement of the control arms
62
,
64
,
66
and their actuation of the upper and lower spring-biased valves
16
,
18
so that a constant volume of pressurized fluid is momentarily retained in the metering chamber
24
. This delay is created in part by a loose mating engagement between the tongue
69
and the notch
67
. In the preferred embodiment, the tongue
69
is provided with a reduced area compared to the notch
67
, so that the control link arm
68
can move slightly along its arcuate travel path without causing movement of the control arms
62
,
64
, and
66
. The looseness or “sloppiness” of the engagement between the tongue
69
and the notch
67
can vary with the application, as can the specific configuration of the mating engagement, including having the notch on the arm and the tongue on the control arm
66
.
The actuator assembly
60
moves the first and second spring-biased valves
16
,
18
in either a first valve sequence or a second valve sequence, depending on which valve is to be opened and which valve is to be closed. The valve sequence is determined according to the combustion cycle, in the case of a combustion tool, or the impact cycle of a pneumatic tool.
Turning now to
FIGS. 3A-3C
, the valve sequences are described. The beginning of the first valve sequence is defined when the tool is in between uses. In this position, the tool is powered up and ready to be used, but is not yet in contact with the workpiece into which a fastener is to be driven. At this time, the actuator assembly
60
is in the first position as depicted in
FIG. 3A
, the arm
62
is spaced a maximum distance from an opposing wall of the housing
12
. The first spring-biased valve
16
is in an open position and the second spring-biased valve
18
is closed. The metering chamber
24
is thus filled with fuel or fluid due to communication with the cartridge
28
through the passageway
52
.
During the first valve sequence, the first spring-biased valve
16
moves from an open position to a closed position and the second spring-biased valve
18
opens, but the second valve does not begin to open until first valve is completely closed. This first valve sequence will generally be triggered by some stimulus in preparation for firing of the tool. To have power to drive a fastener, the metered fluid is moved into position to deliver that power; i.e., fuel is moved into the combustion chamber or air into an expanding cylinder. The sequence is preferably initiated by any preparatory mechanism, such as contact of the tool with a workpiece, beginning to squeeze the trigger mechanism and the like. If a combustion powered framing tool is used, priming of the combustion chamber preferably takes place when a workpiece contact element comes in contact with the workpiece, allowing the fuel to flow from the metering chamber
24
, through the lower chamber
56
, into a combustion chamber passageway
70
and ultimately to the combustion chamber (not shown). In the depicted and preferred embodiment, the sequence is initiated by contacting the tool with a workpiece, which causes the pivoting link arm
68
to begin its arcuate path of travel represented by the arrow A (FIG.
1
).
It is important to note that the metering chamber
24
is used solely for measurement of the fluid, and that there are no physical or chemical changes to the fluid while it is sealed in the chamber. To provide constant power, the fluid is preferably delivered at the same volume, temperature and pressure for each cycle. Fluids cannot be accurately measured while chemical or physical reactions are taking place, thus it is preferred that the fluid have the same chemical composition when it is released from the metering chamber
24
as when it entered the metering chamber.
Referring now to
FIG. 3A
, which corresponds to the first position in the preferred embodiment shown, in this position, fluid freely enters the metering chamber
24
. As the pivoting link arm
68
moves in an arc defined by the arrow A (FIG.
1
), the tongue
67
moves in a reverse arcuate direction. As such, the former upward pressure exerted upon the first rod
34
by the upper arm
62
is released, allowing the spring
38
to bias the first seat
30
of the first valve
16
into engagement with the inlet
20
of the metering chamber
24
.
At this point, both spring-biased valves
16
,
18
are closed, preventing flow of the fluid from the fluid supply canister
28
into and out of the metering chamber
24
. This position is depicted in
FIG. 3B
, and corresponds to the second position of the actuator assembly
60
. The metering chamber
24
is closed at both the inlet
20
and the outlet
22
, sealing the fluid within it and providing a measured volume of fluid within the chamber.
The loose mating engagement between the tongue
69
and the notch
67
described above results in a temporary delay in the opening of the second valve
18
while the pivoting link arm
68
continues its arcuate path defined by the arrow A (FIG.
1
). Due to the loose engagement, as the pivoting link arm
68
moves, there is a delay while the upward bias opening the first valve
16
is released, and the control arm
66
has not been moved sufficiently to open the second valve
18
. This delay ensures that the volume of fuel in the metering chamber
24
will remain constant, and that unwanted additional amounts cannot enter the chamber, or that premature leakage from the outlet
22
into the lower chamber
56
cannot occur.
The third position of the actuator assembly
60
is shown in
FIG. 3C
, which is attained after the first valve
16
has completely closed and the second spring-biased valve
18
is opened. In this position, the fluid is released from the metering chamber
24
. In the preferred embodiment, the entire first valve sequence takes place as the actuator arm
60
moves continuously from the first position through the second position to the third position.
Following firing of the tool
12
, the second valve sequence is initiated, in which the lifting of the tool from the workpiece causes the pivoting linking arm
68
to move the actuator assembly
60
from the third position, through the second position, to the first position. This sequence closes off the outlet
22
of the metering chamber
24
from flow downstream, and reopens the inlet
20
to again allow flow of fluid into the metering chamber
24
. Any stimulus that follows firing of the tool
12
but precedes the first valve sequence may be used to start this sequence.
The second valve sequence moves the first and second spring-biased valves through the same steps as the first valve sequence, but in the reverse order. Starting with the third actuator assembly
60
position shown in
FIG. 3C
, the second spring-biased valve
18
is disengaged from the outlet
22
, preventing flow of the fluid from the metering chamber
24
. After the second valve
18
is completely closed, the second actuator assembly
60
position is obtained, as shown in FIG.
3
B. Here both valves
16
,
18
are closed to prevent backflow of the fluid, and the metering chamber
24
contains only a residual amount of fluid. Finally, the first spring-biased valve
16
is disengaged from the inlet
20
, allowing free flow of the fluid from the fluid supply
28
into the metering chamber
24
, but that fluid is prevented from flowing freely from the pressurized fluid supply
28
through the inlet
20
and the outlet
22
of the metering chamber
24
to the combustion chamber passageway
70
.
In the preferred embodiment, this operation or valve sequence is controlled by the pivoting action of the link arm
68
which moves the actuator assembly
60
from a position where the upper arm
62
has a maximum spacing from the housing
12
(FIG.
3
A), to a position where the lower arm
64
has a maximum spacing from the housing
12
(FIG.
3
C). In the preferred embodiment, in addition to the loose mating engagement between the notch
67
and the tongue
69
, the actuator assembly
60
also includes a delay mechanism also operating between the closing of one of the valves
16
,
18
and the closing of the other valve
18
,
16
. Any type of delay mechanism is suitable, such as an electrical delay, electronic means of a mechanical delay mechanism. In the most preferred mechanical delay mechanism, the actuator assembly
60
is slidably connected to each of the rods
34
,
36
. The first rod
34
has a first opener
71
such as a ‘C’-clip secured to the rod
34
and the second rod
36
has a second opener
72
. Spacing of the openers
71
,
72
on the rods
34
,
36
are preferably used to create a delay in the closing of one valve
16
,
18
before the opening of the other valve
18
,
16
.
In the preferred delaying mechanism, the control arm
66
of the actuator assembly
60
is longer than the housing
26
in which the valve assembly resides. The excess length is sufficient to allow the upper arm
62
and the lower arm
64
to sandwich the housing
12
between them with excess space between the housing, and the actuator arms
62
,
64
. In response to the stimulus that triggers the valve sequences, the control arm
66
moves up and down (directions relate to the tool, as oriented in FIG.
3
).
Referring now to
FIG. 3A
, as the actuator assembly
60
moves through the first valve sequence, the upper arm
62
begins in contact with the first opener
71
. As the control arm
66
moves downward, release or expansion of the first spring
38
holds the first opener
71
against the upper arm
62
until the first seat
30
comes into contact with the inlet
20
of the metering chamber, closing the first spring-biased valve. Once the control arm
66
moves sufficiently so that the upper arm
62
is disengaged from the first opener
71
(as shown in FIG.
3
B), the first spring
38
biases the valve
16
into the closed position. During this movement from the first position (
FIG. 3A
) to the second position (
FIG. 3B
) of the control arm
66
, the lower arm
64
has slid along the second rod
36
, partially, but not totally decompressing the second spring
40
. Next, in moving from the second position (
FIG. 3B
) to the third position (
FIG. 3C
) of the control arm
66
, the lower arm
64
slides along the second rod
36
and finally contacts the second opener
72
, compressing the second spring
40
, and opening the second spring-biased valve
18
. The second valve sequence similarly reverses the above steps, introducing a delay between the closing of the second spring-biased valve
18
and the opening of the first spring-biased valve
16
.
Seals are used where suitable to prevent flow of the fluid into the area outside the valve assembly
10
, the metering chamber
24
, and the housing
12
. The exact number, shape and placement of such seals depend on the exact configuration of the valve assembly
10
for a specific application. In the preferred embodiment shown, a removable insert
74
is optionally used to surround the rod
34
,
36
of each of the spring-biased valves
16
,
18
as the rod passes through the housing
26
and contacts actuator assembly
60
. O-rings
76
, gaskets or similar devices, are preferably used to prevent leakage between the removable insert
74
and the housing
12
or the rods
34
,
36
. In some applications, it will be preferable for the length of the spring
38
,
40
to exceed the dimensions of the upper chamber
54
or the lower chamber
56
. When this is desirable, the removable insert
74
includes a hollow compartment
78
that is sized and configured to receive a portion of the length of the spring
38
,
40
, and to receive the anchored end
42
. The removable insert
74
also provides easy access to the spring-biased valves
16
,
18
and their component parts when replacements are installed.
Referring now to
FIG. 4
, it is preferred that the present valve assembly
10
be provided with a mechanism for facilitating the movement or evacuation of fuel from the metering chamber
24
through the outlet
22
and ultimately into the passageway
70
leading to the combustion chamber. As described above, it has been found that when combustion-powered tools of this type are operated at cold temperatures, such as below
32
° F., the fuel pressure drops and it becomes more difficult to move the fuel into the combustion chamber. To address this problem, the present valve assembly
10
is preferably provided with a disk
80
secured to the valve
18
, specifically at the end of the rod
36
disposed in the metering chamber
24
. The disk
80
is preferably located closer to the inlet
20
when the valve
18
is closed. To that end, the disk
80
is secured to a pedestal
82
which in turn is secured to the conical seat
32
. In the preferred embodiment, the disk
80
is made of brass or equivalent rigid, heat resistant material, and the pedestal
82
is made of rubber or similar resilient polymeric or plastic material. However, other materials are contemplated. Preferably, the disk
80
is friction fit to the pedestal
82
through a frictional mating engagement between a lug
84
on the pedestal and an axial bore
86
in the disk. However, other ways of fastening the disk
80
to the pedestal
82
are contemplated, including but not limited to ultrasonic welding, insert molding, adhesives or other mechanical fasteners. The disk
80
is dimensioned to have a diameter which approximates, but is less than the diameter of the metering chamber
24
.
In operation, as the valve
18
opens, as described above in relation to
FIG. 3C
, the disk
80
moves with the seat
32
from its rest position near the inlet
20
of the metering chamber
24
, (best seen in
FIG. 4
) to a location closer to the outlet
22
. This movement will push any residual fuel from the metering chamber
24
through the outlet
22
and ultimately into the passageway
70
leading to the combustion chamber. In this manner, the fuel is mechanically moved from the metering chamber
24
. However, since the problem of low fuel pressure is temperature-related, an alternate solution would be to provide a supplemental exhaust passageway
88
through which hot exhaust from the combustion chamber heats up the metering chamber during operation of the tool. An equivalent arrangement is the provision of an electric heating element powered by a resistor or other known arrangement which maintains a satisfactory temperature in the metering chamber
24
to maintain fuel pressure.
Referring now to
FIG. 5
, the connection between the valve
10
and the fuel canister
28
is shown in greater detail. It is important that a sealing relationship be established between the valve
10
and the fuel canister
28
to prevent loss of fuel, as well as avoid unwanted combustion. The fuel canister
28
is provided with an internal stem
90
which defines an outlet for the fuel contained in the canister under pressure, as is known in the art. As is well known in the art, and exemplified by U.S. Pat. No. 5,115,944 which is incorporated by reference, the stem
90
is secured to, and is circumscribed by an endcap
92
which encloses the end of the canister
28
and forms a rolled seam
94
thereover.
An adapter
96
frictionally engages the endcap
92
and circumscribes and protects the projecting stem
90
. An axial passageway
98
is defined by the adapter
96
and accommodates the stem
90
. In the preferred embodiment, the adapter also includes a frangible end membrane
100
which blocks the passageway
98
, and provides a visible indication of whether or not the canister
28
has been used. The membrane
100
is configured to be pierced upon mating engagement with the nipple
51
. Accordingly, the passageway
98
is dimensioned for accommodating the nipple
51
.
By the same token, the nipple
51
is preferably generally cylindrical in shape, and has a diameter or cross-sectional parameter dimensioned to slidably and matingly engage the passageway
98
, and a length dimensioned to engage an end
102
of the stem
90
to effect fluid communication between the canister
28
and the valve
10
. In the preferred embodiment, the nipple
51
is cylindrical, however, other non-circular cross-sectional shapes are contemplated depending on the application, and including oval, square, rectangular and polygonal shapes.
In the preferred embodiment, the nipple
51
and the stem
90
are configured so that, upon operational engagement as depicted in
FIG. 5
, a sealing relationship is achieved. This relationship, designed to prevent unwanted loss of fuel, may be achieved through frictional contact between the end
102
of the stem
90
and an end
104
of the nipple
51
. However, it is preferred that some sort of sealing formation be provided to at least one of the nipple
51
and the stem
90
. In the preferred embodiment, the sealing formation is a resilient O-ring
106
provided to the nipple
51
. However, other known types of sealing formations are contemplated, including but not limited to ring seals, molded seals and flat washers.
Also, the present nipple end
104
defines a chamber
108
for receiving or capturing a resilient sealing member such as the O-ring
106
. More specifically, the end
104
is tapered or chamfered for both retaining the O-ring
106
and also for facilitating insertion of the nipple
51
into the adapter passageway
98
. The tapered end
104
more easily pierces the membrane
100
, especially when the nipple
51
is fabricated of metal such as brass, which is preferred, however other suitably rigid and durable materials are contemplated.
To further enhance the sealed relationship of the engaged nipple
51
and the stem
90
, the end
102
of the stem is configured for matingly engaging or accommodating the O-ring
106
. As such, the end
102
is preferably provided with an annular groove
110
. Naturally, it is contemplated that the O-ring
106
or other resilient sealing member may be alternately mounted to the stem
90
, or that it may be attached to the nipple end
104
by adhesive, in a groove (not shown) or other known type of O-ring attachment technology.
It is also contemplated that, depending on the application, if fluid communication with the canister
28
is required for any reason, a connector maybe provided in the form of the nipple
51
which, at the end opposite to the end
104
, is in fluid communication with a fluid container or reservoir as desired.
In use, the canister
28
is inserted into the combustion tool so that the nipple
51
matingly engages the adapter
96
. The canister
28
is pressed upon the nipple
51
so that the membrane
100
is pierced and the nipple end
104
enters the passageway
98
until contact is made with the stem end
102
. As described above, as sealing relationship is preferably obtained, and it is contemplated that other locking apparatus may be employed to secure the canister
28
in this position.
Thus, it will be seen by those skilled in the art that the present valve assembly and metering changer provide a simple method of providing a constant volume of fluid to a power fastening tool. The two spring-biased valves
16
,
18
control the inlet and the outlet to the constant volume metering chamber
24
, measuring a constant amount of fluid, independent of in fluctuations in the fluid flow rate. The actuator assembly
60
manipulates opening and closing of the valves
16
,
18
, receiving the fluid from the pressurized source
28
and metering it before it flows downstream to a combustion or expansion chamber. This arrangement of the valves
16
,
18
minimizes wear on the seals, reducing maintenance.
While a particular embodiment of the constant volume valve assembly and metering chamber has been shown and described, it will be appreciated by those skilled in the art that changes and modifications maybe made thereto without departing from the invention in its broader aspects and as set forth in the following claims.
Claims
- 1. A constant volume metering chamber and valve assembly for use with a pressurized fluid supply containing a fluid in a combustion-powered tool, said assembly comprising:a housing defining a metering chamber having a plurality of ports including an inlet and an outlet; a first spring-biased valve disposed in said housing to control fluid flow through said inlet; a second spring-biased valve disposed in said housing to control fluid flow through said outlet; an actuator assembly, connected to said first and second spring-biased valves and sequentially operable from a first position, in which said first spring-biased valve is open and said second spring-biased valve is closed, to a second position, in which said first and second spring-biased valves are both closed, and a third position, in which said first spring-biased valve is closed and said second spring-biased valve is open; and said valve assembly being configured and arranged so that a volume of fluid entering said chamber from said inlet in said first position is collected in said metering chamber, sealed within said metering chamber in said second position, and released from said metering chamber in said third position to provide a constant volume of fluid for each sequential movement of said actuator from said first position to said third position.
- 2. The valve assembly of claim 1, wherein said actuator assembly is operable from said third position, in which said first spring-biased valve is closed and said second spring-biased valve is open, to said second position, in which said first and second spring-biased valves are both closed, to said first position, in which said first spring-biased valve is open and said second spring-biased valve is closed, such that, after a volume of fluid is released from said metering chamber in said third position to provide a constant volume of fluid, said metering chamber is sealed to prevent backflow of said fluid in said second position, and said metering chamber is refilled with a volume of fluid in said first position for each sequential movement of said actuator from said third position to said first position.
- 3. The valve assembly of claim 1, wherein said metering chamber is configured and arranged so that the volume of fluid collected equals the volume of fluid released from said metering chamber.
- 4. The valve assembly of claim 1, wherein said metering chamber is provided with a device for facilitating the evacuation of fuel from said chamber.
- 5. The valve assembly of claim 4, wherein said device is a disk secured to said second spring-biased valve so that said disk is disposed in said metering chamber and moves toward said outlet when said second spring-biased valve opens.
- 6. The valve assembly of claim 1, wherein said each of said first and second spring-biased valves further comprise:a seat with a flange, said seat being sized and configured to sealingly engage a corresponding one of said ports; a rod connecting said seat to said actuator assembly; and a biasing element configured for exerting force on said seat in the direction of said corresponding port.
- 7. The valve assembly of claim 6, further comprising at least one removable insert sealingly engaged with said housing and sealingly engaged with said rod, said removable insert being configured to allow said rod to pass through said housing to said actuator assembly.
- 8. The valve assembly of claim 1, further comprising a delay mechanism configured for causing a delay between the closing of one of said first or second spring-biased valves and the opening of the other of said first or second spring-biased valves.
- 9. The valve assembly of claim 8, wherein each of said first and second spring-biased valves include a biased rod, and said actuator assembly is slidably connected to each of said rods between said housing and an opener, said opener being positioned on said rod such that the delay is caused due to slideable movement of said actuator assembly between said opener of one of said spring biased valves and said opener of the other one of said spring biased valves.
- 10. The valve assembly of claim 8 wherein said actuator assembly includes a control arm configured for actuating said first and second spring-biased valves, and a pivoting link arm configured to engage said control arm to cause said actuation, said arms being configured to have a loose mating engagement for causing said delay.
- 11. The valve assembly of claim 10 wherein said control arm has a notch, and said pivoting link arm has a tongue configured for loosely engaging said notch for causing said delay.
- 12. The valve assembly of claim 1, wherein said second spring-biased valve is generally axially collinear with said first spring-biased valve.
- 13. The valve assembly of claim 1 wherein said housing further comprises a combustion chamber passageway configured and arranged to be at an oblique angle relative to axes of said spring-biased valves.
- 14. The valve assembly of claim 1, wherein the volume of said metering chamber is fixed and the fluid released from said metering chamber is the same chemical composition as the fluid entering said metering chamber.
- 15. A constant volume valve assembly for a combustion powered tool having a pressurized fluid supply, the tool to be used in conjunction with a workpiece, said valve assembly comprising:a first spring-biased valve; a second spring-biased valve generally axially collinear with said first spring-biased valve; a metering chamber having a constant volume, an inlet and an outlet, said inlet being controlled by said first spring-biased valve and said outlet being controlled by said second spring-biased valve; an actuator including a control arm connected to said first spring-biased valve and to said second spring-biased valve; a pivoting link arm that moves in response to engagement of the tool with the workpiece causing said control arm to move toward said second side, engaging said first spring-biased valve with said inlet, preventing flow of said fluid from said fluid supply into said metering chamber, then disengaging said second spring-biased valve from said outlet, allowing flow of said fluid from said metering chamber, and that disengagement of the tool from the workpiece causes movement of said pivoting link arm to move said control arm toward said first side, engaging said second spring-biased valve into said outlet, preventing flow of said fluid from said metering chamber, then disengaging said first spring-biased valve from said inlet, allowing flow of said fluid from said fluid supply into said metering chamber, such that said fluid is prevented from flowing freely from said pressurized fluid supply through said inlet and said outlet of said metering chamber.
- 16. The valve assembly of claim 15, wherein said each of said first and second spring-biased valves further comprise:a seat with a flange, said seat being sized and configured to sealingly engage said cavity; a rod connecting said seat to said control arm; and a spring having an anchored end and a movable end, said spring exerting force on said seat in the direction of said cavity.
- 17. The valve assembly of claim 15, further comprising a delay mechanism configured for causing a delay between the closing of one of said first or second spring-biased valves and the opening of the other of said first or second spring-biased valves.
- 18. The valve assembly of claim 17 wherein said control arm is slidably connected to each of said rods of each of said first and second spring-biased valves between said housing and an opener, said opener being positioned on said rod such that a delay is caused in part due to slideable movement of said control arm between said opener of one of said spring biased valves and said opener of the other one of said spring biased valves.
- 19. The valve assembly of claim 17, wherein said delay is caused in part by a loose engagement between said control arm and said pivoting link arm.
US Referenced Citations (31)