CA1049413A - Rotary internal combustion engine - Google Patents
Rotary internal combustion engineInfo
- Publication number
- CA1049413A CA1049413A CA241,105A CA241105A CA1049413A CA 1049413 A CA1049413 A CA 1049413A CA 241105 A CA241105 A CA 241105A CA 1049413 A CA1049413 A CA 1049413A
- Authority
- CA
- Canada
- Prior art keywords
- radially extending
- channel
- central
- pipe
- rotors
- 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
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Rotary Pumps (AREA)
Abstract
ABSTRACT OF THE INVENTION
A rotary internal combustion engine comprising two inter-meshing rotors provided with radially extending lobes and intervening grooves, the lobes of at least one of the rotors being provided with radially extending channels for supply and return of cooling liquid from and to, respectively, axially extending central channels of the rotor, said return channels being interposed said supply channels and a heated surface portion of the lobes, and the temperature difference between the cooling liquid portions in the radially extending channels being utilized for circulating the liquid under the action of the centrifugal forces arising during rotation of the rotors.
A rotary internal combustion engine comprising two inter-meshing rotors provided with radially extending lobes and intervening grooves, the lobes of at least one of the rotors being provided with radially extending channels for supply and return of cooling liquid from and to, respectively, axially extending central channels of the rotor, said return channels being interposed said supply channels and a heated surface portion of the lobes, and the temperature difference between the cooling liquid portions in the radially extending channels being utilized for circulating the liquid under the action of the centrifugal forces arising during rotation of the rotors.
Description
-~ ~10494~3 The present invention relates to a rotary positive displacement internal combustion engine oE the type comprising j two intermeshing rotors, each provided with a central hub portion, amember ofaxially and radially extending spokelike lobes with intervening grooves, andwithin itshub portion a central channel system comprising a supply channel and a discharge channel for passage of a cooling liquid therethrough.
More specifically the invention relates to means of , such an engine providing an automatic circulation of the cooling ¦ 10 liquid in radial direction for transfer of the heat to be removed radially inwardly to the central channel system owing to the centrifugal forces acting upon two media of different ~ density.
; In rotors of complicated shape, especially such pro-; vided with several relatively thin spokes extending from a central hub it is a problem to circulate the cooling liquid passing through the hub out into the back from the spokes in order to obtain an efficient cooling of the spokes. One ~ example of such a rotor is a rotor of an internal combustion i 20 engine of the type comprising two intermeshing rotors each provided with grooves and intervening lands extending radially inwardly from a generally cylindrical surface. An engine of such a type is for instance shown in British patent 1 172 828.
In such a machine the lands of the rotors represent the spokes 'l mentioned above.
i Up to now it has been necessary to shape the rotors with a complicated system of cooling channels to be passed through by means of a forced pump circulation. Anyhow there are difficulties to avoid pockets of stagnant liquid resulting ~ 30 in inadequate cooling of certain portions of the rotor lands.
.,y .
i ~04~413 -The pxesent inVention provides means Eor the internal cooling of s~ch roto~s whlch means are efficient, simple and inexpensive in production~
According to the present invention there is provided a rotary positive di.splacement internal combustion engine of the type comprising two intermeshin~ rotors, each provided with a central hub portion, a plurality of axially and radially extending spokeli]ce lobes with intervening grooves, and within its huh portion a central channel system comprising a supply channel and a discharge channel for passage of a cooling liquid therethrough, at least one of the rotors within each of its spokeli~e lobes being provided with at least one radially extend-ing central channel having an inner end communicating with said central supply channel and an outer end communicating with a radially extending return passage connected to said cen-tral discharge channel, said radially extending return passage bein~
interposed hetween said radially extending channel and each one of said heated surface portions of said lobe to be cooled, said raaially extending return passage and said radially extending :
channel heing composed of a cavity and a pipe, respectively, ~ :
said pipe being radially inserted in the cavity and projecting from said central supply channel towards the radially outermost portion of said ca~ity. Thus according to the present invention at least one of the rotors within each of its spo~.elike lobes is provided with at least one radially extending channel having an inner end communicating with said central supply channel ~.
and an outer end communicating with a rad.ially extending return . passage connected to said central discharge channel, said radially I extending return passage being interposed said radially extendin~
channel and a heated surface portion of said lobe to be cooled.
, Since each return passage is interposed a radially extendingchannel and a flan}~ of the land so that the heat transerred from the flank to the cooling liquid is supplied to -the li~uid in
More specifically the invention relates to means of , such an engine providing an automatic circulation of the cooling ¦ 10 liquid in radial direction for transfer of the heat to be removed radially inwardly to the central channel system owing to the centrifugal forces acting upon two media of different ~ density.
; In rotors of complicated shape, especially such pro-; vided with several relatively thin spokes extending from a central hub it is a problem to circulate the cooling liquid passing through the hub out into the back from the spokes in order to obtain an efficient cooling of the spokes. One ~ example of such a rotor is a rotor of an internal combustion i 20 engine of the type comprising two intermeshing rotors each provided with grooves and intervening lands extending radially inwardly from a generally cylindrical surface. An engine of such a type is for instance shown in British patent 1 172 828.
In such a machine the lands of the rotors represent the spokes 'l mentioned above.
i Up to now it has been necessary to shape the rotors with a complicated system of cooling channels to be passed through by means of a forced pump circulation. Anyhow there are difficulties to avoid pockets of stagnant liquid resulting ~ 30 in inadequate cooling of certain portions of the rotor lands.
.,y .
i ~04~413 -The pxesent inVention provides means Eor the internal cooling of s~ch roto~s whlch means are efficient, simple and inexpensive in production~
According to the present invention there is provided a rotary positive di.splacement internal combustion engine of the type comprising two intermeshin~ rotors, each provided with a central hub portion, a plurality of axially and radially extending spokeli]ce lobes with intervening grooves, and within its huh portion a central channel system comprising a supply channel and a discharge channel for passage of a cooling liquid therethrough, at least one of the rotors within each of its spokeli~e lobes being provided with at least one radially extend-ing central channel having an inner end communicating with said central supply channel and an outer end communicating with a radially extending return passage connected to said cen-tral discharge channel, said radially extending return passage bein~
interposed hetween said radially extending channel and each one of said heated surface portions of said lobe to be cooled, said raaially extending return passage and said radially extending :
channel heing composed of a cavity and a pipe, respectively, ~ :
said pipe being radially inserted in the cavity and projecting from said central supply channel towards the radially outermost portion of said ca~ity. Thus according to the present invention at least one of the rotors within each of its spo~.elike lobes is provided with at least one radially extending channel having an inner end communicating with said central supply channel ~.
and an outer end communicating with a rad.ially extending return . passage connected to said central discharge channel, said radially I extending return passage being interposed said radially extendin~
channel and a heated surface portion of said lobe to be cooled.
, Since each return passage is interposed a radially extendingchannel and a flan}~ of the land so that the heat transerred from the flank to the cooling liquid is supplied to -the li~uid in
2 -10~9~13 I the interposed passa~e onl~ the li~uid in the interposed ; passage will get a higher temperature than that in the radially extending channel and consequently the density of the liauid will be somewhat different in the two channels. The centrifugal forces acting upon the liquid during revolving of the rotor will then be different in the two channels resulting in an j automatic circulation of the cooling liquid from the central channel system outwardly through said set of radially extending channels and inwardly back to the central channel system through ¦ 10 said set of interposed passages. Furthermore the higher the
3 temperature of the flank the larger the difference in density between the ].i~uid in the two channels and conseauently the speed of the radial circulation is increased which means that i the capacity of the coolin~ automatically increases with an increased supply of heat so that the temperature of the flank j will be practically the same independant of the amount of heat supplied to the surface of the rotor.
The present invention will be Eurther described by way of the accompanying drawings, wherein;
,., ~:' ' ~ 30 ',~; '~ ' . , ' ` - 2a - :
~`
~6~494~3 Figure 1 shows a cross section o~ a rotary abutment member for a rotary internal combustion engine of the type schematically indicated by dot-dashed lines.
Figure 2 shows a detail of Figure 1 on a larger scale, and I Figure 3 shows a longitudinal section o~ the rotor ¦ detail shown in Figure 2.
;~ The engine indicated by dot-dashed lines in Figure 1 -' has a casing 1 enclosing a working space composed of the barrel walls of two intersecting bores 2, 3 having paral].el axes and intersecting along two straight axial lines and two end walls.
The casing 1 is provided with combined inlet and scavenging outlet channels 4 and with exhaust ports 5, 6 in the barrel , walls of the two intersecting bores 2, 3 and further with a ; fuel injection nozzle 7 and a spark plug 8 placed in a somewhat -depressed position in each of the three tip portions of a power rotor 9 which is rotatably mounted in the casing 1 for sealing cooperation with the walls of the bore 2.
~ A rotary abutment me~ber or abutment rotor 10 is ;' 20 rotatably mounted in the casing 1 for sealing cooperation with the walls of the bore 3 and with the power rotor 9 as is clearly , described in the British patent specification 1 392 174. The abutment rotor 10 is provided with five grooves 12 and inter-vening lands 1~ extending axially along the rotor. As better :
shown in Figures 2 and 3 the rotor 10 is provided with a central, axially extending bore 16 in which a concentric pipe 18 is ,~inserted. A cooling liquid is in a conventional manner supplied to the pipe 18 and discharged from the bore 16 outside the .1 pipe 18~ Each land 14 of the rotor 10 is furthex provided with five axially spaced bores 20 extending radially outwards from the central bore 16. A pip2 22 is inserted in each radial. bore ~;
20 and is supported in its outer end by the bottom of the bore 20, whereas its inner end penetrates the central pipe 18 and is ',,', -`\
1049~3 supported thereby. The outer end of the pipe 22 ls further provided with slits 24 in order to form a communication between the pipe 22 and the surrounding bore 20.
The internal cooling of the rotor 10 takes place in -I the following way. The cooling liquid, for instance water or ~ oil, is supplied to the central pipe 18 from an outer source, ¦ not shown, of cooling liquid and fills up the channel system, comprising the central pipe 18, the radial pipes 22, the radial bores 20, and the central bore 16, and i9 discharged from the central bore 16 through a cooler, not shown, back to the liquid source. During operation of the engine the rotor 10 is contin-uously revolved at a high speed, simultaneously as the flanks and the crest of each ro~or land 14 is exposed to the high ~-~
temperature of the wor~ing fluid passing through the engine.
Owing to the centrifugal forces the cooling liquid will be forced outwardly through the radial pipes 22 and the radial bores 20. The heat absorbed by the surfaces of the rotor land 14 from the hot working fluid is transferred through the body of the land 14 to the surface of each radial bore 20, and further transferred to the liquid in the bore 20 contacting said surface.
The liquid in thebore 20 outside the pipe 22 will in this way get a higher temperature than that of the liquid inside the pipe 22. Owing to the temperature difference the density of the liquid outside the pipe 22 will be lower than that inside the ~;
i pipe 22. Consequently the centrifugal forces acting upon the ~- liquid outside and inside the bore 22 will not any longer be the same, but the forces acting upon the liquid outside the pipe 22 will decrease those inside the pipe 22 resulting in a forced circulation outwardly inside the pipe 22 and inwardly outsid~ the pipe 22. In other words an automatic circulation of the cooling liquid through the radial channel system is achieved.
.~
~l This automatic circulation effect can be taken care of 1 '' :
,, ,:
in different ways.
The simplest way is to completely rely upon this effect which means that no pump is needed for the circulation of the liquid from the back to the liquid source.
However, in most cases a pump for the circulation is needed to speed up the flow in spite of the flow losses in the system including the liquid cooler, which otherwise must be considerably larger. In such a pump circulation system the automatic circulation effect is of extremely importance not only to the resulting decrease of the power needed for the pump, but primarily as it guarantees such a distribution of the liquid , that more liquid is distributed to those portions of the rotor
The present invention will be Eurther described by way of the accompanying drawings, wherein;
,., ~:' ' ~ 30 ',~; '~ ' . , ' ` - 2a - :
~`
~6~494~3 Figure 1 shows a cross section o~ a rotary abutment member for a rotary internal combustion engine of the type schematically indicated by dot-dashed lines.
Figure 2 shows a detail of Figure 1 on a larger scale, and I Figure 3 shows a longitudinal section o~ the rotor ¦ detail shown in Figure 2.
;~ The engine indicated by dot-dashed lines in Figure 1 -' has a casing 1 enclosing a working space composed of the barrel walls of two intersecting bores 2, 3 having paral].el axes and intersecting along two straight axial lines and two end walls.
The casing 1 is provided with combined inlet and scavenging outlet channels 4 and with exhaust ports 5, 6 in the barrel , walls of the two intersecting bores 2, 3 and further with a ; fuel injection nozzle 7 and a spark plug 8 placed in a somewhat -depressed position in each of the three tip portions of a power rotor 9 which is rotatably mounted in the casing 1 for sealing cooperation with the walls of the bore 2.
~ A rotary abutment me~ber or abutment rotor 10 is ;' 20 rotatably mounted in the casing 1 for sealing cooperation with the walls of the bore 3 and with the power rotor 9 as is clearly , described in the British patent specification 1 392 174. The abutment rotor 10 is provided with five grooves 12 and inter-vening lands 1~ extending axially along the rotor. As better :
shown in Figures 2 and 3 the rotor 10 is provided with a central, axially extending bore 16 in which a concentric pipe 18 is ,~inserted. A cooling liquid is in a conventional manner supplied to the pipe 18 and discharged from the bore 16 outside the .1 pipe 18~ Each land 14 of the rotor 10 is furthex provided with five axially spaced bores 20 extending radially outwards from the central bore 16. A pip2 22 is inserted in each radial. bore ~;
20 and is supported in its outer end by the bottom of the bore 20, whereas its inner end penetrates the central pipe 18 and is ',,', -`\
1049~3 supported thereby. The outer end of the pipe 22 ls further provided with slits 24 in order to form a communication between the pipe 22 and the surrounding bore 20.
The internal cooling of the rotor 10 takes place in -I the following way. The cooling liquid, for instance water or ~ oil, is supplied to the central pipe 18 from an outer source, ¦ not shown, of cooling liquid and fills up the channel system, comprising the central pipe 18, the radial pipes 22, the radial bores 20, and the central bore 16, and i9 discharged from the central bore 16 through a cooler, not shown, back to the liquid source. During operation of the engine the rotor 10 is contin-uously revolved at a high speed, simultaneously as the flanks and the crest of each ro~or land 14 is exposed to the high ~-~
temperature of the wor~ing fluid passing through the engine.
Owing to the centrifugal forces the cooling liquid will be forced outwardly through the radial pipes 22 and the radial bores 20. The heat absorbed by the surfaces of the rotor land 14 from the hot working fluid is transferred through the body of the land 14 to the surface of each radial bore 20, and further transferred to the liquid in the bore 20 contacting said surface.
The liquid in thebore 20 outside the pipe 22 will in this way get a higher temperature than that of the liquid inside the pipe 22. Owing to the temperature difference the density of the liquid outside the pipe 22 will be lower than that inside the ~;
i pipe 22. Consequently the centrifugal forces acting upon the ~- liquid outside and inside the bore 22 will not any longer be the same, but the forces acting upon the liquid outside the pipe 22 will decrease those inside the pipe 22 resulting in a forced circulation outwardly inside the pipe 22 and inwardly outsid~ the pipe 22. In other words an automatic circulation of the cooling liquid through the radial channel system is achieved.
.~
~l This automatic circulation effect can be taken care of 1 '' :
,, ,:
in different ways.
The simplest way is to completely rely upon this effect which means that no pump is needed for the circulation of the liquid from the back to the liquid source.
However, in most cases a pump for the circulation is needed to speed up the flow in spite of the flow losses in the system including the liquid cooler, which otherwise must be considerably larger. In such a pump circulation system the automatic circulation effect is of extremely importance not only to the resulting decrease of the power needed for the pump, but primarily as it guarantees such a distribution of the liquid , that more liquid is distributed to those portions of the rotor
4 14 where the temperautre is higher than to those portions there-of where the temperature is lower. The cooling effect is thus ,~ so distributed inside the rotor that not only the different lands 14 will be kept at about the same temperature, but also I ~ the different axial sections of each land 14 will be kept at '' practically the same temperature. In other words the invention results in a guarantee that no portion is overheated without ~ ~ 20 any risk that any other part thereof is cooled down to a non-; ~ desired low temperature resulting in a disadvantageous increase of the cooling losses of the engine.
;~ When using a pump circulation system a direct communi-~ cation between the central pipe 18 and the surrounding bore 16 ,l may be advantageous for reduction of the cooling effect at part.,. , , load of the engine, and if the cooling liquid passes axially through the rotor 10 from an inlet in one end thereof to an out-let in the other end thereof the central pipe 18 may be complet-. ~ , :
ely dispensed with.
;30 One or both rotors 9j 10 may be provided with means ~i for cooling the rotors. If the interspaces between the bore 20 ;1 and the adjacent surfaces of the land 14 in Figure 2 is not too ; _5_ -. - . . , ~ , .
~4~3 narrow it is possible to use the bore 20 in substitute for said radially extending channel 22 and to provide each land 14 with radially extending return bores on opposite sides of each bore 20 adjacent the surfaces of the lands 14, the outer ends of each bore 20 and adjacent return bores being connected to each other via suitable circumferential passages.
,~ . ' , ':
;l 30 .~ .
~ 6 :, `
- . . .. . :.. : ., .,, :
;~ When using a pump circulation system a direct communi-~ cation between the central pipe 18 and the surrounding bore 16 ,l may be advantageous for reduction of the cooling effect at part.,. , , load of the engine, and if the cooling liquid passes axially through the rotor 10 from an inlet in one end thereof to an out-let in the other end thereof the central pipe 18 may be complet-. ~ , :
ely dispensed with.
;30 One or both rotors 9j 10 may be provided with means ~i for cooling the rotors. If the interspaces between the bore 20 ;1 and the adjacent surfaces of the land 14 in Figure 2 is not too ; _5_ -. - . . , ~ , .
~4~3 narrow it is possible to use the bore 20 in substitute for said radially extending channel 22 and to provide each land 14 with radially extending return bores on opposite sides of each bore 20 adjacent the surfaces of the lands 14, the outer ends of each bore 20 and adjacent return bores being connected to each other via suitable circumferential passages.
,~ . ' , ':
;l 30 .~ .
~ 6 :, `
- . . .. . :.. : ., .,, :
Claims (3)
OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A rotary positive displacement internal combustion engine of the type comprising two intermeshing rotors, each provided with a central hub portion, a plurality of axially and radially extending spokelike lobes with intervening grooves, and within its hub portion A central channel system comprising a supply channel and a discharge channel for passage of a cooling liquid therethrough, at least one of the rotors within each of its spokelike lobes being provided with at least one radially extending central channel having an inner end communicating with said central supply channel and an outer end communicating with a radially extending return passage connected to said central dis-charge channel, said radially extending return passage being interposed between said radially extending channel and each one of said heated surface portions of said lobe to he cooled, said radially extending return passage and said radially extending channel being composed of a cavity and a pipe, respectively, said pipe being radially inserted in the cavity and projecting from said central supply channel towards the radially outermost portion of said cavity.
2. A rotary engine as defined in Claim 1, in which said cavity is shaped as a radial bore enclosing said pipe.
3. A rotary engine as defined in Claim 1 or 2, in which each lobe is provided with several axially spaced radially extending channels.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA241,105A CA1049413A (en) | 1975-12-04 | 1975-12-04 | Rotary internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA241,105A CA1049413A (en) | 1975-12-04 | 1975-12-04 | Rotary internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1049413A true CA1049413A (en) | 1979-02-27 |
Family
ID=4104667
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA241,105A Expired CA1049413A (en) | 1975-12-04 | 1975-12-04 | Rotary internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1049413A (en) |
-
1975
- 1975-12-04 CA CA241,105A patent/CA1049413A/en not_active Expired
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