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Description  |
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BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a rotary piston assembly structured to be
usable in a variety of mechanical devices so as to provide a highly
effective and efficient piston assembly, which maximizes the continuous
output achievable through its utilization of a rotary assembly, while also
significantly simplifying the overall mechanical design into a more
efficient, versatile, and expandable configuration.
2. Description of the Related Art
For years standard piston assemblies have been utilized in a variety of
different configurations so as to provide driving power and/or the
compression of fluid in a variety of different fields. Typically,
conventional piston assembly operate under a reciprocating movement
whereby the movement of the standard piston sequentially expand and
contracts a fixed chamber. Naturally, the expansion time during which the
piston retracts is a necessary step in order to allow future compression
by the piston to take place, and visa versa. As a result, such a
conventional piston assembly typically can only operate one half of the
time, the remaining time being spent in essentially a reset function.
Accordingly, it would be beneficial to provide a mechanical system which
does not have such down time.
To this end, and recognizing this problem piston assemblies which require
large and/or continuous power outputs typically incorporate the use of a
plurality of piston assemblies, sometimes offset from one another. As a
result, a certain degree of power and/or mechanical activity is always
being undertaken by at least some of the piston assemblies, while other
piston assemblies are resetting. Still, however, such a configuration
requires large and complex mechanical assemblies to be configured so as to
accommodate the large numbers of piston assemblies and effectively drive
them in opposing manners with one another. As a result, such assemblies
are not conducive to compact and/or high efficiency uses.
Having recognized the general efficiency losses associated with standard
piston assemblies, others in the field have attempted over the years to
develop rotary assemblies which can provide for continuous outputs and/or
driving operation. For example, others have sought to replace standard
piston driven engines with rotary engines that seek to take advantage of
the mechanical benefits associated with a continuous rotary driving. Much
like other devices which seek to take advantage of a rotary action, such
rotary engines are often substantially complex assemblies, which have a
variety of physical limitations associated with their use. For example,
recognizing the compression and expansion that is still required within
any type engine assembly, including a rotary engine, conventional rotary
engines typically try to solve the problem by utilizing an interior body
rotating asymmetrically within an exterior body. This asymmetrical
relative rotation is a critical factor in such current rotary engines, as
such has generally been considered one of the only physical and effective
manners available to achieve the required compression surface against the
leading edge of the interior fin structures. As can be appreciated,
however, the complex mechanical nature of such rotary engines tends to
counter any advantage that is generally achieved from the continuous
rotary aspect of the driving and/or pumping cycle.
As a result, it would be highly beneficial to provide a rotary assembly
which achieves a mechanical advantage by having one or more pistons
continuously rotating in the same direction, but which does not require
overly complex and elaborate configurations to provide effective results.
Moreover, such rotary piston assembly should be readily expandable and
usable in a variety of configurations, including engines, turbines, pumps,
etc., wherein piston assemblies are currently utilized and wherein the
losses associated with the necessary reciprocating motion of standard
pistons are seen as limiting.
SUMMARY OF THE INVENTION
The present invention relates to a rotary piston assembly configured for
use in a variety of different applications, including, engines, turbines,
pumps, and the like, many of which have traditionally utilized standard
reciprocating piston configurations. Looking particularly to the rotary
piston assembly of the present invention, it includes a piston housing.
The piston housing is structured to contain at least one, but preferably a
pair of pistons, and preferably includes a generally circular
cross-sectional. Defined within the piston housing is at least one annular
chamber. The annular chamber is preferably concentrically disposed about a
central axis of the piston housing, and is configured so that the piston
may move therethrough as it rotates about the central axis.
Disposed in generally overlapping association with the piston housing is an
abutment housing. In particular, the piston housing preferably includes a
generally arcuate passage defined therein, and which may receive at least
a portion of the abutment housing. As such, the abutment housing, which is
structured to rotate about an abutment axis, rotates through the arcuate
passage, and accordingly, through the piston housing. As a result of this
overlapping engagement, an interior chamber is defined between the
abutment housing and the piston housing.
Further defined in the abutment housing is at least one gap. In particular,
the gap is defined by a pair of opposing ends, and as a result of rotation
of the abutment housing, the gap is also structured to pass through at
least the annular chamber of the piston housing.
The piston and the abutment housing are structured to rotate relative to
one another at first and second angular velocities, respectively.
Preferably, however, the first and second angular velocities are set
relative to one another such that the gap of the abutment housing is
disposed in the annular chamber upon the piston moving into the interior
chamber defined between the abutment housing and the piston housing.
Accordingly, passage of the piston into the interior chamber is achieved
through the gap. Likewise, the first and second angular velocities are
also preferably set relative to one another such that the gap is also
positioned within the annular chamber upon the piston moving out of the
interior chamber. As a result, upon the piston passing out of the interior
chamber, it again passes through the gap.
Accordingly, the abutment housing generally provides a surface which
defines a necessary piston chamber and/or against which compression from a
leading surface of the piston can take place. Still, however, continuous
movement of the piston in its rotary path is not hindered and/or otherwise
interrupted by the opposing surface defined by the abutment housing. A
mechanical advantage from the rotary piston is thereby achieved, in an
efficient and effective configuration.
These and other features and advantages of the present invention will
become more clear when the drawings as well as the detailed description
are taken into consideration.
BRIEF DESCRIPTION OF THE DRAWINGS
For a fuller understanding of the nature of the present invention,
reference should be had to the following detailed description taken in
connection with the accompanying drawings in which:
FIG. 1 is a perspective exploded illustration of an embodiment of the
rotary piston assembly of the present invention;
FIGS. 2A and 2B are sequential, cross-sectional illustrations of the rotary
piston assembly of the present invention illustrating cooperative passage
of the piston through the gap defined in the abutment housing of the
present invention;
FIG. 3 is a schematic, cross-section illustration of an alternative
embodiment of the piston assembly of the present invention incorporating a
plurality of pistons and a plurality of gaps defined in the abutment
housing;
FIG. 4 is a schematic cross-section illustration of an alternative
embodiment of the rotary piston assembly of the present invention
incorporating a pair of abutment housings;
FIG. 5 is a schematic, cross-section illustration of the rotary piston
assembly of the present invention including a plurality of concentric
annular chambers defined in the piston housing;
FIG. 6 is a schematic cross-section illustration of the present invention
utilized as a pump;
FIG. 7 is a schematic cross-section illustration of the piston assembly of
the present invention utilized in a turbine configuration;
FIG. 8 is a schematic cross-section illustration of the piston assembly of
the present invention utilized in an internal combustion engine
configuration;
FIG. 9 is a schematic cross-section illustration of yet another alternative
embodiment of the rotary piston assembly of the present invention wherein
the annular chamber is defined only partially and variably about the
central axis of the piston housing between the pistons and the abutment
housing;
FIG. 10 is a perspective, schematic illustration of yet another embodiment
of the present invention wherein a rotational direction of the abutment
housing is generally perpendicular to a direction of rotation of the
piston; and
FIG. 11 is a cross-section of a preferred gearing configuration in an
embodiment of the present invention.
Like reference numerals refer to like parts throughout the several views of
the drawings.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Shown throughout the Figures, the present invention is directed towards a
rotary piston assembly, generally indicated as 10. The rotary piston
assembly 10 may be incorporated for a variety of different uses, including
a fluid pump, as depicted in FIG. 6, a turbine, as depicted in FIG. 7, an
internal combustion engine, as depicted in FIG. 8, and a variety of other
uses wherein a piston assembly may be utilized.
Looking in particular to the rotary piston assembly 10 of the present
invention, it includes a piston housing 20. The piston housing 20
preferably, but not necessarily depending upon the embodiment, includes a
generally circular interior, cross-section surface contour. Moreover,
defined, preferably as part of the piston housing 20, generally about a
central axis 23 is at least one annular chamber 22. The annular chamber 22
preferably defines a generally donut or circular shaped configuration
along a cross-section of the rotary piston assembly 10 of the present
invention relative to the central axis 23, as depicted in the accompanying
Figures. It is noted, however, that the piston housing 20, and as a result
the annular chamber 22, in addition to a generally circular cross-section
for the annular chamber 22 perpendicular to the central axis may include a
generally elongate tubular and/or elliptical type configuration along a
length of the central axis 23, and/or may include an overall annular
and/or circumferencially tubular configuration about the central axis 23,
with any shaped cross section in the plane of the central axis 23.
Moreover, the overall size and dimension of the piston housing 20 may be
varied depending upon the output and/or input requirement of the system in
which the rotary piston assembly 10 will be utilized. However, it is
noted, that the effective yet simplistic design to be described hereafter
is particularly suited for effective utilization within a small, compact
assembly, thereby allowing for the simplification and effective operation
of small articles, as well as a larger high output configurations.
Additionally, the choice of materials from which the piston housing 20,
and the various other components of the present invention to be described,
are formed may also vary although, a rigid material, such as a metal,
plastics, rigid composite and/or combination thereof, is typically
preferred so as to maintain the general integrity of the piston housing
20, and/or the other components during operation of the rotary piston
assembly 10.
Movably disposed within the piston housing 20, and preferably within the
annular chamber 22 defined about the central axis 23, is at least one
piston 30. The piston 30 preferably includes a general length and contour,
between its oppositely disposed side ends, that is at least somewhat
equivalent to a length and/or contour of the piston housing 20 and annular
chamber 22, but includes a general wedge shaped configuration at its
cross-section. As a result, the piston 30 will include a leading surface
which extends preferably radially across the annular chamber 22, and a
trailing surface which also extends preferably radially across the annular
chamber 22. Preferably, the aforementioned wedge shape is such that the
radially exterior end, which preferably conforms to the radially exterior
surface contour of the annular chamber 22, is defined by an arc that is at
least slightly larger than the arc which defines the radially interior
end, which preferably conforms to the radially interior surface contour of
the interior chamber 22.
Also, in the preferred embodiment, and for reasons to be described
subsequently, it is preferred that at least a pair of pistons 30 be
movably disposed within the annular chamber 22, at a spaced apart distance
from one another. Preferably that spaced apart relation is one hundred and
eighty (180) degrees so as to provide uniform, opposing movement. In
particular, the at least one, but preferably opposing pair of pistons 30
are structured to rotate about the central axis 23 of the piston housing
20 by moving through the annular chamber 22. Furthermore, the pistons 30
preferably rotate in unison with one another through the annular chamber
22, thereby maintaining the predetermining spacing between one another, at
a first angular velocity. The first velocity may vary depending upon the
particular needs from the rotary piston assembly 10, and in the
illustrating embodiment, a preferably uniform first angular velocity is
maintained in a direction of rotation. For example, the pistons 30
preferably rotate about the central axis 23 in a first direction, shown in
the illustrating embodiments of FIGS. 2A and 2B to be a counter clockwise
direction.
The rotary piston assembly 10 of the present invention further includes at
least one abutment housing, generally indicated as 40, which rotates about
an abutment axis 43. The abutment housing 40 also preferably includes a
generally circular cross-section perpendicular to the abutment axis 43,
and much like the piston housing 20 may include an elongate tubular
configuration along the abutment axis 43, and/or an annular tube type
configuration about the abutment axis with any shaped cross section in the
plane of the abutment axis 43. The abutment housing 40 is preferably
defined by at least a generally rigid peripheral wall structure which
follows that circular configuration. Furthermore, the abutment housing 40
includes at least one gap defined in that peripheral wall structure. In
particular, the gap is preferably defined by a pair of spaced apart ends
42 and 44 of the peripheral wall structure. Moreover, in the illustrated
embodiment a size of the gap is defined by an arc that has an angular
dimension that is generally about twice a radial angular thickness of the
piston 30.
The abutment housing 40 is structured to rotate about the abutment axis 43
at a second angular velocity. Furthermore, the abutment housing 40 is
structured to overlap and generally pass through the piston housing 20, as
seen in FIGS. 2A and 2B. In particular, the piston housing 20 preferably
includes one or more arcuate passages 26, 28 defined therein. The abutment
housing 40 is structured to rotate through those passages 26, 28 so as to
effectively rotate through and relative to the piston housing 20.
Moreover, defined between the overlapping portions of the piston housing
20 and the abutment housing 40 is preferably an interior chamber 35. The
interior chamber 35 is defined primarily within the annular chamber 22,
and is bordered by the rotating peripheral wall structure of the abutment
housing 40. As can be appreciated, however, based upon the rotation of the
abutment housing 40 the gap defined by the opposite ends 42 and 44 of the
abutment housing 40 will also rotate through the annular chamber 22, and
at times will define the opposite ends of the interior chamber 35.
Along these lines, the first and second angular velocity of the piston 30
and abutment housing 40, respectively, are set relative to one another
such that the gap defined by the opposite ends 42 and 44 of the abutment
housing 40 rotate through the annular chamber 22 of the piston housing 20
substantially simultaneously with the piston 30 passing into the interior
chamber 35. Looking specifically to FIGS. 2A and 2B, the abutment housing
40 and the piston 30 preferably, but not necessarily, rotate about
parallel axis in the same direction as one another, although the first and
second angular velocities, respectively, may be different from one
another. Accordingly, as one of the pistons 30 is entering the interior
chamber 35, the gap defined by the opposite ends 42, 44 of the abutment
housing 40 is preferably simultaneously rotating into the annular chamber
22 to begin to define the entrance of the interior chamber 35. As a result
of the timed relative rotation, and preferred sizing of the pistons 30 and
the gap in the abutment housing 40, the piston 30 essentially passes
through the gap in the abutment housing 40 so as to enter the interior
chamber 35 without being obstructed. In this regard, references should be
had to FIG. 2A which illustrates how one end 44 of the abutment housing 40
generally passes along the front or leading surface of the piston 30,
while the other end 42 of the abutment housing 40 trails towards the
trailing surface of the piston 30. As the abutment housing 40 continues to
rotate and the piston 30 continues to move, as in FIG. 2B, the end 44 of
the abutment housing 40 continues to slide radially outward along the
leading surface of the piston 30 until eventually full clearance for the
piston is achieved and the piston 30 can pass into the interior chamber
35. Based upon the relative angular velocities and sizing, the piston 30
moves continuously and generally unobstructed into the interior chamber
35. Furthermore, so as to facilitate that slided passage of the ends 42,
44 of the abutment housing 40 over the piston 30, thereby permitting the
piston 30 to pass therethrough, the ends 42, 44 are preferably tapered
inwardly towards the gap. Moreover, the ends 42, 44, which may be rigid or
somewhat resilient, preferably defined a substantially fluid impervious
sliding engagement with the piston 30 during the piston's passage through
the gap, thereby preserving an integrity of the interior chamber 35 and/or
a remainder of the annular chamber 22 in substantial isolation from one
another.
Looking further to the illustrated embodiments of the piston housing 20 and
the abutment housing 40, the diameter of the abutment housing 40 may be
generally equivalent to the diameter of the piston housing 20 at an outer
periphery of the annular chamber 22. Furthermore, the piston housing 20
and the abutment housing 40 preferably overlap relative to one another
such that the abutment axis 43 is generally aligned with an outer
periphery of the annular chamber 22 of the piston housing 20, while the
peripheral wall structure of the abutment housing 40 is generally aligned
with and passes through the central axis 23 of the piston housing 20.
Also in such an embodiment, the second angular velocity of the abutment
housing 40 is preferably twice the first angular velocity of the piston
30. As a result of this relative angular velocity between the abutment
housing 40 and the piston 30, not only can the piston 30 effectively slide
through the gap defined between the ends 42 and 44 of the abutment housing
40 when entering the interior chamber 35, but the abutment housing 40 will
also rotate sufficiently such that the gap will re-enter the annular
chamber 22 when the piston 30 is exiting the interior chamber 35.
Accordingly, in the same manner that the piston 30 passes through the gap
so as to enter the interior chamber 35, the piston 30 passes through the
gap once again so as to exit the interior chamber 35, still preserving the
isolated integrity of the interior chamber 35 from the rest of the annular
chamber 22. As a result of the proceeding, and as will be described in
greater detailed subsequently with regard to some specific examples of the
use of the rotary piston assembly 10 of the present invention, the
abutment housing 40 generally provides a surface against which the piston
30 moves and/or pushes fluid to define a piston chamber, while not
restricting and/or otherwise hampering the normal rotary movement of the
piston 30 as it continues along it rotary path. Further, in the
illustrated embodiment, the second, one hundred and eighty degree offset
piston is also provided, the timed rotation between the pistons and the
abutment housing 40 being such that when the second piston enters and
leaves the interior chamber 35, the gap once again moves into position to
permit the entry and exit of the piston 30 therethrough. In addition to
ensuring the unhindered movement of the pistons 30 along the rotary path,
such a configuration also ensures that a generally sealed isolation is
maintained between the interior chamber 35 and the remainder of the
annular chamber 22 when gap once again rotates through the annular chamber
22.
Although the illustrated preferred embodiment, as depicted in FIGS. 2A and
2B includes a pair of piston 30 disposed at a one hundred eighty degree
spacing from one another and a single gap defined in the abutment housing
40, it is understood that a variety of alternate configuration, such as
those including one or more gaps and/or one or a plurality of pistons 30,
could also be utilized and considered to be within the scope of the
present invention. For example, looking specifically to FIG. 3, four
pistons 30 and 30' are preferably provided, the pistons 30 and 30'
preferably defining two oppositely disposed piston pairs, the
corresponding pistons within each pair being spaced one hundred eighty
degree apart from one another. Likewise in the embodiment of FIG. 3 a pair
of gap 45 and 45' are preferably defined in the abutment housing 40. The
gaps 45, 45' are disposed a predetermined distance relative to one another
corresponding the spacing between the piston pairs 30 and 30'. For
example, in the illustrated embodiment, the gaps are disposed of one
hundred eighty degrees apart from one another since the piston pairs 30,
30' are disposed generally ninety (90) degrees from one another. As a
result, the rotation of the abutment housing 40 and the pistons 30, 30' in
a corresponding uniform direction results in one of the gaps 45 passing
through the annular chamber 22 when the first pair of pistons 30 are
entering and leaving the interior chamber 35, while the second gap 45'
passes through the annular chamber 22 when the second set of pistons 30'
are entering and leaving the interior chamber 35. Along these lines, it is
noted that although it is preferred that a generally symmetrical
orientation between the pairs of pistons 30 and 30' as previously
described be maintained, alternate spacings could also be utilized. In
such an embodiment wherein the spacing between the piston pairs 30 and 30'
is not ninety degrees, and/or is less than ninety degree so that
additional piston pairs can be incorporated, the relative orientation of
the gaps 45 and 45' relative to one another in the abutment housing 40
would correspondingly be adjusted so as to effectuate proper timed passage
of the gaps into the annular chamber 22.
Turning to FIG. 4, in yet another embodiment a pair of abutment housings
40, 40' may be provided in overlapping relation with a single piston
housing 20. In such an embodiment each of the abutment housings 40 and 40'
preferably includes a gap defined therein, however, a pair of spaced apart
interior chambers 35, 35' are defined within the annular chamber 22 of the
piston housing 20. Further, although in the illustration the abutment
housings 40, 40' are disposed directly opposite from one another, it is
understood that differing, and/or more tangential configurations with two
or more abutment housing 40, 40' could also be configured. However, in
such an embodiment a more symmetrical configuration is preferred so as to
standardize an effective piston stroke achieved by either of the pistons
30. Likewise, it is also noted that a single abutment housing 40 can also
be seen to rotate through multiple piston housing 20 in much the same
manner that multiple abutment housings 40, 40' rotate through a single
piston housing 20. As a result, a generally continuous array of
interlocking piston housings 20 and abutment housings 40 could be utilize,
if desired, for a particular application.
Also, looking to FIG. 5, an embodiment wherein a plurality of annular
chambers 22, 22' are defined radially from one another within the piston
housing 20 may also be provided. in such an embodiment a plurality of
integral or separate pistons 30, 30' are correspondingly disposed to move
through an appropriate annular chamber 22, 22' and pass into an out of a
corresponding plurality of interior chamber 35, 35". In such an
embodiment, as well as some others, the diameters of the abutment housing
is different from that of the piston housing.
In yet another embodiment, as defined in FIG. 9, the annular chamber is
only partially and/or variably defined about the central axis 23, more
precisely being defined directly between the abutment housing 40 and an
enlarged piston 30. In such an embodiment, the interior chamber and the
annular chamber are generally equivalent, an engagement by the abutment
housing along the leading and trailing surfaces of the pistons 30 serving
to enclose and define the interior chamber whose radial position moves
with rotation of the piston about the central axis.
Furthermore, looking to FIG. 10, it is also recognized that the abutment
axis of the abutment housing 40 may be defined perpendicular to the
central axis of the piston housing, while still achieving the desired
overlap therebetween. Such an embodiment may be beneficial wherein the
piston housing includes an annular tubular configuration about the central
axis.
So as to preserve a general isolating integrity between the abutment
housing 40 and the piston housing 20, an exterior housing 46, which at
least partially contains the abutment housing 40 is provided. In
particular, the abutment housing 40 is preferably structured to rotate
through the exterior housing 46 when not passing through the piston
housing 20. As a result, the exterior housing 46 allows for effective
rotation of the abutment housing 40 through the piston housing 20, while
maintaining overall containment | | |
