HK1006190B

HK1006190B - Rotary vee engine

Info

Publication number: HK1006190B
Application number: HK98105355.1A
Authority: HK
Inventors: W. Sullivan Robert; Joe Holder Tommie; Franklin Buchanan Max
Original assignee: R Vec, Inc.
Priority date: 1988-02-03
Filing date: 1998-06-16
Publication date: 1999-04-16

Description

BACKGROUND OF THE INVENTION

The present invention relates to improvements in internal combustion engines and, more particularly, to improvements to internal combustion engines of the rotary vee type, such as described in U.S. Patent No. 4,648,358, issued March 10,1987 to the same inventors and entitled Rotary Vee Engine.

BRIEF DESCRIPTION OF THE PRIOR ART

In a conventional internal combustion engine, pistons reciprocate in cylinders formed in a stationary cylinder block and combustion within the cylinders is timed to cause the pistons to turn a crank shaft from which power is delivered from the engine. While engines of this type are the most common type of engine currently in use, it has been recognized that such engines are inherently subject to a problem that lowers the efficiency of the engine. In particular, the reciprocation of the piston involves a sequence of accelerations each piston from rest followed by a deceleration of each piston to rest. The work that is done on the pistons during these accelerations and decelerations is not recovered so that the energy, provided by the fuel used in the engine, necessary to perform this work results in an overall loss of efficiency of the engine.

Because of this loss of efficiency in a conventional engine, other types of engines have been considered as possible candidates for replacing the conventional engine. One such type of engine is the rotary vee engine which includes two cylinder blocks mounted in a housing for rotation about intersecting axes that are angled toward one side of the engine. Cylinders are bored into each of the cylinder blocks from the end which faces the other cylinder block and the engine is further comprised of a plurality of pistons, angled in the same manner so that the rotation axes of the cylinder blocks are angled, so that one portion of each piston can be extended into a cylinder in one cylinder block and another portion of the piston can be extended into a corresponding cylinder in the other cylinder block. Thus, as the cylinder blocks rotate, the pistons orbit about the rotation axes of the cylinder blocks to vary the free volumes of the cylinders in the cylinder blocks. This is, when a piston is on the side of the engine away from which the rotation axes of the cylinder blocks are angled, only a small part of each piston will extend into each of the cylinders, in the two cylinder blocks, in which the piston is mounted while major portions of each piston are disposed in the two cylinders in the two cylinder blocks when the piston is moved to a position at the side of the engine toward which the two rotation axes of the cylinder blocks are angled. Thus, compression and expansion of gases in the cylinders can take place with a continuous motion of both the cylinder blocks and the pistons to eliminate the loss of efficiency of a conventional engine, that has been described above.

In practice, the rotary vee engine has not lived up to the expectations that inventors have had for such engines. Because of the angled disposition of the rotating cylinder blocks and the firing of each cylinder at one side of the cylinder block, forces which tend to spread the two cylinder blocks into a straight line; that is, out of the vee configuration, are exerted on the cylinder blocks and such forces result in drag between the pistons and cylinder blocks that interferes with the operation and efficiency of the engine. Because of this problem, rotary vee engines have not enjoyed much success despite the promise that they hold and, indeed, it has been found that an engine constructed in the rotary vee configuration will often not even operate because of these problems that are inherent in the rotary vee configuration.

The rotary vee engine described in Patent No. 4,648,358 solves the basic problems that have plagued the rotary vee engine in the past and provides the operability that is necessary to exploit the advantages that are offered by engines of this type. As set forth in Patent No. 4,648,358, an operable rotary vee engine can be constructed by including in the engine an angled support shaft having portions that extend through the cylinder blocks along the axes of rotation of the cylinder blocks and having ends that are both supported by a housing in which the cylinder blocks are disposed. Bearings on the support shaft are located near each end of each cylinder block to transmit the forces that tend to spread the cylinder blocks out of the rotary vee configuration to the housing and thereby avoid any misalignment of the cylinder blocks that can, experience has shown, prevent the engine from operating. Other aspects of the engine which substantially improve on prior rotary engine designs are also described in Patent No. 4,648,358.

SUMMARY OF THE INVENTION

The present invention provides a rotary vee engine comprising:

a housing having outer ends;
two cylinder blocks each having inner and outer ends and mounted in the housing for rotation of one cylinder block about a first rotational axis and rotation of the other cylinder block about a second rotational axis, said axes being angled to intersect adjacent the inner ends of said blocks at an included angle less than one hundred and eighty degrees;
each cylinder block having a plurality of cylinders formed therein to intersect the inner end of the cylinder block and to extend therefrom into the cylinder block parallel to the rotational axis of the cylinder block;
a plurality of angled pistons each having a portion disposed in a cylinder of one block and a portion disposed in a cylinder in the other block for orbital motion of the pistons coordinately with the rotation of the cylinder blocks;
a central bore formed through each of the cylinder blocks along the rotational axis for the respective cylinder block;
an angled support shaft extending through the central bores of each cylinder block, the support shaft having portions supported by the housing and including means for rotatably and axially supporting each of the cylinder blocks on the support shaft;
a generally bent axis cylindrical wedge shaped central cavity formed by the housing between the inner ends of the cylinder blocks for receiving air/fuel mixture during the operation of the engine;
an exhaust cavity formed by the housing axially outwardly from the central cavity adjacent each cylinder block for receiving and discharging exhaust gases. created during the opertion of the engine;
a cooling air cavity formed by the housing adjacent the outer ends of each cylinder block; and
cooling air intake means defined in the outer ends of the housing in fluid communication with the adjacent cooling air cavity; characterised in that
the cooling air cavity includes a torus shaped chamber expanding in volume radially outwardly from the rotational axis of the adjacent cylinder block and terminating in a cooling air discharge port.

Preferred aspects of the present invention are given in claims 2 to 9.

Continuing developments in the rotary engine disclosed in Patent No. 4,648,358 have resulted in substantial modifications and improvements which enhance the utilization and operational characteristics of the engine. The invention makes provisions for the selective cooling of the exhaust gases by the cooling air, for environments where a substantially reduced temperature of the exhaust gases provides substantial operational advantages.

Features and advantages of the engine of the present invention will become clear from the following detailed description of the engine when read in conjunction with the drawings and appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGURE 1 is a top external plan view of a rotary vee engine constructed in accordance with this invention.

FIGURE 2 is an end view of the engine taken along the line 2-2 in FIGURE 1 showing the cooling air intake and the cooling air and exhaust portions of the housing.

FIGURE 3 is a partial elevational view of the engine as viewed along the line 3-3 showing the cooling air and exhaust manifolds.

FIGURE 4 is a view of the engine along the line 4-4 in FIGURE 2, showing the cylinder blocks in place with the top part of the engine housing removed.

FIGURE 5 is a sectional view of the end of the cylinder housing and cylinder block, as seen along the line 5-5 in FIGURE 4, shown with the top housing portion in place.

FIGURE 6 is a removed plan view of one embodiment of a piston incorporated into the engine.

FIGURE 7 is an elevational view, partly in section, showing the central shaft assembly and stuffer block incorporated into the engine.

FIGURE 8 is a cross-sectional view of the stuffer block and shaft assembly taken along the line 8-8 in FIGURE 7.

FIGURE 9 is an enlarged view of the engine as shown in FIGURE 4 with the cylinder blocks and hollow shafts of the shaft assembly shown in cross-section.

FIGURE 10 is an enlarged cross-sectional view of the left-hand cylinder block as shown in FIGURE 9, showing the arrangement of the pistons in the cylinder block and the mounting of the cylinder blocks on the support shaft.

FIGURE 11 is an enlarged cross-sectional view taken along the line 11-11 in FIGURE 10 showing the arrangement of the bearings for mounting the support shaft in the housing and for mounting the hollow shafts on the central solid shafts.

FIGURE 12 is a cross-sectional view of the engine similar to FIGURE 9 illustrating the oiling system incorporated in the engine in accordance with this invention.

FIGURE 13 is an elevational view, in partial section, of a light-weight and low inertial load piston which can be incorporated into the engine.

FIGURE 14 is a cross-sectional view of the left end of the engine, taken along the line 14-14 in FIGURE 15, illustrating the starter system which can be incorporated into the engine.

FIGURE 15 is a cross-sectional view of the engine starter system taken along the line 15-15 in FIGURE 14.

FIGURE 16 is a cross-sectional of one end of the engine illustrating the magneto system which can be readily provided to operate the spark ignition of the engine.

FIGURE 17 is a cross-sectional view of the engine taken along the line 17-17 in FIGURE 16.

FIGURE 18 is a cross-sectional view of one end of the engine illustrating the incorporation of an alternator in the engine for generating electrical power to operate the engine and/or to provide an auxiliary power source.

FIGURE 19 is a cross-sectional view of the engine taken along the line 19-19 in FIGURE 18.

FIGURE 20 is a removed partial sectional view taken along the line 20-20 in FIGURE 10, showing the conductor contacts included in the engine to fire the spark plugs.

FIGURE 21 is a cross-sectional view of the conductor contacts taken along the line 21-21 in FIGURE 20.

FIGURE 22 is a cross-sectional view, taken along the line 22-22 in FIGURE 10, showing the exhaust manifold portion of the engine.

FIGURE 23 is a sectional view of the exhaust manifold, taken along the line 23-23 in FIGURE 22.

FIGURE 24 is a timing diagram relating to the engine, showing the functions of the engine in relation to the rotational position of each piston.

FIGURE 25 is a cross-sectional view of the air/fuel intake manifold portion of the engine, taken along the line 25-25 in FIGURE 10.

FIGURE 26 is a partial plan view of a cylinder sleeve in the engine illustrating the preferred arrangement for the intake and exhaust ports.

FIGURE 27 is a cross-sectional view of the cylinder sleeve taken along the line 27-27 in FIGURE 26.

FIGURE 28 is a perspective view of the end of the piston illustrating the preferred arrangement for the rotary valving head provided on the end of each piston in accordance with this invention.

FIGURE 28A is a top view of the piston head shown in FIGURE 28.

FIGURE 28B is a side view of the piston head as viewed along line 28B-28B in FIGURE 28A.

FIGURE 28C is a side view of the piston head as viewed along the line 28C-28C in FIGURE 28A.

FIGURE 28D is a side view of the piston head as viewed along the line 28D-28D in FIGURE 28A.

FIGURE 28E is a side view of the piston head as viewed along the line 28E-28E in FIGURE 28A.

FIGURE 29A is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly in accordance with this invention shown at the initial stages of the intake and supercharging portion of the engine cycle.

FIGURE 29a is a cross-sectional view taken along the line 29a-29a in FIGURE 29A.

FIGURE 29B is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown at the conclusion of the compression portion of the engine cycle.

FIGURE 29b is a cross-sectional view taken long the line 29b-29b in FIGURE 29A.

FIGURE 29C is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown at the ignition point of the engine cycle.

FIGURE 29c is a cross-sectional view taken along the line 29c-29c in FIGURE 29C.

FIGURE 29D is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown during the power stroke of the engine.

FIGURE 29d is a cross-sectional view taken along the line 29d-29d in FIGURE 29D.

FIGURE 29E is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown during the continuing stages of the power stroke and the initial stages of the exhaust portion of the engine cycle.

FIGURE 29e is a cross-sectional view taken along the line 29e-29e in FIGURE 29E.

FIGURE 29F is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown during the ending stages of the power stroke and the continuing stages of the exhaust portion of the engine cycle.

FIGURE 29f is a cross-sectional view taken along the line 29f-29f in FIGURE 29F.

FIGURE 29G is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly shown during the initial stages of the scavenging portion of the engine cycle.

FIGURE 29g is a cross-sectional view taken along the line 29g-29g in FIGURE 29G.

FIGURE 29H is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly showing the final stages of the scavenging portion of the engine cycle.

FIGURE 29h is a cross-sectional view taken along the line 29h-29h in FIGURE 29H.

FIGURE 29I is a removed partial sectional view of the combustion chamber portion of a cylinder and piston assembly showing the return cf the engine to the intake and supercharging portion of the engine cycle, as shown in FIGURE 29A.

FIGURE 29i is a cross-sectional view taken along the line 29i-29i in FIGURE 29I.

DETAILED DESCRIPTION OF THE DRAWINGS

The engine 100 illustrated in the drawings is a twelve cylinder engine incorporating several modifications and improvements, in the engine illustrated in Patent No. 4,648,358, as will be described in detail hereinbelow.

The engine 100 includes a split housing 200 which is formed from two cast aluminum sections. As seen in FIGURE 2, the upper housing section 202 and the lower housing section 204 are fastened together by means of flanges provided along the mating edges of the housing sections. Only the lower housing section 204 is shown in FIGURES 4 and 9. Each housing section 202 and 204 also defines end sections which are positioned at a selected angle and joined at the center line C of the engine 100. Where appropriate, the left end sections of the housing 202 and 204 are designated 202L and 204L, and the right end sections are designated 202R and 204R, respectively. The left housing section L is essentially a mirror image of the right housing section R of the same housing section 202, 204. The left housings define a central axis of rotation A_L, and the right housings likewise define a central axis of rotation A_R. The axes of rotation intersect at a selected angle X along the center line C of the engine 100. Angle X is less than 180° and greater than 90°.

As seen in FIGURES 1 and 4, each housing section 202, 204 is formed to define a series of internal cylindrical cavities of differing shapes and diameters when the upper and lower housing sections are joined. Accordingly, the outer end of each housing end section (202L, 202R, 204L and 204R) provides an enlarged semicircular cavity 206. When the upper and lower housing sections are joined, the cavities 206 mate to form a cylindrical air cooling chamber at each end of the engine 100. The air cooling chamber formed by the mating cavities 206 receives a major portion of the cylinder head assembly of the engine 100, as described further below.

As shown in FIGURE 2, and as further described in detail in Patent No. 4,648,358, the outer ends of each housing section 202 and 204 also include a semicircular opening 208 concentric with the respective housing axes A_L and A_R. When the housing sections are joined together the openings 208 form an annular air intake port through which cooling air can be drawn axially into each cavity 206 in the ends of the engine by the rotary action of the cylinder assemblies in the housing 200. Adjustable louvers 207, as seen in FIGURE 2, are provided in each of the openings 208 to allow the volume of the intake of cooling air to be adjustably controlled. These louvers 207 can be adjusted manually or through some remote or automatic means, not shown.

The cooling air which is drawn in axially through the openings 208 in the housing 200 is directed radially outward by the rotary motion of the cylinder blocks. A substantial centrifugal force is thereby imparted to the cooling air. As seen in FIGURES 9 and 10, the cylinder blocks are provided with spaced radial fins, openings between the cylinders in the cooling chamber 206, and an annular central chamber. As a result of this construction, the radial air flows by and cools the cylinders provided in the cylinder blocks by moving outwardly between the cooling fins, and thereby dissipates the heat created by the operation of the engine 100. As seen in FIGURES 2 and 3, the housing sections 202, 204 in this cooling section of the engine are cast to define an expanding torus-shaped air chamber 205 to direct the cooling air in an expanding volume to a cooling air discharge port 209. The air outlet port 209 allows the cooling air to be discharged from the air cooling cavity 206 into the surrounding atmosphere. Adjustable louvers 209L, as shown in FIGURE 3, can be provided in the air outlet port 209 to allow further control over the flow of the cooling air through the engine 100.

The intermediate portion of each housing section 202, 204 also defines an exhaust ring 210 in the housing 200. The exhaust ring made up of the mating cavities 210 is in fluid communication with the exhaust ports in each cylinder of the engine 100. As shown in FIGURES 2, 3 and and 23, the exhaust ring 210 is adjacent the cooling air chamber 206 and has a similar expanding torus shape to facilitate the removal of the exhaust gases from the engine. The exhaust ring 210 also includes an outlet opening 211 in the wall of the housing which leads to a suitable exhaust manifold. The exhaust ring in each engine section 202, 204 thus functions to collect the exhaust gases from each adjacent cylinder during the operation of the engine.

A divider wall 213 can be provided in the housing 202L to separate the discharging cooling air from the exhaust gases. This arrangement is particularly appropriate when the cooling air chamber 210 is provided with the adjustable louvers 209L. If desired for particular engine applications, the divider wall 213 can be eliminated so the exhaust gases are mixed with and are cooled substantially by the exiting cooling air. A second smaller divider wall 217 is also formed in the exhaust chamber 210 to block the exhaust gases from the inner portions of the engine containing the air/fuel mixture. (See FIGURE 23).

The exhaust cavity 210 in each engine section 202, 204 is sealed from the inner ends of each engine section by a sealing ring 212. Each ring 212 is positioned within the respective housing section 202, 204 on the outside of a roller bearing 216. The bearings 216 function to stabilize the rotation of inner end of the adjacent cylinder block within the housing 200, as described further below. The seals 212 function to create a seal between the adjacent rotating cylinder block and the housing 200, to prevent the exhaust gases from moving further inwardly between the cylinder block and the housing toward the center line C of the engine 100.

The central portion of the housing sections 202, 204 between the bearings 216, and centered in the center line C, defines a bent axis cylindrical wedge-shaped chamber 218 into which air fuel mixture is supplied to the engine 100. The seals 212 and the divider wall 217 operate to seal the exhaust ring portion 210 of the engine from this air-fuel chamber 218.

The side 220 of the housing 200 toward which the axes A_L and A_R are angled (the top side in FIGURE 1) comprises the top-dead-center side for the engine 100. The opposite side 222 (the lower side in FIGURE 1) comprises the bottom-dead-center side. Each piston 600 in the engine 100 is fired a few degrees of rotation in advance of reaching the top-dead center side 220 during the operation of the engine. Accordingly, the outer end of each housing section 202 and 204 include a spark plug contactor assembly 224 positioned closely adjacent the top-dead center side 220. As shown in FIGURES 20 and 21, the contactor assembly 224 comprises an insulator sleeve 226 extending through the outer end of each housing section 202, 204 slightly below the flanges provided to join the two housing sections together. An electrical conductor 228 extends through the insulator sleeve 226 and terminates in an arcuate electrical contact 230. The conductors 228 and contacts 230 are connected to an ignition system, such as magneto system (See Figs. 14 and 15) which produces a timed high-voltage spark to fire the spark plugs on the associated cylinder block assembly as the plugs are sequentially rotated into close proximity to the contacts 230. The spark plug contactor assemblies 224 and the ignition system are arranged so that the spark plugs fire slightly in advance of the top-dead center position for both cylinders and assemblies are fired simultaneously. As seen in FIGURES 20 and 21, this advanced spark arrangement is caused by providing each electrical contact 230 with a selected arcuate length, so that each rotating spark plug S is in a position to be energized by the contact 230 a selected degree 'Y' in advance of reaching the top dead center position.

As seen in FIGURES 4 and 9, the left housing portions 202L, 204L house a cylinder block 250L, and the right housing portions 202R, 204R likewise houses a cylinder block 250R. The cylinder blocks 250L, 250R are mirror images of each other. Hence, identical features and components have been designated by the same reference numerals. Each cylinder block 250L, 250R is generally cylindrical in shape, and includes an interior end positioned adjacent the center line C of the engine 100 when the engine is assembled in the housing 200. The exterior end of each of the cylinder blocks 250L, 250R is positioned adjacent the outer ends of the housing 200, as shown in FIGURE 4. The left cylinder block 250L is centered about the rotational axis A_L and the right cylinder block 250R is centered about the rotational axis A_R.

As further seen in FIGURES 4 and 9; the interior end of each of the cylinder blocks 250L and 250R includes an annular beveled surface 252 defined in the outer radial portion of the cylinder blocks. The beveled surfaces 252 on the cylinder blocks 250L, 250R are axially spaced by a substantial distance at the bottom-dead-center side 222 of the engine. In contrast, the two beveled surfaces 252 are in a close sealing relationship at the top-dead-center side 220 of the engine. The parts are machined to allow for heat expansion so that the beveled surfaces 252 do not bind at this top-dead-center side 220. In operation the surfaces 252 rotate approximately a few thousandths of an inch apart at the top-dead-center side 220. The surfaces 252 will thereby form an effective seal which will assist in containing the air/fuel mixture in the central chamber 218 of the engine housing 200. A second annular surface extends radially inwardly from the beveled surface 252 toward the center of rotation of each cylinder block 250L, 250R.

As shown in FIGURE 9, the second annular surface is a multiple-stepped surface, including the steps 256 and 258. The stepped surfaces 256,258 are designed to receive complimentary stepped surfaces 502 and 504, respectively, on the end of a stuffer block 500 positioned in the center of the engine 100, as shown in FIGURES 7 and 8. The mating stepped surfaces on the cylinder blocks 250L, 250R and stuffer block 500 will operate to impede the escape of air/fuel mixture from the central portion of the engine 100. The complementary stepped surfaces are spaced sufficiently close to prevent any substantial gas flow, but are spaced apart sufficiently so that heat expansion will not cause binding of the cylinder blocks and stuffer block 500 during the operation of the engine 100.

The exterior end of each cylinder block 250L and 250R includes an central opening 260 whiah provides the exterior end of each block with an annular opening. A plurality of coaxial rings 262 on the annular exterior end of the cylinder blocks and the annular interior of the opening 260 provide air cooling surfaces and pathways for the cylinder blocks during the operation of the engine. To accomplish this arrangement, the cylinder blocks 250L and 250R are cast to provide radial openings between the rings 262 in the portions of the blocks between the cylinder and piston assemblies.

As seen in FIGURES 4 and 23, a portion of each cylinder block 250L, 250R is formed to define an exhaust chamber 270 for each engine cylinder 300. Each chamber 270 is axially aligned with radially inward exhaust ports 302 in each cylinder 300, so that the spent combustion gases are directed from each cylinder in a radially inward direction into the associated chamber 270. As seen in FIGURE 22, the exhaust chambers 270 are then curved to extend in an arcuate and expanding fashion to the periphery of the cylinder block 250L, 250R between the cylinders 300. The chambers 270 are thereby placed into fluid communication with an adjacent exhaust cavity 210 of the housing 200, which in turn is in communication with an exhaust manifold, not shown. The operation of the engine maintains the exhaust gases under pressure so that the gases, which were initially directed radially inward, are rapidly redirected in a radially outward direction from the exhaust chambers 270 into the exhaust cavities 210 in the housing 200, and then out through the exhaust manifold.

The interior ends of each cylinder block 250L, 250R are cast to provide the cylinder block with an axially and radially extending cavity that defines an air/fuel intake manifold 280 for each cylinder 300A-F. As shown in FIGURES 9, 10 and 25, each manifold 280 is provided with evenly spaced axial fins 282 which assist in imparting a substantial rotational and centrifugal force.to the air/fuel mixture passing through each manifold 280.

The interior ends of each manifold 280 are positioned toward the centerline C of the engine. The interior ends of each manifold 280 are open so that each manifold is in fluid communication with the air/fuel chamber 218 defined in the central portion of the housing 200. Each manifold 280 continues radially outwardly past the adjacent cylinder, and then extends axially outwardly along the cylinder. The manifold 280 thereby defines an outer air/fuel inlet chamber portion 284 that is positioned radially outwardly of each cylinder 300. Each inlet chamber 284 is in direct fluid communication in a radially inward direction with an air/fuel inlet port 304 provided in each cylinder 300. The air/fuel mixture is directed, by pressure forces created by the rotation of the cylinder blocks, from the central air/fuel chamber 218 into the manifolds 280. The fins 282 in the manifolds 280 impart additional velocity to the air/fuel mixture so that the mixture is forced radially outward under high pressure into the inlet chambers 284. The air/fuel mixture is thereby positioned radially outwardly of the engine cylinders 300. This air/fuel charge is subjected to a supercharged pressure which is sufficient to overcome the centrifugal forces working on the charge in order to force the charge into the engine cylinders 300 through the associated intake ports 304.

As seen in FIGURES 7 and 9, the stuffer block 500 is a cast member, made from lightweight aluminum or other suitable material, such as a light-weight plastic. In the preferred arrangement, the stuffer block 500 is formed or cast in place on the solid shafts 402L and 402R, at the vee-shaped junction of the shafts, as shown in FIGURE 7. The left and right faces of the stuffer block 500 are formed to have a cylindrical configuration which includes the above-described steps 502 and 504. The central body of the stuffer block is formed in the shape of two intersecting truncated cylinders 506L and 506R, which provide the central portion of the stuffer block 500 with a generally wedged shape.

As shown in FIGURE 9, the stuffer block 500 is designed to be positioned within the central space 218 of the engine 100 between the rotating cylinder blocks 250L and 250R and inside of the rotating pistons 600. The portions 506L and 506R of the stuffer block are dimensioned so that they extend between the cylinder blocks 250L and 250R. The periphery of the stuffer block 500, on the side adjacent the top dead center side 220 of the engine, is provided with a bent-axis cylindrical and wedge-shaped cavity 510. This cavity is in fluid communication with the central opening 218 defined in the housing and is adapted to receive the air/fuel mixture being fed into the engine 100 through a suitable carburetor inlet 210 (see FIGURE 1). As shown in FIGURE 8, this cavity 510 extends transversely from the periphery of the stuffer block 500 past the central portion of the stuffer block. A pair of axial and arcuately shaped passageways 508L and 508R are provided in the stuffer block to bring the cavity 510 into fluid communication, in an axial direction along the length of the shafts 402L and 402R, with the air/fuel manifolds 280 defined in each of the rotating cylinder blocks 250L, 250R.

The stuffer block 500 and the solid shafts 402L and 402R are stationary during the operation of the engine. As seen in FIGURE 9, the dimensions of the stuffer block place the block centrally in the engine 100 so that the pistons 600 orbit around the stuffer block within the central engine cavity 218. Because of this arrangement, air/fuel mixture directed into the stuffer block cavity 510 from a carburetor system will be compressed and supercharged in the cavity 510 by the rotary action of the cylinder blocks 250L, 250R and the orbiting action of the pistons 600 within the central chamber 218. This supercharged air/fuel mixture will then be directed axially out of the chamber 510 into the air/fuel manifolds 280 in each cylinder block 250L, 250R through the passageways 508L, 508R. The manifolds 280 then conduct the supercharged air/fuel mixture into the engine cylinders, as described further below.

Each cylinder block 250L and 250R includes six cast-in-place cylinder sleeves 300A through 300F. As shown in FIGURE 5, these sleeves 300A-F are uniformly spaced in an annular arrangement around the axis of rotation A_L and A_R of the cylinder blocks. Each cylinder sleeve 300 is preferably integrally cast within the cylinder block during the aluminum casting operation. The interior end of each cylinder sleeve 300 is beveled, so that the interior end of each sleeve will be in alignment with the beveled surface 252 on the respective cylinder block 250L, 250R, as shown in FIGURE 9. Each sleeve 300 is axially aligned to be parallel to the respective axis of rotation A_L or A_R of the cylinder block 250L or 250R. The sleeves 300A-F are further positioned so that the sleeve 300A in cylinder block 250L intersects with sleeve 300A in block 250R along the centerline C when the sleeves are positioned at the top-dead center side 220 of the engine. Moreover, each sleeve 300A-F in cylinder block 250L is axially aligned with the corresponding sleeve 300A-F in the other cylinder block 250R along centerlines which are parallel to the angled axes of rotation A_L and A_R. Due to this alignment, the centerlines of the aligned sleeves 300A-F in cylinder 250L would intersect with the centerlines of the sleeves 300A-F in cylinder 250R at the engine centerline C. This alignment is maintained through the rotation of the cylinder blocks 250L, 250R during the operation of the engine.

Each of the aligned cylinder sleeves 300A-F is provided with a piston member 600 (see FIGURES 6 and 9). A solid embodiment for the piston 600 is shown in FIGURE 6. The head or outer ends 602L and 602R have a specifically programmed shape, as explained in more detail below, so that the heads 602L, 602R function as rotary valves during the operation of the engine. One or more piston rings 620 are provided in the piston adjacent each head 602 to seal the compression/ignition chamber defined at the ends of the piston in the conventional manner. The intermediate portion of each piston 600 is also provided with a pair of spaced sealing rings 630. These rings 630 function to seal each end of each piston and cylinder sleeve combination from the central air/fuel chamber 218 of the engine 100. The rings 630 also act as oil wiper and sealing rings to prevent the leakage of lubricating oil into the air/fuel chamber 218.

Alternatively, the functions of the piston rings 630 can be performed by a seal 640. As seen in FIGURES 9 and 10, the seal 640 is an O-ring type seal mounted in the interior wall of each cylinder 300 adjacent the inner end of the cylinder. In FIGURE 13 an angled positon 600A comprises a hollow tubular piston body 680L connected at a selected angle to a second hollow piston body 680R. The bodies 680L,R can be formed by boring out a solid piston rod to have a selected wall thickness which is uniform throughout the axial length of the piston. A wall thickness in the range of one-eighth to three sixteenths of an inch (0.3175 cm to 0.47628 cm) has been found sufficient to withstand the forces applied to the piston in the engine. As seen in FIGURE 13, the outer end of each piston body is open. The resulting hollow piston 600A has a low weight and mass.

The piston 600A further includes a piston head 602L fixed in the open outer end of the body 680L and a similar piston head 602R fixed in the open end of the body 680R. Each head includes piston rings 620, as described above. As further described above, each piston can also be provided with the second set of piston rings 630 as shown in FIGURE 6. A wrist pin 640, or other suitable means such as threads, can be used to secure the piston heads to the adjacent piston body.

Since the piston bodies 680L,R are hollow, the weight and mass of the piston 600A is substantially reduced. The centrifugal force and inertial loads on the piston are accordingly reduced so that the bearing loads between the piston and the cylinder sleeve are minimized. The resultant wear between the piston and the associated cylinder sleeve is thereby likewise minimized.

The cylinder sleeves 300A-F terminate near the exterior end of the cylinder blocks 250L, 250R. As seen in FIGURE 9, cylinder heads 310 are formed in the ends of the cylinder blocks 250L, 250R in axial alignment at the outer end of each sleeve 300A-F. A spark plug S is provided in each cylinder head 310 and arranged in the conventional manner so that the spark-gap end of the plug extends into the interior of the associated cylinder sleeve 300A-F. The external end of each spark plug S is positioned to rotate into close conductive relationship to the fixed electrical contact 230. As shown in FIGURES 20 and 21, each contact 230 has an arcuate shape that is positioned to be in close relationship (i.e., by a gap of 0.030 inches) to the rotating spark plugs S. The arc of the contact 230 extends from an advanced point, e.g., twenty-five degrees before the top dead center 220 of the engine. The plugs S therefore rotate with the cylinder blocks 250L, 250R, and are fired a few degrees of rotation before the top-dead-center side 220 of the engine by electrical conduction from the contacts 230.

The engine 100 also includes an angled support shaft assembly 400. The assembly 400 supports the cylinder blocks 250L, 250R for rotation within the housing 200 and provides the engine 100 with dual power output shafts. The left-hand end of the shaft assembly 400 includes a solid support shaft portion 402L, and the right hand end likewise includes a solid support shaft portion 402R. Each shaft portion 402L, 402R is concentric with the respective axis of rotation A_L, A_R of the related cylinder block 250L, 250R.

In the preferred embodiment, the shaft portions 402L, 402R comprise a solid shaft that is pre-bent to the desired angle. As shown in FIGURE 7, stuffer block 500 is cast or otherside formed onto the central portion of the bent shaft portions 402L, 402R and machined to the proper angle and configuration. The shaft portions 402L, 402R and the stuffer block 500 thereby form a solid one-piece support shaft structure which will resist the thrust and bending forces created by the operation of the engine 100. The interior end of each shaft 402L, 402R includes a slightly enlarged portion that receives a roller bearing 404.

As seen in FIGURES 4 and 9, the solid shafts 402L, 402R extend outwardly to the ends of the respective housing 202L or 202R, so that the ends of the shafts 402L, 402R will be supported by the housings 200. The outer end of each support shaft 402L, 402R also includes a reduced-diameter portion which will receive a combined roller and thrust bearing 406.

The shaft assembly 400 also comprises a pair of hollow output shafts 412L and 412R. As shown in FIGURES 4, 9 and 11, the hollow shaft 412L is positioned over and concentric with the solid shaft 402L, and the hollow shaft 402R is positioned over and concentric with the solid shaft 402R. In the preferred arrangement the hollow shafts 412L, 412R are fixed to the associated cylinder blocks 250L, 250R by being cast or formed in place when the aluminum cylinder block is cast. The hollow shafts 412L, 412R are positioned in the blocks 250L, 250R to be parallel to the cylinder sleeves 300A-F and concentric with the respective rotational axis A_L or A_R.

The inner ends of the hollow shafts 412L, 412R are closely adjacent the stuffer block 500, and include bearing recesses 414. As shown in FIGURE 9, the bearings 404 are press-fit into the recesses 414 so that the bearings 404 are carried by the hollow shafts 412L, 412R. A ring seal 405 is also carried by the shafts on the inside of the bearings 404 to seal against the stuffer block 500. The interior ends of the cylinder blocks 250L, 250R and the hollow shafts 412L, 412R can thereby rotate around the solid shafts 402L, 402R on the bearings 404. Since bearings 404 are press-fit into the recesses 414 they are restrained from axial movement by friction and by a shoulder defined on the shafts 412L, 412R by the recesses 414. The bearings 404 are also restrained from inward movement by the stuffer block 500.

The exterior ends of the hollow shafts 412L, 412R extend outwardly beyond the ends of the solid shafts 402L, 402R and beyond the ends of the housing 200. The combined roller and thrust bearing 406 is press-fit into an internal bearing recess 416 on the exterior end of each of the hollow shafts 412L, 412R, as clearly shown in FIGURE 11. A shoulder formed by the recess 416 prevents inward movement of the bearing 406 and transfers thrust loads to the bearing. Outward movement of the bearings is precluded by retaining plate 408 bolted to the shafts 402L, 402R by a bolt 410. The bearings 406 thus support the exterior end of the hollow shafts 412L, 412R and the associated cylinder blocks 250L, 250R for rotation about the solid shafts 402L, 402R. The bearings 406 transfer and absorb the axial thrust loads applied to the cylinders 250L, 250R and the hollow shafts 412L, 412R during the operation of the engine 100.

As seen in FIGURES 9-11, the bearings 244 in each end of the housing 200 rotatably support the hollow drive shafts 412L, 412R, and the drive shaft assembly 400 on the housing 200. As described above, a shoulder 418 on the hollow shafts 412L, 412R will transmit any outward thrust load to the bearings 240, 244. Similarly, a sleeve 420 pinned to the outer portions of the hollow shafts 412L, 412R will transmit any inward thrust loads to the bearings 244. The bearings 244 are thereby arranged to absorb any thrust loads transmitted to the housing in either direction by external loads created by the operation of the engine.

The operation of the engine 100, and the resulting rotation of the cylinder blocks 250L, 250R creates a rotary output driving force through the connected hollow shafts 412L, 412R. Since both shafts 412L and 412R extend beyond the housing 200, the engine 100 is thereby provided with dual output drive shafts, with one drive shaft at each end of the housing.

The dual output shafts 412L and 412R provide the engine 100 with substantial versatility. One output shaft can be employed as the main output, to drive a transmission or the like. The other output shaft can be used simultaneously to power auxiliary equipment, such as a generator or the like. Alternatively, the two shafts 412L and 412R can be coupled to similar transmissions, to drive similar components, such as two separate drive wheels.

Claims

A rotary vee engine comprising:
a housing (200) having outer ends;

two cylinder blocks (250R, 250L) each having inner and outer ends and mounted in the housing (200) for rotation of one cylinder block about a first rotational axis and rotation of the other cylinder block about a second rotational axis, said axes being angled to intersect adjacent the inner ends of said blocks at an included angle less than one hundred and eighty degrees;

each cylinder block (250R,250L) having a plurality of cylinders formed therein to intersect the inner end of the cylinder block and to extend therefrom into the cylinder block parallel to the rotational axis of the cylinder block;

a plurality of angled pistons (600) each having a portion disposed in a cylinder of one block and a portion disposed in a cylinder in the other block for orbital motion of the pistons coordinately with the rotation of the cylinder blocks;

a central bore formed through each of the cylinder blocks along the rotational axis for the respective cylinder block;

an angled support shaft (400) extending through the central bores of each cylinder block, the support shaft having portions supported by the housing (200) and including means for rotatably and axially supporting each of the cylinder blocks (250R,250L) on the support shaft;

a generally bent axis cylindrical wedge shaped central cavity (128) formed by the housing between the inner ends of the cylinder blocks for receiving air/fuel mixture during the operation of the engine;

an exhaust cavity (210) formed by the housing (200) axially outwardly from the central cavity (128) adjacent each cylinder block (250R,250L) for receiving and discharging exhaust gases created during the operation of the engine;

a cooling air cavity (206) formed by the housing adjacent the outer ends of each cylinder block; and

cooling air intake means (208) defined in the outer ends of the housing (200) in fluid communication with the adjacent cooling air cavity characterised in that

the cooling air cavity includes a torus shaped chamber expanding in volume radially outwardly from the rotational axis of the adjacent cylinder block and terminating in a cooling air discharge port (209).
A rotary vee engine in accordance with claim 1 wherein the cooling air discharge port (209) includes adjustable louver means (209L) for controlling the flow of air discharging from the cooling air cavity (206).
A rotary vee engine in accordance with claim 1 or claim 2 wherein the cooling air intake means (208) further includes adjustable louver means (207) for controlling the flow of air entering the cooling air cavity (206).
A rotary vee engine in accordance with any one of the preceding claims wherein the cooling air intake means (208) comprises generally annular cooling air intake ports (208) formed in each outer end of the housing in direct fluid communication with the adjacent air cooling cavity (206).
A rotary vee engine in accordance with any one of the preceding claims wherein the exhaust cavity (210) comprises a torus shaped chamber formed by the housing adjacent the cooling air cavity (206) expanding in volume radially outwardly from the rotational axis of the adjacent cylinder block (250R,250L) and terminating in an exhaust discharge port.
A rotary vee engine in accordance with claim 5 wherein the adjacent torus shaped air cooling (206) and exhaust (210) chambers form a unitary torus chamber and the housing includes wall means (213) extending radially inward to divide the air cooling chamber (206) from the adjacent exhaust (210) chamber.
A rotary vee engine in accordance with claim 6 wherein the housing further includes second wall means (217) extending radially inward to divide the exhaust chamber (210) from the air/fuel cavity of the engine.
A rotary vee engine as claimed in any one of the preceding claims comprising cylinder block bearing means (216) positioned between the housing (200) and each cylinder block (250L,250R) to further support the inner ends of the cylinder blocks (250L,250R) for rotation within the housing (200) during the operation of the engine.
A rotary vee engine according to claim 8 further including sealing means (212) positioned between the housing (200) and the cylinder blocks (250L,250R) in the proximity of the cylinder block bearing means (216) to assist in sealing the exhaust chamber (210) from the air/fuel cavity of the engine.