US3801237A

US3801237A - Rotary engine or pump

Info

Publication number: US3801237A
Application number: US00254053A
Authority: US
Inventors: J Gotthold
Original assignee: Individual
Current assignee: Individual
Priority date: 1972-05-17
Filing date: 1972-05-17
Publication date: 1974-04-02
Anticipated expiration: 1991-04-02
Also published as: AU6490074A

Abstract

This invention pertains to a rotary internal combustion engine and specifically to a rotary engine deriving its motive force from pressure applied to piston vanes which rotate axially inside of a cylinder while they accelerate and decelerate in relation to each other to create relative movement between them. It may also be used as a pump or as a steam engine.

Description

United States Patent Gotthold 1 Apr. 2, 1974 1 ROTARY ENGINE 0R PUMP 3,294,071 12/1966 Turco 4l8/36 x [76] Inventor: John Phillip Gotthold, 255 I Bernardo N0 8 Sunnyvale, Calif. Primary Examiner-Carlton R. Croyle 94086 Assistant ExaminerRobert E. Garrett 22 F] d M 17 1972 Attorney, Agent, or FirmMoore, Zimmerman & 1e ay Dubb [21] Appl. No.: 254,053

I v 57 ABSTRACT g This invention pertains to a rotary internal combustion [58] Fie'ld 123/8 418/35 36 37 engine and specifically to a rotary engine deriving its motive force from pressure applied to piston vanes [56] References Cited which rotate axially inside of a cylinder while they accelerate and decelerate in relation to each other to UNITED STATES PATENTS create relative movement between them. It may also 3,203,405 8/1965 Sabet l23/8.47 be used as a pump or as a steam engine. 3,256,866 6/1966 Bauer v. 3,565,049 2/1971 Bauer l23/8.47 X 7 Claims, 7 Drawing Figures PATENTEU 2 1974 SHEET 1 UF 2 FIG 5} FIGZ.

PATENTEU 2 SHEET 2 OF 2 FIG 5.

FIGT.

ROTARY ENGINE OR PUMP SUMMARY OF THE INVENTION Engines are known having two pairs of vanes which rotate axially and accelerate and decelerate relative to each other. In the past the relative motion of the vanes has been provided for by a gearing and crank arm means but this does not provide for a harmonic sequence and the pairs of vanes actually come to a stop during each revolution, providing a jerking action with high inertial loading.

It is the object of my invention to provide a rotary engine improved over prior art by a piston vane phasing means that allows the piston vanes to continuously rotate as they phase and does so in a harmonic sequence which keeps the inertial loads to a minimum while utilizing a simple and rugged structure for the phasing means.

Further objects of my invention are to provide a rtary engine that is inherently axially balanced and relatively vibration free, has increased power and torque output for its cubic displacement and is of simple and easily manufactured design.

Although the engine of the present invention was primarily designed as an internal combustion engine and will be largely so described, the engine may be operated by an exspansible fluid such as externally generated steam or it may be operated as a pump.

DESCRIPTION OF DRAWINGS FIG. 1 is a longitudinal sectional view of the engine FIG. 2 is a sectional view on the line 2-2 of FIG. 1 showing the porting FIG. 3 is a similar sectional diagram showing the engine as an external combustion device or as a pump.

FIGS. 4, 5, 6, 7 are diagrams illustrating the operation of the engine through the four stages of a cycle.

DETAILED DESCRIPTION AND SPECIFICATION In the prior art, piston engines wasted power and exhibited vibration due to the reciprocation of the pistons. Additionally their valving mechanisms added complications and detracted from their output.

Epitrichoidal rotary engines suffered from high rotor tip speed and low torque at low speed characteristics.

In prior rotary piston vane engines, which phased ei ther one or both piston vanes, the phasing means produced a motion inherently nonharmonic, creating high intertial stress on the piston vanes. Additionally the piston vanes were brought to a full instantaneous stop, relative to the engine case, at the start of each phasing cycle, thus negating the desirable characteristic of continous rotation.

My invention improves on prior art with its harmonic phasing means and simple and rugged construction, which will be made readily apparent by the following detailed description.

Refering to FIG. 1, a cylindrical housing provides an inner wall 1 which defines the combustion chamber, a space for circulation of a cooling medium 2 and an outer wall 3 to contain said medium. The cylindrical housing has double walled end plates 4 which close the ends of the housing, provide a space for further circulation of the cooling medium 2 and provide support for the bearings which carry the piston vane shafts 8. The

cooling medium is thus circulated all around the combustion chamber and then would be cooled and returned to space 2 by means well known to those skilled in the art.

Cylindrical closed end cases 5 are attached to the end plates 4 to contain the lubricant necessary for the phasing meansand provide additional support to the shaft 8.

The power producing rotating and phasing means consists of a diametrically opposed set of piston vanes 6 rigidly attached by means 7 to the axial shafts 8, which extend through the end plates 4 and to the bearing means provided in the end cases-5. Rigidly attached to the end plates 4 is the main bevel gear 9. Carried on a bearing rigidly mounted to the ring housing 10 is the toggle bar flywheel 11, which has a planet bevel gear, of ratio one to two with the main bevel gear 9, as its outer part and a toggle bar bearing frame as its inner part. The toggle bar 12 is located with its shaft section inside the toggle bar flywheel bearing and its flat cylindrical section located inside a slot placed axially through the piston vane shaft 8. The toggle bar is held in place by a pivot pin 13 which has its axis located at the geometric intersection of the bevel gear set 9 and 11.

The ring housing 10 with its integral ring gear is connected with an identical ring housing and bevel gear toggle bar phasing means and its piston vanes on the other end of the engine, by meshing with the gears 14 mounted on external shaft 15, which is contained in and carried by housing 16. This shaft makes the two identical phasing means act in concert to provide the workingaction of the engine.

Both piston vanes and phasing means are identical except that at one end the piston vanes are ninety degrees from the axis of the planet bevel gear and on the other end are mounted parallel to it.

Said shaft 15 actsas the power take off and can be used as an integral part of a transmission means well known to those skilled in the art.

Reference FIG. 2. An inlet port 17 is provided through the double walls of the cylindrical housing and combustive mixture is supplied by means well known to those skilled in the art.

A ignition means 18 is provided at an appropriate radial distance from the intake port 17. Means 18 can be a spark plug or a fuel injection device or glow plug for compression ignition. Said ignition means would be of a design well known to those well skilled in the art.

An exhaust port 19 is provided at an appropriate radial distance from the ignition means, being approximately radially equidistant as is said inlet port. It would utilize such antipollution devices as are known to those well skilled in the art. r

The piston vanes 6 are provided with slots and suitable seals 20 along their sides and arcuate outer ends such as are replaceable and provide apositive gas seal between the working chambers formed between the piston vanes. The seals are held against the cylindrical combustion chamber wall and the wall end plates by springs and centrifugal force derived from the continuous rotation of the piston vanes.

An operational cycle of the engine is described by FIGS. 4, 5, 6, 7. In FIG. 4 the phasing means 21 has its connected piston vanes 22 fully advanced in the direction of rotation and phasing means 23, on the outer end' of the combustion chamber, has its piston vanes 24 fully retarded. The working chambers formed between the piston vanes inside the combustion chamber are performing the following cycle functions. Chamber A is full of compressed combustible mixture andin position to be ignited by ignition means 25. Chamber B has finished expanding from the force of the combusted gases and has opened to the exhaust port 26. Chamber C is beginning to expand and induct new combustible mixture through the intake port 27. Chamber D is starting to compress its charge of combustible mixture.

FIG. shows the relative positions of the working chambers after the phasing means have radially advaced 90. Chamber D has diminished and advanced until it is under the ignition means 25 and the other chambers have likewise advanced to the next sequential combustion cycle segment.

' FIGS. 6 and 7 show that in a full revolution of the phasing means the piston vanes both rotate and phase such that all four working chambers complete the four segments of an internal combustion Otto cycle. Each set of piston vanes phases twice during each revolution of the phasing means due to the ratio of the planet bevel gears to the main bevel gears. The piston vanes also serve as their own valving means.

' The motive power of the expanding fluid between the piston vanes is translated into rotary motion by the phasing mechanisms. As the leading piston vane of a chamber is pushed on, its rigidly connected shaft transfers the torque to its connected toggle bar. The toggle bar in turn applies the torque to its planet bevel gear which causes the planet bevel gear to advance rotatably around its main bevel gear. The planet bevel gear in turn advances its bearing connectedring housing which, through its integral ring gear and the external gears and shaft, drives the phasing means at the other end of the combustion chamber. The second phasing Such revisions and modifications which could be applied to my invention by those skilled in the art, without departing from the principles thereof, are included within the scope of the following claims.

1. In a rotary engine or pump, a cylindrical expansion chamber closed at both ends by end walls and containing two sets of interfitting piston vanes mounted on coaxial drive shafts extending axially through an end wall, at least one of said shafts being connected to harmonic phasing means consisting of a bevel gear set including a main bevel gear and a cooperating planet bevel gear, a toggle bar having one end journaled in said planet bevel gear and extending therefrom towards said drive shaft in a direction non-parallel to the axis of rotation of the planet bevel gear, said drive shaft including means for connecting said extending end of the toggle bar to the drive shaft such that said bar will pivot relative to the shaft in a plane including the axis of rotation of the shaft and about the geometric intersection of the bevel gear set, means connecting the drive shafts for means keeps its piston vane advancing even while it slows down relative to the leading piston vane. The torque differential between the advancing piston vane and the retarding one, which turns the engine, is supplied by the increase in lever arm inherent when the toggle bar of a phasing means is positioned further away from its main bevel gear rather than close to it.

phased rotation of the piston vane sets, and ports at selected locations about the chamber to introduce and exhaust fluid between the interior and exterior of said chamber whereby with relative rotation between the shafts and the chamber said piston vane sets will rotate about the drive shaft axes at non-uniform velocities relative to each other to effect expansion and compression cycles within the chamber and between adjacent vanes.

2. In a rotary engine or pump as defined in claim 1 wherein both drive shafts are connected to harmonic phasing means.

3. In a rotary engine or pump as defined in claim 2, housing means for supporting both planet bevel gears.

4. In a rotary engine or pump as defined in claim 3 the means connecting the drive shafts for phased rotation of the piston vane sets including gear means connecting said housing means.

5. In a rotary engine or pump as defined in claim 1, said means for connecting said extending end of the toggle bar to the drive shaft including an axially extending slot included in the drive shaft for receiving and holding said toggle bar end.

6. In a rotary engine or pump as defined in claim I wherein the included angle between the toggle bar and the axis of rotation of the planet bevel gear is no greater than 265 whereby the connected drive shaft will rotate continuously but at a non-uniform velocity.

7. In a rotary engine or pump as defined in claim 1 wherein the ratio of the main bevel gear to the planet bevel gear is 2 to l.

Claims

1. In a rotary engine or pump, a cylindrical expansion chamber closed at both ends by end walls and containing two sets of interfitting piston vanes mounted on coaxial drive shafts extending axially through an end wall, at least one of said shafts being connected to harmonic phasing means consisting of a bevel gear set including a main bevel gear and a cooperating planet bevel gear, a toggle bar having one end journaled in said planet bevel gear and extending therefrom towards said drive shaft in a direction non-parallel to the axis of rotation of the planet bevel gear, said drive shaft including means for connecting said extending end of the toggle bar to the drive shaft such that said bar will pivot relative to the shaft in a plane including the axis of rotation of the shaft and about the geometric intersection of the bevel gear set, means connecting the drive shafts for phased rotation of the piston vane sets, and ports at selected locations about the chamber to introduce and exhaust fluid between the interior and exterior of said chamber whereby with relative rotation between the shafts and the chamber said piston vane sets will rotate about the drive shaft axes at non-uniform velocities relative to each other to effect expansion and compression cycles within the chamber and between adjacent vanes.

6. In a rotary engine or pump as defined in claim 1 wherein the included angle between the toggle bar and the axis of rotation of the planet bevel gear is no greater than 26.5* whereby the connected drive shaft will rotate continuously but at a non-uniform velocity.

7. In a rotary engine or pump as defined in claim 1 wherein the ratio of the main bevel gear to the planet bevel gear is 2 to 1.