CA1046940A - Rotary engine and pump - Google Patents
Rotary engine and pumpInfo
- Publication number
- CA1046940A CA1046940A CA264,788A CA264788A CA1046940A CA 1046940 A CA1046940 A CA 1046940A CA 264788 A CA264788 A CA 264788A CA 1046940 A CA1046940 A CA 1046940A
- Authority
- CA
- Canada
- Prior art keywords
- piston
- output shaft
- wall
- groove
- rollers
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Landscapes
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Abstract of Disclosure Disclosed herein is an engine having opposed cylinders with a guided rotary and reciprocating piston which telescopes over an output shaft and transmits rotary motion directly to the output shaft without the need for a crankshaft. Guided rotary movement of the piston is afforded by rollers rotatably supported on a radial pin on the cylindrical wall of the piston.
The rollers travel in an elliptical type groove on the inside surface of the cylinder to impart rotary motion to the piston as a result of rectilinear motion of the piston caused by com-bustion of fuel in the working chambers on opposite sides of the piston. The engine can also be operated by an external source of pressurized gas or operated as a pump. The rotary motion is transmitted to-the output shaft by a rider block which has a square cross section and which is fixed to the output shaft and is complementary in shape to a square opening in the piston.
The rider block is movable between end walls in the piston.
Circular openings with cylindrical seals seal the output shaft to the piston.
The rollers travel in an elliptical type groove on the inside surface of the cylinder to impart rotary motion to the piston as a result of rectilinear motion of the piston caused by com-bustion of fuel in the working chambers on opposite sides of the piston. The engine can also be operated by an external source of pressurized gas or operated as a pump. The rotary motion is transmitted to-the output shaft by a rider block which has a square cross section and which is fixed to the output shaft and is complementary in shape to a square opening in the piston.
The rider block is movable between end walls in the piston.
Circular openings with cylindrical seals seal the output shaft to the piston.
Description
11 )4694C3 Title Rotary Engine and Pump Inventor Ralph 13. Schreiber Back~round of Invention The i~vention relates to a~ improved internal combust~o~ englne employing a free piston which recipro-cates be~wee~ oppositely located working chambers o~ a~
output shaft. Prior ~rt eDgines of ~his type ~uch ~s that show~ in the Moore patent 1,389,453 have a piston with a square bo~e which lntexfit~ ~ith a square portion of the output shaft to transmit rot~ry mot~on of a pis~on to the output shaft. With desi8ns of this type difficulty is encountered ~n sealing the square output ~haft in the square plston bore and ~n providing a ~orkable arrsngement !
of rollgrs ~hich ride the groov~ surface. The g~oove cu~-vature o the prior art is gene~eally l~mi~ed to sinuso~dal configurations.
summarY of lnveDtiorl The invention provides an opposed wor~ing chamber engine in which ~ealing difficulties o the ~oore pi8toD
are overcome by~an arrangement which employs ~ rider block square in cros~ section fixed on the cylind~ical outpu~
~hat ~hich inter~its in a s~uare bo~e on the piston. Thg rider ~lock has a leDgth less than the piStDD and the cylindrical portions of the output shaft ad~ace~t ~he rider block exte~d through cylindrical ~pertures in the pis~on ~
end walls to thus afford the use of conventional annular ~:
seals between $he output shaft and ~he pistoD
- . ~ .
;. 30 The rc~ctili3lear motior of the pistor~ is conve~ed ~ `~' ' " .
- 1 ~ ~ . .
~ 4694~
to rotary motion by two rollers or bearings rotating on the same axis on a pin located on the piston surface. The rollers are gulded in an elliptical or oval type track on the inDer offse cylinder wall. The track is in a plane which is traosverse to both ~he longi~udinal and radial axes of the cylinder and thus, the groove or track provides a camming ac~ion iD cooperation with the piqtoD rollers to cause rotary movement of the piston as the piston recipro-cates in response to firing impulses in ~he opposit~ly located workiog chambers of the cylinder. Smooth guided movement of the piston with respect to the annular cam track i9 affo~d~d by the u~e of two rollers of diff~reDt diameters suppo~ted for rotatio~ on one axis. The large diameter roller engages an oute~ channel wall and the small diameter roller engag~s ~n inwardly offset shoulder on the opposite channel wall. The dual rollers on a common axis provide .1 constant engagement o~ each roller with an opposed wall surface to minimize play which would occur if only one roller is employed as found in prior art pate~ts.
Further objects, advantages and f~atures of the ~nve~tion will become app~rent from the following disclosure. .~
-,:
Fig. 1 is a sectloDal view of $he e~gine in accor-dance with ~he invention.
Fig. 2 is ~n exploded view of the cylinder and piston an~ output shaft assembly of the engine shown in :.
Fig. 1, with th~ parts in the same orientation as they are ~, in Fig~
Fig. 3 is an e~larged fragme~tary section~l vie~ -~
of the eam ~rack ~nd roller 2~rangement shown.
.
, 94~ 3-Description of Preferred Embodlment Although the disclosure hereof is detailed and exact to enable those skilled in the art to practice the invention, the physical embodiments hereiD d~sclosed merely exemplify the i~vention which may be embodied in other specific structure. The scope of the inventioD is defined ; in the claims appended hereto.
A rotary engine 10 lncludes a cylinder 12 having opposed cyli~der h~ads 14, 16 and opposed workig chambers 18, 20 located on opposite sides of a piston 22.
Rectilinear movemPnt o the p~ston 22 can be caused by combu~tion of fuel in tbe working chambers caused by spar~ plugs~ compressed fuel injection or other ignition devices (not shown3. Alternatively, comprsssed gas~s can be employed to cause movement of the piston. The shaf t can be powered by an external source ~i.e. electric motor) ~nd ~ , , thus convert the de~ign to a pum~
In accord~nce with the invention9 ~eans are p~o~
v~ded for impartiDg rotary motio~ to the piston upon recti-l~near movement thereof. In the disclosed construotion themeans comprises a cam groove or track 30 having a groove botto~ 32, opposed groove walls 349 36 and a shoulder ha~ing a surface 38 which is inwardly offset ~rom surface 36. The cam groove 30 i~ generally oval or elliptical in con~igux-ation and ~s in a plane which ~s non-ormal to the axis of linear movement of the piston 22. The means also includes two bearings or rollers 40, 42 mounted on a pin 44 for ~o-tatio on the same axis which is radial or normal wi~h re spect to the axis of lo~gitudinal moYement of the pistonD
The rolle~ 40 engages a surface 38 and the larger dlamete~
)4694(~
roller 42 engages the sur~ace 34, thus providi~g continuous engagement of the rollers with the cam groove or track during the complete circuit of the rollers in the cam track.
The use of a single roller is not feasible because a certain amount of clearance is xequired in order to prevent binaing of the roller in the groove. Such clearance also can cause vibratio~ during use ~f the engine which will minimize the lif~ of the parts. The use of t~o rollers as shown elimi-nates play and thus vibration.
In accordance with the invention, means are pro-vided for transmitting the rotary motion of the piston 22 to the outpu shaft 46. In the disclosed construction the .
output sha~t 46 is provided with a rlder block 48 which is fixed thereto ~nd of a length le~s than that of the piston. : `
The ~d~r bloek 48, as shown (Fig. 2), is square in cross ~ :
section and interfi~s iD a s~uare bore 50 in the piston. .
Other compleme~tary rider block cross sections and bore con-figura~ions can be utllize~ if they provide a rotary drlving .
engagement between the piston and the output shaft 46. The xider block 48 is sealed i~ the bore 50 b~ pistoD end walls 52, 54 which have cylindrical apertures 51 with compre~sion :
and o~l sealin~ rl~gs S8 which seal the bore 50 to the out- ;
pYt shaft 46 for both sliding and rotary movement. In ad~
dition, the end walls 52~ 54 csn be provided with the com- ~.
p~ess~.o ~d oil rings 56 to seal the piston to the wall of .
the cylinde~ P~s~on 22 is of a ~;omewhat smaller dianaeter than pi3ton end walls 52, 54 to allo~ air and oil movement~
only r~ng~ 56 have contact with ~yllrlder 125 however.
~ .
The output ~h~fS 46 c~n be provided with a ~apered - 30 surface 60 adj ~cent each end thereof with beariDgs 62 ir~ j !
1 ~
~ . . .. . - , . ~ , .......................... .
; ... . .. . ..
46~4~
the cylinder heads irl engagement with the surfaces 60 to positiveiy locate the shaft 46 with respect to the cylinder 12. A compression plate 67 or ring seals, would be fitted to the shaft to seal the bearing area in addition to use of conYentional oil bearing seals.
Intake and exhaust valve assemblies 64, 66 for each working chambe~ are shown but not described in detail because they form r~o part o~ ~he pre~ent ~nvention. Any suitabl~ valvi~g and valve control can be employed for operation in a two or four cycle mode.
Although ~otary internal combustion engines having opposed combustion chambers or cylinders are known, eDgines of this type have not been succe~sful because of sealing difficulties and problems in controlling the guided rotary piston mo~ement. The prese~t inYention overcome~ diffi-culties of prior art engines of this type by employing con-ventlon~l cylindrical piston ring~ and conven~ional cylin~
drical seals to seal the working chambers ~round the piston - and by employ~ng two bearings operated through a single axis on o~fset walls in the cylinder grooves.
ConventioDal head and cylinder cooling can be employed. Oil clrculat~on is basically conventional with alternative ~outing and drainage approaches available. Oil can erl er the bearings 62 and flow ioto ~ hollaw shaft 4~ :
and out on each rider block sur~ace 48~ and out duct exits 89 in the piston to the cyl~nder wall and ~roove surface, fo~ lubricatiDg the Idual bearings 40, 42 and into a sm~ll - ~ump trlot shown~ through groove surface 32. Cent~ifugal motion ~s~d the rela'cive motion be~een the riLd~r block and 30 piStDlD provide pumping astion ~or movement of oil th~ough '";~' :' `~" ~L~469~
pa s sage 89 .
Several of ~he engines of this design can be serially connected with the output shafts co-axi`ally con-nected . This design also af fords the use of various dimensio~s for piston diameter, s~roke and groove path, which flexibility is not found in other rotary eng~ De de-signs .
- ';' .': "
,'~. ' , .. ..
- ' ', :.
"'"' ~ ~ .
.
~.
, -. .
, '':.
~ .
~ ' ' ~ ~:
output shaft. Prior ~rt eDgines of ~his type ~uch ~s that show~ in the Moore patent 1,389,453 have a piston with a square bo~e which lntexfit~ ~ith a square portion of the output shaft to transmit rot~ry mot~on of a pis~on to the output shaft. With desi8ns of this type difficulty is encountered ~n sealing the square output ~haft in the square plston bore and ~n providing a ~orkable arrsngement !
of rollgrs ~hich ride the groov~ surface. The g~oove cu~-vature o the prior art is gene~eally l~mi~ed to sinuso~dal configurations.
summarY of lnveDtiorl The invention provides an opposed wor~ing chamber engine in which ~ealing difficulties o the ~oore pi8toD
are overcome by~an arrangement which employs ~ rider block square in cros~ section fixed on the cylind~ical outpu~
~hat ~hich inter~its in a s~uare bo~e on the piston. Thg rider ~lock has a leDgth less than the piStDD and the cylindrical portions of the output shaft ad~ace~t ~he rider block exte~d through cylindrical ~pertures in the pis~on ~
end walls to thus afford the use of conventional annular ~:
seals between $he output shaft and ~he pistoD
- . ~ .
;. 30 The rc~ctili3lear motior of the pistor~ is conve~ed ~ `~' ' " .
- 1 ~ ~ . .
~ 4694~
to rotary motion by two rollers or bearings rotating on the same axis on a pin located on the piston surface. The rollers are gulded in an elliptical or oval type track on the inDer offse cylinder wall. The track is in a plane which is traosverse to both ~he longi~udinal and radial axes of the cylinder and thus, the groove or track provides a camming ac~ion iD cooperation with the piqtoD rollers to cause rotary movement of the piston as the piston recipro-cates in response to firing impulses in ~he opposit~ly located workiog chambers of the cylinder. Smooth guided movement of the piston with respect to the annular cam track i9 affo~d~d by the u~e of two rollers of diff~reDt diameters suppo~ted for rotatio~ on one axis. The large diameter roller engages an oute~ channel wall and the small diameter roller engag~s ~n inwardly offset shoulder on the opposite channel wall. The dual rollers on a common axis provide .1 constant engagement o~ each roller with an opposed wall surface to minimize play which would occur if only one roller is employed as found in prior art pate~ts.
Further objects, advantages and f~atures of the ~nve~tion will become app~rent from the following disclosure. .~
-,:
Fig. 1 is a sectloDal view of $he e~gine in accor-dance with ~he invention.
Fig. 2 is ~n exploded view of the cylinder and piston an~ output shaft assembly of the engine shown in :.
Fig. 1, with th~ parts in the same orientation as they are ~, in Fig~
Fig. 3 is an e~larged fragme~tary section~l vie~ -~
of the eam ~rack ~nd roller 2~rangement shown.
.
, 94~ 3-Description of Preferred Embodlment Although the disclosure hereof is detailed and exact to enable those skilled in the art to practice the invention, the physical embodiments hereiD d~sclosed merely exemplify the i~vention which may be embodied in other specific structure. The scope of the inventioD is defined ; in the claims appended hereto.
A rotary engine 10 lncludes a cylinder 12 having opposed cyli~der h~ads 14, 16 and opposed workig chambers 18, 20 located on opposite sides of a piston 22.
Rectilinear movemPnt o the p~ston 22 can be caused by combu~tion of fuel in tbe working chambers caused by spar~ plugs~ compressed fuel injection or other ignition devices (not shown3. Alternatively, comprsssed gas~s can be employed to cause movement of the piston. The shaf t can be powered by an external source ~i.e. electric motor) ~nd ~ , , thus convert the de~ign to a pum~
In accord~nce with the invention9 ~eans are p~o~
v~ded for impartiDg rotary motio~ to the piston upon recti-l~near movement thereof. In the disclosed construotion themeans comprises a cam groove or track 30 having a groove botto~ 32, opposed groove walls 349 36 and a shoulder ha~ing a surface 38 which is inwardly offset ~rom surface 36. The cam groove 30 i~ generally oval or elliptical in con~igux-ation and ~s in a plane which ~s non-ormal to the axis of linear movement of the piston 22. The means also includes two bearings or rollers 40, 42 mounted on a pin 44 for ~o-tatio on the same axis which is radial or normal wi~h re spect to the axis of lo~gitudinal moYement of the pistonD
The rolle~ 40 engages a surface 38 and the larger dlamete~
)4694(~
roller 42 engages the sur~ace 34, thus providi~g continuous engagement of the rollers with the cam groove or track during the complete circuit of the rollers in the cam track.
The use of a single roller is not feasible because a certain amount of clearance is xequired in order to prevent binaing of the roller in the groove. Such clearance also can cause vibratio~ during use ~f the engine which will minimize the lif~ of the parts. The use of t~o rollers as shown elimi-nates play and thus vibration.
In accordance with the invention, means are pro-vided for transmitting the rotary motion of the piston 22 to the outpu shaft 46. In the disclosed construction the .
output sha~t 46 is provided with a rlder block 48 which is fixed thereto ~nd of a length le~s than that of the piston. : `
The ~d~r bloek 48, as shown (Fig. 2), is square in cross ~ :
section and interfi~s iD a s~uare bore 50 in the piston. .
Other compleme~tary rider block cross sections and bore con-figura~ions can be utllize~ if they provide a rotary drlving .
engagement between the piston and the output shaft 46. The xider block 48 is sealed i~ the bore 50 b~ pistoD end walls 52, 54 which have cylindrical apertures 51 with compre~sion :
and o~l sealin~ rl~gs S8 which seal the bore 50 to the out- ;
pYt shaft 46 for both sliding and rotary movement. In ad~
dition, the end walls 52~ 54 csn be provided with the com- ~.
p~ess~.o ~d oil rings 56 to seal the piston to the wall of .
the cylinde~ P~s~on 22 is of a ~;omewhat smaller dianaeter than pi3ton end walls 52, 54 to allo~ air and oil movement~
only r~ng~ 56 have contact with ~yllrlder 125 however.
~ .
The output ~h~fS 46 c~n be provided with a ~apered - 30 surface 60 adj ~cent each end thereof with beariDgs 62 ir~ j !
1 ~
~ . . .. . - , . ~ , .......................... .
; ... . .. . ..
46~4~
the cylinder heads irl engagement with the surfaces 60 to positiveiy locate the shaft 46 with respect to the cylinder 12. A compression plate 67 or ring seals, would be fitted to the shaft to seal the bearing area in addition to use of conYentional oil bearing seals.
Intake and exhaust valve assemblies 64, 66 for each working chambe~ are shown but not described in detail because they form r~o part o~ ~he pre~ent ~nvention. Any suitabl~ valvi~g and valve control can be employed for operation in a two or four cycle mode.
Although ~otary internal combustion engines having opposed combustion chambers or cylinders are known, eDgines of this type have not been succe~sful because of sealing difficulties and problems in controlling the guided rotary piston mo~ement. The prese~t inYention overcome~ diffi-culties of prior art engines of this type by employing con-ventlon~l cylindrical piston ring~ and conven~ional cylin~
drical seals to seal the working chambers ~round the piston - and by employ~ng two bearings operated through a single axis on o~fset walls in the cylinder grooves.
ConventioDal head and cylinder cooling can be employed. Oil clrculat~on is basically conventional with alternative ~outing and drainage approaches available. Oil can erl er the bearings 62 and flow ioto ~ hollaw shaft 4~ :
and out on each rider block sur~ace 48~ and out duct exits 89 in the piston to the cyl~nder wall and ~roove surface, fo~ lubricatiDg the Idual bearings 40, 42 and into a sm~ll - ~ump trlot shown~ through groove surface 32. Cent~ifugal motion ~s~d the rela'cive motion be~een the riLd~r block and 30 piStDlD provide pumping astion ~or movement of oil th~ough '";~' :' `~" ~L~469~
pa s sage 89 .
Several of ~he engines of this design can be serially connected with the output shafts co-axi`ally con-nected . This design also af fords the use of various dimensio~s for piston diameter, s~roke and groove path, which flexibility is not found in other rotary eng~ De de-signs .
- ';' .': "
,'~. ' , .. ..
- ' ', :.
"'"' ~ ~ .
.
~.
, -. .
, '':.
~ .
~ ' ' ~ ~:
Claims (4)
1. In an engine, a pair of spaced working chambers defined by a cylindrical wall having an inner surface, a piston movable lineraly in said working chamber in response to gas pressure in said chambers and in gas sealed relation with said cylindrical wall, said piston having end walls with cylindrical apertures, an output shaft having cylindrical shaft portions extending through said apertures, and guide means on said piston and cylindrical wall to cause guided rotary movement of said piston upon axial movement of said piston, and means on said output shaft between said piston end walls for drivingly and slidingly connecting said output shaft to said piston to impart rotary motion to said shaft upon rotation of said piston and wherein said guide means comprises an oval groove recessed in said inner surface of said cylinder wall and inwardly open towards said piston, said groove being in a transverse plane with respect to the axis of travel of said piston and said groove limiting travel of said piston between two opposed piston positions and two guide rollers located in said groove and supported for free rotation on said piston about an axis radial with respect to said piston, said rollers having different diameters and said groove being defined by a groove bottom wall and first, second and third groove side walls, said first and second side walls being opposite said third side wall and wherein said first side wall joins said bottom wall and is spaced from said third wall a distance less than the distance of said second wall from said third wall, to form a stepped shoulder within said groove and wherein said smaller diameter roller rollably engages said first side wall and said larger diameter roller rollably engages said third wall.
2. The improvement of claim 1 including seals in said apertures in said piston end walls to prevent trans-mission of gas from one working chamber to another and afford relative movement of said piston with respect to said output shaft.
3. The improvement of claim 1 wherein said means on said piston and said cylinder wall to afford rotary movement of said output shaft upon axial movement of said piston com-prises an opening in said piston and a body portion on said output shaft interfitting in said piston opening said body portion having a shape complementary to said piston opening to afford guided axial movement of said piston relative to said output shaft and cause movement of said output shaft upon rotary movement of said piston.
4. In an engine having a piston operatively asso-ciated with a pair of spaced working chambers defined by a continuous cylindrical wall and movable axially and rotatably in said cylinder the improvement for guiding said axial and rotatable piston movement comprising large and small diameter rollers rotatably supported on said piston for ro-tation about a common generally radial axis and an oval track in said cylindrical wall having two opposed surfaces and an outwardly offset surface with said rollers engaged with said opposed surfaces and said offset surface affording clearance with said larger diameter roller and wherein the combined radial distance of said rollers is substantially equal to the maximum spacing between said surfaces.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA264,788A CA1046940A (en) | 1976-11-03 | 1976-11-03 | Rotary engine and pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA264,788A CA1046940A (en) | 1976-11-03 | 1976-11-03 | Rotary engine and pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1046940A true CA1046940A (en) | 1979-01-23 |
Family
ID=4107195
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA264,788A Expired CA1046940A (en) | 1976-11-03 | 1976-11-03 | Rotary engine and pump |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1046940A (en) |
-
1976
- 1976-11-03 CA CA264,788A patent/CA1046940A/en not_active Expired
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