US3312200A - Energy converter - Google Patents

Description

April 4, 1967 c. F. BENSON ENERGY CONVERTER 4 Sheets-Sheet 1 Filed Aug. 21, 1964 m M 1m 1 mw w H T 8 EH B .1 Q F N 7 ili vb 4|? L Y 0m 3 Q. C E o: fi mm or S P A d HHH I I 45 m9 w: 8 mw O 3 9 t M Q @Q mv a ,1 8 o: mm E E on. 2 v s mm w/v @2 Saw, 5m 5m Q? N: a Q Lam F a 5 W Q km E 02 v 3% 5 43: y 8 W W m F? 4 NF o2 0* F m N 3 MN m 5 April 4, 1967 c. F. BENSON ENERGY CONVERTER 4 Sheets-Sheet 2 Filed Aug. 21, 1964 INVENTOR CARL F Benson April 4, 1967 c. F. BENSON ENERGY CONVERTER 4 Sheets-Sheet 5 Filed Aug. 21, 1964 ATTORNEYS April 4, 1967 c. F. BENSON ENERGY CONVERTER 4 Sheets-Sheet 4 Filed Aug. 21. 1964 United States Patent Oflfice 3,312,200 Patented Apr. 4, 1967 of Maine Filed Aug. 21, 1964, Ser. No. 391,167 19 Claims. (Cl. 12311) This invention relates to a noval energy converter, and in particlular, to a novel rotary engine and/ or compressor including a plurality of pistons rotatable about an axis of a floating pivot pin eccentric to a main shaft and driveably connected to the main shaft by a cylinder whereupon rotation of the pistons drives the shaft through the cylinder or alternatively, rotation of the shaft drives the pistons.

An object of this invention is to provide a noval energy converter including a housing having a cylindrical bore, a cylinder rotatably mounted within the bore, a plurality of pistons rotatable relative to the cylinder about an axis of a floating pivot pin, a main shaft, drive means coupling the pistons to the shaft, and the floating pivot pin axis about which the pistons travel being eccentric relative to the main shaft axis whereupon rotation of the pistons the main shaft is driven through the drive means.

A further object of this invention is to provide a novel energy converter including a cylinder rotatably mounted in a bore of the energy converter housing, a plurality of pistons in the cylinder, adjacent pairs of the plurality of pistons defining a chamber, a main shaft, means journalling the main shaft for rotation, a floating pivot pin central to the pistons, a pair of axially spaced plates carried by the shaft, the floating pivot pin being positioned between the plates in eccentric relationship relative to the axis of the main shaft and in concentric relationship relative to the bore and the cylinder, each of the pistons being axially confined between the plates and radially confined between the cylinder and the floating pivot pin, and means driveably coupling the plates to each of the pistons whereby movement of the pistons imparts rotation to the main shaft through the coupling means and limited rotation of the cylinder relative to the pistons.

Still another object of this invention is to provide a novel energy converter of the type immediately described above, in which the coupling means comprise an elongated slot in each of the pistons, the axis of each slot being directed generally normally toward the axis of the floating pivot pin and a pin passing through each slot and connected to the axially spaced plates.

A further object of this invention is to provide a novel energy converter including each of the elements set forth above and further including means in one of the plates for introducing fluid media axially into the chambers, and means in another of the plates for withdrawing fluid media axially from the chambers.

Yet another object of this invention is the provision of a novel energy converter of the type described in which means are provided for igniting the fluid media in a selected one of the chambers.

A further object of this invention is to provide a novel energy converter combination including an engine unit and a compressor unit, each of the units including housing means provided with a bore, a plurality of pistons in each of the bores, adjacent pairs of the plurality of pistons defining fluid media receiving chambers, rotatable main shaft means, means coupling the pistons of each unit to the shaft means, a member at each bore defining an axis of rotation about which the pistons travel, the axes of the members being eccentric relative to each other and to the axis of the shaft means whereby the pistons of the units rotate out of phase, and means for placing selected ones of the engine unit and the compressor unit chambers in fluid communication.

A further object of this invention is to provide a novel energy converter combination of the type defined in which the last mentioned means include a plurality of intake and exhaust ports opening axially into the engine and compressor chambers, means for sealing the ports against the escape of fluid media during compression and/or expansion of the fluid media in selected ones of the engine and compressor chambers, and ignition means for igniting fluid media introduced into a selected one of the engine unit chambers, and means for supplying fluid media into another selected one of the engine chambers.

With the above and other objects in view that will hereinafter appear, the nature of the invention will be more clearly understood by reference to the following detailed description, the appended claims and the several views illustrated in the accompanying drawings.

In the drawings:

FIGURE 1 is a fragmentary longitudinal sectional view partially in side elevation of a novel energy converter constructed in accordance with this invention, and illustrates an engine unit and a compressor unit, each unit including a plurality of pistons housed between a floating pivot .pin and a rotatable cylinder and axially defined between a pair of axially spaced rotor plates carried by a shaft, drive pins connecting the pistons to the plates, and valve porting means for introducing fluid media into and exhausting fluid media from chambers defined between adjacent ones of the pistons.

FIGURE 2 is a sectional view taken along line 22 of FIGURE 1 and clearly illustrates the pistons and chambers of the engine unit and a driving pin passing through a slot in each of the pistons.

FIGURE 3 is a sectional view taken along line 3-3 of FIGURE 1 and illustrates the pistons and chambers of the compressor unit, and a slot in each of the pistons receiving an associated one of the driving pins connected between the axially spaced plates.

FIGURES 4-A, 4-H and 4-C are reduced schematic views taken substantially along line 4-4 through the engine unit of FIGURE 1, and sequentially illustrate 0, 60 and degrees of rotation of the engineunit pistons, and the exhaust valve porting of the engine unit.

FIGURES 5-A, 5-B and 5-C are schematic reduced sectional views taken along line 55 of FIGURE 1 and illustrate the intake valve porting of the engine unit at O, 60 and 90 degrees of revolution of the engine unit pistons.

FIGURES 6-A, 6B and 6-C are schematic sectional views taken substantially along line 6-6 through the engine unit of FIGURE 1, and sequentially illustrate the position of the compressor pistons and chambers at O, 60 and 90 degrees of rotation, and the exhaust valve porting of the compressor unit.

FIGURES 7-A, 7-13 and 7-C are reduced fragmentary schematic sectional views taken along line 7-7 of FIG- URE 1, and illustrate the intake valve porting of the compressor unit at 0, 60 and 90 degrees of rotation and a generally cylindrically shaped compressor housing portion 16 (FIGURE 3) provided with a similar cylindrical bore 17. The housing portions 14 and 16 and the respective cylindrical bores 15, 17 thereof are positioned on opposite sides of acentral housing portion 18 (FIG- URE 1) of the housing 13. The central housing portion 18 includes a cylindrical bore 20 in axial alignment with a cylindrical bore 21 of a face plate 22 secured to the engine housing portion 14 by a plurality of bolts 23 (PEG- URE 2) in the manner clearly illustrated by the bolt 23 of FIGURE 1. The cylindrical bore 2%) is similarly in axial alignment with a cylindrical bore 24 in a face plate 25 secured to the compressor housing portion 16 by a plurality of bolts 26 (FIGURE 3), in a manner clearly illustrated by the single illustrated bolt 26 in FIGURE 1.

The engine unit 11 contains a cylindrical sleeve or race 27 (FIGURE 2) positioned in the cylindrical bore 15 of the engine housing 14. A radially innermost circumferential surface 28 of the sleeve 27 forms an outer raceway for a plurality of rollers 30 maintained in spaced parallel relationship by a bearing cage 31. A radially outermost circumferential surface 32 of a cylindrical sleeve or cylinder 33 forms an inner raceway for the rollers 30, as is best illustrated in FIGURE 2 of the drawings.

Three pie-shaped annular se ments or pistons 34, 35 and 36 are mounted in the engine unit between the cylinder 33 and a floating pivot pin or member 37, as is best illustrated in FIGURE 2 of the drawings. The pistons 34-36 rotate about the axis of the floating pivot pin 37 and oscillate circumferentially relative to each other during the operation of the en rgy converter in a manner to be described more fully herea ter.

Adjacent pairs of the plurality of pistons 34-36 define variable volume fluid media receiving chambers 40-42.

hile three such chambers 40-42 and three pistons 34-36 are illustrated for the purpose of describing this invention, the number of chambers and pistons can be varied from the number illustrated in the drawings.

The pistons 34-36 are radially confined between the floating pivot pin 37 and the cylinder 33, as is best illustrated in FIGURE 2 of the drawings, and are similarly confined against axial movement or displacement relative to the axis of the floating pivot pin 37 by a pair of axially spaced circular rotor plates 43, 44 (FIGURE 1) forming an integral part of or conventionally secured to a main shaft 45. The main shaft 45 includes oppositely directed shaft portions 46 and 47 conventionally rotatably journalled in the respective cylindrical bores 21 and 20 by conventional roller bearing assemblies 59, 51 respectively.

As is best illustrated in FIGURE 2 of the drawings, the axis of the main shaft is eccentrically offset from but parallel to the axis of the floating pivot pin 37. The plates 43, 44 when driven in a manner to be described fully herea ter, rotate about the axis of the drive shaft 45 while the pistons 34-36 rotate about -a second displaced axis corresponding to the center of the floating pivot pin 37.

Each of the pistons 34-36 is driveably connected to the plates 43, 44 by an associated one of three drive pins 52-54 passing through respective elongated slots 55-57 (FIGURE 2). The drive pins 52-54 are identical, and the following description of the drive pin 52 of FIGURE 1 will suffice for a complete understanding of the remaining drive pins 53-54. The drive pin 52 includes a head 58 received in a recess (unnumbered) of the plate 44. A threaded end portion 60 of the drive pin 52 is threadably secured to a flanged sleeve 61 passing through an opening (unnumbered) in the plate 43 and telescopically surrounding the pin 52. A flange (unnumbered) of the flanged sleeve 61 seats in a recess (also unnumbered) in the plate 43. A rolling sleeve '62 surrounds the flanged sleeve 61. The pin 52 and the flanged sleeve 61 are provided with bleed passages collectively referred to by the reference numeral 63 for introducing a suitable liquid lubricant, such as oil, between the flanged sleeve 61 and the rolling sleeve 62.

The drive pins 52-54 are concentrically and symmetrically positioned relative to the axis of the shaft 45 (FIGURE 2) but are in eccentric relationship relative to the axis of the floating pivot pin 37.

The rotor plate 43 of the engine unit 11 is provided With three sets of three triangularly arranged exhaust ports or openings 65-67 (FIGURES 4-A through 4-C) which selectively place the chambers 46-42 in fluid communication with a pair of arcuately shaped exhaust ports 76, '71 in the face plate 22 of the engine unit 11. The exhaust ports 73, 71 merge to form a single opening (unnumbered) in fluid communication with an exhaust pipe 72 (FIGURE 1) secured to the face plate 22. A single port 73 of each of the three sets of exhaust ports 65-67 is larger than the remaining two ports (individually unnumbered) of the three sets. The exhaust port 71 in the face plate 22 is likewise wider than the exhaust port 711. The radial distance between the axis of the main shaft 4.5 and each of the exhaust ports 73 corresponds to the radial distance between this same axis and the center of the wider arcuate exhaust port 71 to permit registration between the ports 73 and the exhaust port 71 (FIGURE 4-B) to exhaust combustion gases from the chambers 40-42 in a manner to be described more fully hereafter. The unnumbered ports of each of the three sets of exhaust ports 65-67 are similarly spaced from the axis of the main shaft 45 to overlie the narrower arcuate port 70 (FIGURE 4-B).

The port 73 of each of the three sets of triangularly arranged exhaust ports 65-67 is enlarged relative to the remaining two ports of each of the three sets to permit a combustible gaseous medium in any one of the chambers 43-42 to be ignited by ignition means 75 (FIGURE 1) including a spark plug or glow plug 76 threaded into a bore 7'7 of the face plate 22. A conductor 78 is connected between an electrical energy source and the plug 76 to energize the latter in a well known manner. The bore 77 into which the plug 76 is threaded is spaced from the axis of the main shaft 45 a distance equal to the spacing of each of the larger ports 73 of the three sets of exhaust ports 65 through 67 in the plate 43. This arrangement permits the firing or ignition of a combustible gas in any one of the chambers 46-42 through any one of the larger ports 73 when the axis thereof is coincident with the axis of the bore 7 7 The combustible medium is introduced into any one of the combustion chambers 49-42 of the engine unit 11 through three axial intake ports or openings 80-82 formed in the rotor plate 44. The intake ports 80 through 82 are equally radially spaced from the axis of the main shaft 45 and upon rotation of the shaft 45 and the plate 44 the intake ports 80 through 82 pass across a pair of arcuately shaped stationary intake ports 83, 84 (FIG- URES 1, 5-13 and S-C) in the central housing portion 18 (FIGURE 1) of the housing 13. The arcuate intake ports 83 and 84 merge in the central housing portion 18 to form a generally large trapezoidally shaped exhaust port 85 of the compressor unit 12.

The compressor or driven unit 12 of the energy converter 19 is similar in construction to the engine unit 11 and compreses a cylindrical sleeve or race 87 (FIG- URES 1 and 3) positioned in the cylindrical bore 17 of the compressor housing portion 16. A radially innermost circumferential surface 88 of the sleeve 87 forms an outer raceway for a conventional anti-friction bearing assembly 91. A radially outermost circumferential surface 92 of a cylindrical sleeve or cylinder 93 forms an inner raceway for the bearing assembly 91, as is best illustrated in FIGURE 3 of the drawings.

Three pie-shaped annular segments or pistons 94, 95 and 96 are mounted in the compressor unit between the cylinder )3 and a floating pivot pin or member 97, as is best illustrated in FIGURE 3 of the drawings. The pistons 94 through 96 rotate about the axis of the floating pivot pin 97 and oscillate circumferentially relative to each other during the operation of the energy converter 10 in a manner to be described fully hereafter.

Adjacent pairs of the plurality of pistons 94 through 96 define variable volume fluid media receiving chambers Nil-102. There are three such chambers 100-102 and three such pistons 94-96, thus corresponding in number to the three chambers 40-42 and the three pistons 34-36 of the engine unit 11. However, just as in the case of the engine unit 11, the number of chambers and pistons of the compressor unit 12 can be varied from the number shown in the drawings.

The pistons 94 through 96 are radially confined between the floating pivot pin 97 and the cylinder 93, as is best ilustrate-d in FIGURE 3 of the drawings, and are similarly confined against axial movement or displacement relative to the axis of the floating pivot pin 97 by a pair of axially spaced circular rotor plates 103, 104 (FIGURE 1) forming an integral part of or conventionally secured to a shaft 105. The shaft 105 includes oppositely directed shaft portions 106 and 107. The shaft portion 107 is conventionally rotatably journalled in the cylindrical bore 24 of the face plate 25 by a conventional roller hearing assembly 108. The shaft portion 106 is conventionally secured in an axial bore 110 (FIGURE 1) of the shaft portion 47 of the main shaft 45.

As is best illustrated in FIGURE 3 of the drawings, the axis of the main shaft 45 is eccentricall'y offset from but parallel to the axis of the floating pivot pin 97, and as is apparent by comparing FIGURES 2 and 3 of the drawings, the floating pivot pin 97 is approximately 180 degrees out of phase relative to the main shaft 45 as compared to the angular relationship of the floating pivot pin 37 with respect to this same shaft. When the plates 103, 104 are driven in a manner to be described more fully hereafter, the same rotate about the axis of the drive shaft 45 and the shaft 105 while the pistons 94-96 rotate about a second displaced axis, corresponding to the center of the floating pivot pin 97, approximately 180 degrees out of phase with the rotation of the pistons 34-36 of the engine unit 11.

Each of the pistons 94-96 is driveably connected to the plates 103, 104 by an associated one of three drive pins 121 passing through respective elongated slots 115- 117 (FIGURE 3).

Each of the drive pins 121 includes a head 113 (FIG- URE 1) received in an associated recess (unnumbered) of the plate 103. A threaded end portion 120 of a screw 112 passing through an opening (unnumbered) in the plate 104 is threadably secured to the head 118 of each of the pins 121. A flange 119 of each of the screws 112 seats in a recess (also unnumbered) in the plate 104. A rolling sleeve 122 surrounds each of the drive pins 121. The screw 112 and the head 118 of the drive pins 121 can be provided with bleed passages (not shown) similar to the bleed passages 63 in the pin 52 and flanged sleeve 61 of the engine unit 11 for introducing lubricant between the drive pin 121 and the roller sleeve 122.

The drive pins 121 are concentrically and symmetrically positioned relative to the axis of the shaft 45 and 105, but are in eccentric relationship relative to the axis of the floating pivot pin 97.

The rotor plate 103 of the compressor unit 12 is provided with three sets of four radially arranged exhaust ports or openings 125-127 (FIGURES 6-A, 6-B and 6-C) which selectively place the chambers 100-102 in fluid communication with the exhaust port 85 in the central housing portion 18 of the compressor unit 12. The exhaust ports 125-127 are equally circumferentially spaced from each other and are arranged concentrically relative to the axis of the shafts 105 and 45. Upon rotation of the shaft 45, the shaft 105 secured thereto and the plate 103, the exhaust ports 125-127 pass across the exhaust port 85 during maximum compression of one of the chambers 100-102 whereupon the combustible fluid medium passess through the intake ports 83, 84 and one of the intake ports 80 through '82 into a selected one of the chambers 40-42 of the engine unit 11.

The combustible medium is introduced into the compression chambers 100-102 of the compressor unit 12 of the energy converter through three elongated axial intake ports or openings -132 in the rotor plate 104. The intake ports 130-132 are equally radially spaced from the axis of the main shaft 45 and the shaft 105, and upon rotation of these shafts and the plate 104 the intake ports 130-132 pass across an arcuately shaped stationary intake port 133 (FIGURES 7-A through 7-C) in the face plate 25 of the housing 13. The arcuate intake port 133 is connected by an intake passage 134 (FIGURE 1) to a conventional carburetor which is fed a combustible medium, such as gasoline, through a conduit 136 in fluid communication with a conventional source of combustible medium (not shown) such as a gasoline tank.

The operation of the energy converter will be described with particular reference to FIGURES 4-A through 4-C, 5-A through 5-C, 6-A through 6-C and 7-A through 7-C, to which attention is directed. In each of these figures, the pistons 34 through 36, 94 through 96, the shaft 45, and the rotor plates 43, 44, 103 and 104 are rotating in a clockwise direction as indicated by the directional arrows of FIGURES 4-A, S-A, 6-A and 7-A.

In FIGURE 4-A of the drawings, the chamber 40 between the pistons 34 and 35 is at maximum compression, and the combustible medium therein i.e., a gas and air admixture, for example, is ignited by the spark or glow plug 76 (FIGURE 1) through the larger exhaust port 73 of the group of exhaust ports 65. At this point of maximum compression of the chamber 40 of the engine unit 11, the corresponding chamber 100 (FIGURES 6-A and 7-A) between the pistons 94 and 95 of the compression unit 12 is at maximum expansion because the eccentricity of the engine unit 11 is approximately degrees out of phase with that of the compressor unit 12, as has been heretofore noted.

Upon the ignition of the gas in combustion chamber 40, the rotor plates 43 and 44 are driven clockwise by the driving connection between the drive pins 52-54 and the slots 55-57 in the respective pistons 34-36. As the rotor plates 43, 44 rotate clockwise about the axis of the shaft 45, 0 to 60 degrees (FIGURE 4-B) and 90 degrees (FIGURE 4-C), chamber 40 completes approximately one-half of its expansion cycle. Complete expansion of the chamber 40 occurs when the chamber 40 reaches the position of chamber 41 in FIGURE 4-B.

Between the firing position of chamber 40 (FIGURE 4-A) and the complete expansion thereof the set of exhaust ports 65 in the rotor plate 43 rotate across the exhaust ports 70, 71 in the face plate 22 of the housing 13,

as shown with respect to the chamber 41 in FIGURE 4-B to expel some of the combustion gases from the chamber 40 through the exhaust pipe 72 (FIGURE 1). Prior to the set of exhaust ports 66 approaching cutoff (FIGURE 4-B) the intake port 81 of the rotor plate 44 begins to pass across the intake ports 83, 84 in the central housing portion 18 of the housing 13 (FIGURE S-B). A new charge of combustible gas under pressure from the compressor unit 12 is expanded into the chamber 41. During the period of time that both the exhaust ports 66 and the intake ports 81 are open (FIGURE 1) to the chamber 41, the chamber 41 is scavenged by the new charge entering therein.

During this 0 to 90 degree rotation of the components of the engine unit 11 the shaft 45 connected to the shaft 105 drives the rotor plates 103, 104 and the pistons 94- 96 connected by the drive pins 121 from 0 to 90 degrees (FIGURES 6-A through 6-C, and 7-A through 7-C).

During this 90 degree rotation the compression chamber 100 completes approximately one-half of its compression cycle, noting again that in FIGURE 7-A the chamber 100 is at maximum expansion during maximum compression of the chamber 40 of the engine unit 11. The remainder of the compression cycle of the chamber 100 is shown by the chamber 101 in FIGURES 6-A and 6-B, with maximum compression being shown in FIG- URE 6-B. At this point the compressor unit exhaust ports 126 in the compression rotor plate 103 open through the intake port 85 in the central housing portion 18 (FIG- URES 1 and 6-B) to place the chamber 101 in fluid communication with the chamber 41 of the engine unit 11. As the intake port 81 (FIGURES 1 and -B) of the engine unit rotor plate 44 opens into the arcuate intake ports 83, 84 the charge of combustible gas in the chamber 191 is introduced into the combustion chamber 41.

The illustrated travel of chamber 42 in FIGURES 4-A through 4-C illustrates the compression of this new charge introduced into the chamber 41, noting that the chamber 42 is sealed as soon as the intake port 32 (FIG- URE 5-A) passes beyond the arcuate intake ports 83, 84 in the central housing portion 18 of the housing 13.

The introduction of a charge of combustible gas admixed With air from the carburetor 135 (FIGURE 1) into the compressor unit 12 is best shown in FIGURES 7-A through 7-C with respect to the chamber 102. In FIGURE 7-A the intake port 132 of the rotor plate 104 is shown opening into the arcuate intake port 133 in the face plate 25 which port 133 opens into the intake passage 134. The chamber 102 expands (FIGURES 7A through 7C) and is cut off just prior to ignition of the engine unit 11 when the intake port 132 passes clockwise beyond the intake port 133. This position is shown by the intake port 130 (FIGURE 7-A).

The same series of events outlined above will occur consecutively for each of the chambers as the motor and compressor unit pistons rotate and circumferentially oscillate relative to each other in the housing 13 of the energy converter 10. During such continuous operation of the energy converter a combustible gas-air mixture would thus be sequentially drawn into and compressed in each of the compressor chambers 100-192 of the compressor unit 12 with maximum compression of the mixture occurring simultaneously with maximum expansion in each corresponding combustion chamber 40 through 42 of the engine unit 11. By means of the ports heretofore noted such combustible gas charges are expanded into the respective engine chambers scavenging the spent combustion gases and filling the respective combustion chambers preparatory to compression, ignition and expansion in a series or repetitive cycles comparable to the cycle just described.

Each of the combustion chambers 46 through 42 are sealed during the compression portion of their cycle relative to the housing 13 and the sleeve or cylinder 33. Such sealing is preferably accomplished by a plurality of sealing rings 140, 141 (FIGURE 1) positioned in respective circular grooves 142, 143 in the respective rotor plates 43 and 44. The sealing ring 140 and the groove 142 surrounds the set of exhaust ports 65, and an identical sealing ring and groove (not shown) surrounds the remaining sets of exhaust ports 66, 67 in the rotor 43. An identical sealing ring and groove (also not shown) similarly surrounds each of the two remaining intake ports 80, 82. In this manner, the chambers 40 through 42 are sealed against the escape of combustible gases as the sealing rings 140 bearingly engage against the inner surface (unnumbered) of the face plate 22 while the sealing rings 141 similarly bear against the inner surface (also unnumbered) of the central housing portion 18. A circular spring is positioned in each of the grooves 142, 143 to bias the respective sealing rings 14%, 141 into bearing sealing contact with associated portions of the housing 13 The sleeve or cylinder 33 is similarly provided with sealing rings 144, 145 received in respective ring grooves 146, 147 (FIGURE 1) in peripheral faces (unnumbered) of the cylinder 33. A spring (not shown) is preferably positioned in each of the grooves 146, 147 to urge the respective sealing rings 144, 145 into intimate sealing contact with the innermost surfaces (unnumbered) of the respective rotor plates 43 and 44.

The housing 13 is also preferably provided with a fluid-coolant chamber 151) (FIGURE 1) to aid in dissipating heat of combustion. The chamber and connecting passages is fed coolant from a suitable conventional source (not shown) through an inlet conduit 151, and upon circulation through the chamber 150, the fluid coolant is withdrawn through an outlet conduit 152.

From the foregoing, it will be seen that novel and advantageous provisions have been made by carrying out the desired end. However, attention is again directed to the fact that additional variations may be made in this invention without departing from the spirit and scope thereof as defined in the appended claims.

I claim:

1. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, a shaft, a pair of axially spaced plates coupling said pistons to said shaft, a plurality of circumferentially spaced exhaust ports in one of said plates, a plurality of circumferentially spaced intake ports in the other of said plates and port means in said housing for selective fluid communication with said exhaust and intake ports.

2. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, adjacentpairs of said plurality of pistons defining a chamber, 'a shaft, means coupling said pistons to said shaft, and means for introducing fluid media into and substantially simultaneously withdrawing fluid media from said chamber.

3. The energy converter as defined in claim 2, wherein ignition means are provided in radial alignment with at least one of said circumferentially spaced exhaust ports for ignition of a fluid therethrough.

4. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, adjacent pairs of said plurality of pistons defining a chamber, a shaft, means journalling said shaft for rotation, a floating pivot pin in said cylinder, a pair of axially spaced plates carried by said shaft, said pivot pin being positioned between said plates in eccentric relationship relative to the axis of said shaft and in concentric relationship relative to said bore and cylinder, each of said pistons being axially confined between said plates and radially confined between said cylinder and pivot pin, means coupling said plates to each of said pistons whereby movement of said pistons imparts rotation to said shaft through said coupling means and limited rotation of said cylinder relative to said pistons, means in one of said plates for introducing fluid media axially into said chambers and means in another of said plates for withdrawing fluid media from said chambers.

5. The energy converter as defined in claim 4 including means for igniting the fluid media in a selected one of said chambers through aperture means in said another of said plates.

6. The energy converter as defined in claim 5 wherein said aperture means forms a portion of said fluid media withdrawing means.

7. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, adjacent pairs of said plurality of pistons defining a chamber, a shaft, means journalling said shaft for rotation, a floating pivot pin in said cylinder, a pair of axially spaced plates carried by said shaft, said pivot pin being positioned between said plates in eccentric relationship relative to the axis of said shaft and in concentric relationship relative to said bore and cylinder, each of said pistons being axially confined between said plates and radially confined between said cylinder and pivot pin, means coupling said plates to each of said pistons whereby movement of said pistons imparts rotation to said shaft through said coupling means and limited rotation of said cylinder relative to said pistons, said coupling means comprising slot means in each of said pistons, pin means connected to at least one of said plates and received in an associated one of said slot means, fluid withdrawal means in one of said plates, fluid introduction means in the other of said plates and fluid ports in said housing for selective fluid communication with said fluid withdrawal and fluid introduction means.

8. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, adjacent pairs of said plurality of pistons defining a chamber, a shaft, means journalling said shaft for rotation, a floating pivot pin in said cylinder, a pair of axially spaced plates carried by said shaft, said pivot pin being positioned between said plates in eccentric relationship relative to the axis of said shaft and in concentric relationship relative to said bore and cylinder, each of said pistons being axially confined between said plates and radially confined between said cylinder and pivot pin, means coupling said plates to each of said pistons whereby movement of said pistons imparts rotation to said shaft through said coupling meansand limited rotation of said cylinder relative to said pistons, said coupling means comprising an elongated slot in each of said pistons, the axis of each slot being directed generally toward the axis of said pivot pin, and a pin passed through each slot and connected to said plates, said plates defining means for substantially simultaneously introducing and withdrawing fluid to and from the chamber.

9. An energy converter comprising in combination a drive unit and a driven unit, each of said units including housing means provided with a bore, a plurality of pistons in each of said bores, adjacent pairs of said plurality 0f pistons defining fluid media receiving chambers, rotatable shaft means, means coupling the piston of each unit to said shaft means, a member in each bore defining an axis of rotation about which said pistons travel, the axes of said members being eccentric relative to each other and to the axis of said shaft means whereby the pistons of said units rotate out of phase, and means for placing selected ones of said drive unit and said driven unit chambers in fluid communication.

10. The energy converter as defined in claim 9 wherein said last mentioned means include a plurality of ports opening axially into said drive and driven unit chambers.

11. The energy converter as defined in claim 9 wherein means are provided for igniting fluid media introduced into a selected one of said drive unit chambers during substantially minimum volume thereof and means for supplying fluid media to a selected one of said driven unit chambers during substantially maximum volume thereof.

12. The energy converter as defined in claim 11 wherein minimum volume of said selected one drive unit chamber and the maximum volume of said selected one driven unit chamber are approximately 180 degrees out of phase.

13. The energy converter comprising in combination a drive unit and a driven unit, each of said units including housing means provided with a bore, a cylinder rotatably mounted in each bore, a plurality of pistons in each of said cylinders, adjacent pairs of said plurality of pistons defining fluid media receiving chambers, rotatable shaft means, means coupling the pistons of each unit to said shaft means, a floating pivot pin in each cylinder defining an axis of rotation about which said piston and cylinders travel, the axes of said pivot pins being eccentric relative to each other and to the axis of said shaft means whereby the pistons of said units rotate out of phase, and means for placing selected ones of said drive unit and driven unit chambers in fluid communication.

14. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of segmental pistons in said cylinder, adjacent pairs of said plurality of pistons defining a chamber of varying volume as said pistons advance and retract relative to each other during the rotation thereof, a shaft, means journalling said shaft for rotation in said housing, a pair of axially spaced plates carried by said shaft, said pistons being axially confined between said plates, a floating pivot pin between said plates, said pistons being radially confined between said floating pivot pin and said cylinder, said floating pivot pin having an axis in parallel eccentric relationship relative to the shaft axis, means coupling said plates to each of said pistons, said coupling means including an elongated slot in each piston, .a pin passed through each of said slots and positively secured between said plates, valve means including a plurality of circumferentially spaced axial exhaust ports in a first of said plates and a plurality of circumferentially spaced intake ports in a second of said plates, and port means in said housing for selective fluid communication with said exhaust and intake ports.

15. The energy converter as defined in claim 14, Wherein said exhaust ports are arranged in a plurality of groups and ignition means are provided for igniting fluid media in said chambers through one of the exhaust ports of said groups.

16. An energy converter comprising a housing having a cylindrical bore, a cylinder rotatably mounted in said bore, a plurality of pistons in said cylinder, adjacent pairs of said plurality of pistons defining a chamber, a shaft, means coupling said pistons to said shaft, a member in said cylinder, a portion of each piston contacting said member, said member defining an axis of rotation about which said pistons and cylinder travel, said axis of piston and cylinder travel being eccentric relative to the shaft axis, means for axially introducing fluid media into each of said chambers during a predetermined period and means for withdrawing fluid from the chambers into which fluid media is being introduced during at least part of said predetermined period, and means for sealing said fluid media introducing means.

17. An energy converter comprising in combination a drive unit and a driven unit, a plurality of pistons in each of said units, adjacent pairs of said plurality of pistons defining fluid media receiving chambers, rotatable shaft means, means coupling the pistons of each unit to said shaft means, and means for placing selected ones of said drive unit and said driven unit chambers in fluid communication.

18. The energy converter as defined in claim 17 wherein said coupling means includes eccentric means whereby the pistons of said units-rotate out of phase.

19. The energy converter as defined in claim 17 wherein means are provided for withdrawing fluid media from a selected drive unit chamber during part of the time the drive unit and driven unit chambers are in fluid communication.

References Cited by the Examiner UNITED STATES PATENTS 2,547,374 4/1951 Carideo 103-129 2,685,256 8/ 1954 Humphreys 103-129 3,139,871 7/1964 Larpent Born Corset 123-43 FOREIGN PATENTS 1,569 3 Great Britain. 1,732 1881 Great Britain. 4,494 191 1 Great Britain. 257,664 9/ 1926 Great Britain. 326,109 3/ 1930 Great Britain.

MARK NEWMAN, Primary Examiner. CARLTON R. CROYLE, Examiner. F. T. SADLER, Assistant Examiner.

Claims (1)

1. AN ENERGY CONVERTER COMPRISING A HOUSING HAVING A CYLINDRICAL BORE, A CYLINDER ROTATABLY MOUNTED IN SAID BORE, A PLURALITY OF PISTONS IN SAID CYLINDER, A SHAFT, A PAIR OF AXIALLY SPACED PLATES COUPLING SAID PISTONS TO SAID SHAFT, A PLURALITY OF CIRCUMFERENTIALLY SPACED EXHAUST PORTS IN ONE OF SAID PLATES, A PLURALITY OF CIRCUMFERENTIALLY SPACED

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