US3670705A

US3670705A - Engine with an annular chamber

Info

Publication number: US3670705A
Application number: US58800A
Authority: US
Inventors: Masahiro Saito
Original assignee: Individual
Current assignee: Individual
Priority date: 1970-07-28
Filing date: 1970-07-28
Publication date: 1972-06-20
Anticipated expiration: 1989-06-20

Abstract

An engine comprises an annular chamber, a plurality of runners disposed in the annular chamber in a manner to be moved in the same direction by gas pressure through the annular chamber, the runners being divided into two equal groups each having at least two units, two rotor members respectively coupled with each group of runners, inertia imparting blocks attached to the respective rotor members so as to apply the momentum of the runners of one group to those of the other group by collision between the block associated with one rotor member and that coupled with the other rotor member, a power take off shaft journaled in bearings in a manner to be aligned with the rotating axis of the rotor members, two power transmitting members fixed to the power take off shaft so as to cooperate with each rotor member in the advancing direction of the runner, and means for preventing the rotor members from being moved backwards.

Description

United States Patent Saito 1 June 20, 1972 541 ENGINE WITH AN ANNULAR Primary Examiner-William E. Wayner CHAMBER Attorney-Flynn & Frishauf [72] inventor: Masahlro Salto, 407 Takashi, Mobara-shi, 57 STRAC Chiba-ken, Japan An engine comprises an annular chamber, a plurality of run- Flledi J y 1970 ners disposed in the annular chamber in a manner to be moved Appl. No.: 58,800

[52] US. Cl l23/8.47, 418/36 [51 Int. Cl. F02b 55/00 [58] Field of Search ..4l8/36, 38; 123/8.47

[56] References Cited UNITED STATES PATENTS 1,212,649 1/1917 Krikorian ..123/8.47 X 1,131,148 3/1915 Manuel ..418/34X 3,244,156 4/1966 Curtiss ..4l8/36 3,302,625 2/1967 Cunningham ..4l8/36 X in the same direction by gas pressure through the annular chamber, the runners being divided into two equal groups each having at least two units, two rotor members respectively coupled with each group of runners, inertia impartingblocks attached to the respective rotor members so as to apply the momentum of the runners of one group to those of the other group by collision between the block associated with one rotor member and that coupled with the other rotor member. a power take off shaft joumaled in bearings in a manner to be aligned with the rotating axis of the rotor members, two power transmitting members fixed to the power take off shaft so as to cooperate with each rotor member in the advancing direction of the runner, and means for preventing the rotor members from being moved backwards.

7 Claims, 12 Drawing Figures P'h'TENTEnJunzolsrz 3.670.705

SHEET 010? 10 F l G. 1

PATENTEDJuueo 1972 SHEET 0 [1F 10 FIG. 4

PATENTEDmzo 1972 sum 05 or 10 FIG. 50

PATENTEDJUMEO m2 sum as or 10 FIG.

PRTENTEmuuao I972 3.670.705

SHEET 07 0F 10 FIG. 6

PATENTEDJUHZOIQIZ 3.670.705

sum as or 10 PATENTEDmzo m2 3.670.705

sum 09 or 10 ENGINE WITH AN ANNULAR CHAMBER The present invention relates to an engine with an annular chamber wherein a plurality of runners are advanced by gas pressure in one direction, and more particularly to an engine usable as an ignition combustion engine, compression combustion engine, steam engine and the like.

The feature of this invention consists in obtaining rotation power directly from the circular movement of runners disposed in the annular chamber, so that the engine of this invention is driven with higher efficiency than the prior reciprocating engine of the piston-cylinder type.

According to the present invention, the engine comprises an annular chamber, a plurality of runners so disposed in the annular chamber as to divide it into the same number of gas-actuated areas as the runners and moved along the circular line of the chamber in one direction by the actuation of gases introduced into said areas, the runners being divided into two equal groups each having at least two units in such a manner that the runners of one group are alternately arranged with those of the other group, two rotor members respectively coupled with each group of runners, inertia imparting blocks attached to the respective rotor members so as to apply the mo mentum of the runners of one group to those of the other group by collision between the block associated with one rotor member and that coupled with the other rotor member, a ower take off shaft joumaled in bearings in a manner to be aligned with the rotating axis of the rotor members, two power transmitting members fixed to the power take ofi shaft so as to cooperate with each rotor member in the advancing direction of the runner, and means for preventing the rotor members from being moved backwards.

The other features and advantages of the present invention will be understood from the following description with reference to the accompanying drawings, in which:

FIG. 1 is a vertical cross sectional view of a two cycle ignition combustion engine embodying the present invention;

FIG. 2 is another cross sectional view of the engine of FIG. 1;

FIG. 3 is an end view of the engine taken along a line Ill-III of FIG. 1;

FIG. 4 is a perspective view, partly broken away, of the engine of FIG. 1;

FIGS. 5A and 5B are perspective views of the engine of FIG. 1 where the parts of the engine are demounted;

FIG. 6 is a vertical cross sectional view of a steam engine further embodying the present invention;

FIG. 7 is an end view of the engine taken along a line VII- VII of FIG. 6;

FIG. 8 is a cross sectional view of the engine taken along a line VIII-VIII of FIG. 6;

FIG. 9 is a cross sectional view of the engine taken along a line lX-IX of FIG. 6;

FIG. 10 is a cross sectional view of the engine taken along a line X-X of FIG. 6; and

FIG. 11 is a cross sectional view of the engine taken along a line Xl-XI of FIG. 6.

FIGS. 1 to 5 indicate an ignition combustion gasoline engine embodying this invention. The engine comprises an engine body or housing 1 having a central circular hollow portion la, and an endless tubular portion lb disposed on the periphery thereof so as to form therein an annular chamber 2 having a circular cross section: A plurality of runners are disposed in the annular chamber 2 movably through the tube, and divided into two equal groups, each of which has at least two units or, as indicated, four units totaling eight represented by

reference characters

3a, 3b, 3c and

3d

30, 3b, 3c and 3d) in such a manner that the

runners

3a, 3b, 3c and 3d of one group are altemately arranged with those 30, 3b, 3c and 3d of the other group, and that the chamber 2 is divided into the same number of gas-actuated areas 4a to 4b as all the runners. The runners of each group are arranged on a circular line at a prescribed s ace.

The engine further comprises two disc-shaped rotor member 5 and 5' respectively coupled with the runners of each group, which are attached to the peripheral portion of the rotor member. The rotor members 5 and 5' are disposed in the central circular hollow portion la which communicates with the annular chamber 2 through an annular slot 6 formed in the inside peripheral portion of the tubular portion lb. The peripheral portion of the rotor members 5 and 5' slidably contact each other and the opposite inner surfaces of the annular slot 6 with an air-tight seal there between.

The rotor members 5 and 5' are rotated about their common axis, which is aligned with that of a power take ofi shaft 7 journaled in

bearings

8 and 8 mounted on the side portions of the housing 1. There are provided inertia imparting blocks divided into two groups represented by reference characters 9b-9c-9d, and 9a'-9b'-9c'-9d'. The grouped blocks are arranged on the respective inside surfaces of the rotor members 5 and 5' in such a manner that the blocks of one group bear an alternate relationship with those of the other group along a circular line coaxial with the axis of the rotor member.

The aforementioned alternate arrangement assures that rotation of either of the rotor members 5 and 5' causes the blocks of the corresponding group to strike those of the other group and the momentum of the runners associated with the blocks of the former group is transmitted to those of the latter, before the forward ends of the runners of the former group reach the rear ends of those of the latter.

On the power take ofi shaft 7 are fixed two power transmitting members 10 and 10' which have bearing

portions

10a and 10a, and stop

portions

10b and 10b respectively. The bearing portions and 10a rotatably bear the bosses of the rotor members 5 and 5'. The bosses of the rotor members have inner

stepped portions

5a and 5a facing the

stop portions

10b and 10b respectively and each having circularly arranged ratchet teeth l0c engageable in a clockwise direction, in which the runner advances as shown in F IG. 5b, with pawls 11 which are pivotably disposed in grooves 12 formed on the periphery of the stop portions 10b (10b In the inner peripheral portions of the housing 1 facing the outer periphery of the bosses of the rotor members 5 and 5' are positioned circularly arranged ratchet teeth represented by

reference characters

13 and 13a. The ratchet teeth 13 are engageable in an anticlockwise direction, namely, opposite to that in which the runner advances, with pawls l4 pivotably disposed in grooves 15 formed on the peripheral portion of each of the bosses of the rotor members 5 and 5'. The ratchet teeth 13a are engageable in a clockwise direction, in which the runner advances, with pawls 14a pivotably set in grooves 15a formed on the peripheral portion of each of the bosses of the rotor members 5 and 5'.

To the power transmitting members 10 and I0 are attached disengaging

members

10d and 10d, which are used in such a manner that the pawls 14a of the stopped rotor member which are associated with the ratchet teeth 13a are depressed into the grooves 15a thereof by the corresponding disengaging member so as to cause the pawls 14a to be disengaged from the ratchet teeth 13a immediately before the stop of the preceding runners.

On the mutually facing surfaces of the bosses of the rotor members 5 and 5' are fonned bevel-gear teeth 16 and 16' coaxial with the axis of the shaft 7 and alternately engageable with bevel-

gear teeth

17a and 17a formed on a gear wheel 17 which is, for example, splined on the shaft 7, namely, in a manner to remain fixed in the rotating direction of an engine, but be movable in the axial direction thereof.

On one of the opposite walls of the endless tubular portion lb along the circular line thereof are arranged at an equal spacing six ignition plugs 18a to 18]. On the other wall of the endless tubular portion 1b along the circular line thereof are formed six pairs of intake ports 19a to 19f, and exhaust ports 20a to 20f spaced from the ignition plug by half a pitch therebetween. Each pair of intake and exhaust ports has valve seats 21 and 22 on which there rest poppet valve discs 23 and 24 respectively in a manner to be removable therewith. The valve discs 23 and 24 include operating rods 25 and 26 projecting out of the housing 1 and having at the outer ends guide heads 25a and 26a respectively. Furthermore, each of the valve discs 23 and 24 is outwardly urged by means of a compression spring member 27 surrounding the guide rod 25 or 26, in such manner that the valve disc contacts the corresponding seat so as to cause the corresponding port to be shut.

To the side portion of the housing 1 is attached a cup-like gear casing 28 which contains three

bevel gears

29, 30 and 31 serially engaged with each other. The bevel gear 29 is attached to the end of the shaft 7, the bevel gear 31 is attached to a shaft 32 journaled with the end of the gear casing 28 coaxially with the shaft 7 and projecting therefrom, and the bevel gear 30 is attached to a shaft 33 journaled with the side portion of the gear casing 28 perpendicularly to the axis of the shaft 7. To the outer end portion of the shaft 32 is attached a turn table 34 for controlling the respective poppet valves.

Two parallel

circular guide portions

35 and 36 are formed on the side wall of the turn table 34 in a manner to face the guide heads 25a and 26a of each pair of the poppet valves used in the intake and exhaust ports.

The top surface of the

guide portions

35 and 36 is corrugated particularly in such a manner that the guide head of each of the poppet valves moves relative to the direction in which there is formed the corrugation so as to operate the poppet valves in the following time sequence.

While the runners of one group represented by

reference characters

3a, 3b, 3c and 3d, together with the corresponding rotor member 5, make a first one-twelfth revolution due to the explosion of compressed gases in the areas 4a and 4e caused by the energized ignition plugs 18a and 18d, the gas filled in the areas 4b and 4f is compressed by the advancing movement of the

runners

3a and 3c. Simultaneously, the poppet valves 23 provided in the

intake ports

19a and 19d, though the valves of the other intake ports are closed, are opened so as to allow fresh gas to be sucked in due to the expansion of the areas 40 and 4g caused by the advancing movement of the

runners

3b and 3d. On the other hand the poppet valves 24 positioned in the

exhaust ports

20b and 20e, though the valves of the other exhaust ports are closed, are opened so as to allow waste gas to be expelled therethrough due to the shrinkage of the

areas

4d and 4h caused by the advancing movement of the

runners

3b and 3d.

Next, when a second group of

runners

3a, 3b, 3c and 3d, together with the corresponding rotor member similarly make a one-twelfth revolution, the same cycle of operation is conducted as in the preceding case by another set of runners immediately succeeding to the preceding ones in the direction in which the runners peripherally advance. Namely, when the

runners

3a, 3b, 3c and 3d make a one-twelfth revolution due to the explosion of compressed gases in the areas 4b and 4] caused by the energized ignition plugs 18b and 18a, the gas filled in the areas 4c and 4g respectively is compressed by the advancing movement of the

runners

3a and 3c. Simultaneously, the poppet valves 23 provided in the

intake ports

19b and 19a are opened so as to allow fresh gas to be sucked in due to the expansion of the

areas

4d and 4h caused by the advancing movement of the

runners

3b and 3d, and the poppet valves 24 positioned in the

exhaust ports

20c and 20f are opened so as to allow waste gas to be expelled therethrough due to the shrinkage of the areas 4e and 4a caused by the advancing movement of the

runners

3b and 3d.

When the first mentioned

runners

3a, 3b, 3c and 3d similarly make again a one-twelfth revolution, the same cycle of operation is conducted as in the preceding case by another set of runners immediately succeeding to the preceding ones. Consequently, the aforementioned two cycles of operation of the groups of runners are conducted alternately.

The inertia of the preceding runners of one group is transmitted to the stopped runners of the other group by collision between the inertia imparting blocks associated with the former group and those coupled with the latter.

When the

runners

3a, 3b, 3c and 3d together with the rotor member 5, are advanced along the circular locus defined by the annular chamber in a clockwise direction as shown in FIG. 3, their one-twelfth revolution is imparted to the transmitting member 10 by ratchet teeth of the stop portion 10b engaged with the pawls 1 l, and the rotor member 5' corresponding to the stopped

runners

3a, 3b, 3c and 3d is not urged in the advancing direction, regardless of the rotation of the shaft 7 by the power transmitting member 10 which is forcedly urged by the former rotor member 5, because the ratchet teeth 10c of the stop portion 10b are disengaged from the pawls 11.

Similarly, when the

runners

3a, 3b, 3c and 3d together with the rotor member 5', are advanced along the circular locus, their one-twelfth revolution is imparted to the transmitting member 10' by the ratchet teeth 10c of the stop portion 10b engaged with the pawls 11. In this case, the rotor member 5 corresponding to the

runners

3a, 3b, 3c and 3d is not urged by the ratchet teeth 10c of the stop portion 10b disengaged from the pawls 11.

When the gas pressure of the areas is increased by explosion, one group of runners and the corresponding rotor member, which are stopped, are prevented from making a backward motion in an opposite direction to that shown in FIG. 3, by the ratchet teeth 13 of stopping portion corresponding to the group engaged with the pawls 14.

And the stopped rotor member, together with the associated group of runners is simultaneously prevented from making an unnecessary run in a clockwise direction in FIG. 3, by the ratchet teeth 13a engaged with the pawls 14a until the preceding rotor member completes its movement.

Since the teeth 17a of the gear wheel 17 always engage with those of the moving rotor member, the shaft 7 is rotated at the same speed as the moving rotor member, so that the shaft 7 makes no idle movement.

When the inertia of one group of runners and rotor member is imparted to the other group of runners and rotor member by the inertia imparting blocks with the resultant stop of the former group, then the engaged gear teeth of the gear wheel 17 are disengaged from the bevel-gear teeth corresponding to the former group, and the other gear teeth of the gear wheel 17 are engaged with the other bevel-gear teeth corresponding to the latter group so that the latter group is prevented from making an idle movement against the power transmitting member.

In this case, the gear wheel 17 is so constructed that, for example, the surface of each of its gear teeth 17a inclined in the direction in which the runners revolve is depressed toward the corresponding surface of each of the bevel-gear teeth 16 engaged with gear teeth 17a so as to cause the gear wheel 17 to be moved away from the rotor member 5 along the spline of the shaft 7 when the rotor member 5 is stopped, and the gear wheel 17, together with the shaft 7, rotates forward relative to the rotor member 5.

Preferably, the gear wheel 17 is urged backward to its original position at the center of the spline of the shaft 7 by means of a toggle spring member 37.

FIGS. 7 to 9 illustrate a steam engine further embodying this invention. The engine comprises an engine body having an annular chamber 102 like that of the first mentioned embodiment. A plurality of, for example, six runners are disposed in the annular chamber 102 movably along a circular locus defined by the annular chamber 102 as in the first mentioned embodiment, and divided into two equal groups, each of which has at least two units, or, as indicated, three units totaling six represented by reference characters 103a, l03b and 103c (103a', 103b' and 103c'). The chamber 102 is divided into gas-actuated areas 104a to l04f by the runners.

The engine further comprises two disc-shaped

rotor members

105 and 105 respectively coupled with the runners of each group, which are attached to the peripheral portion of said rotor member. The

rotor members

105 and 105 are disposed in the central hollow portion of the engine body which communicates with the annular chamber 102 through a circular slot 106 formed inside of the periphery of the tubular portion of the engine body defining the chamber 102. The peripheral portions of the rotor members 105 and 105' slidably contact each other and the opposite wall surfaces of the slot 106 in airtight seal.

The

rotor members

105 and 105 are rotated about their common axis, which is aligned with that of a power take ofi shaft 107 joumaled in

bearings

108 and 108 mounted on the side portions of the engine body. There are provided inertia imparting blocks divided into two groups represented by reference characters 109a 109b 109:: and 109a 109b 109c. The grouped blocks are attached to the inside surfaces of the respective rotor members in such a manner that the blocks of one group are alternately arranged with those of the other group along a circular locus co-axial with the axis of the rotor member.

The blocks of both groups are actuated in the same manner as in the first mentioned embodiment.

On the power take off shaft 107 are fixed two

power transmitting members

110 and 110 which have stop portions 11% and 110b' respectively. Each of the stop portions 11011 and 110b' has ratchet teeth 110a and 110d formed on the peripheral portion thereof.

0n the inner periphery of the central hollow portion of the engine housing are circularly arranged

ratchet teeth

113 and 1 13a so as to face the

ratchet teeth

110c and 110d respectively. During the rotation of one of the rotor members 105 and 105', the pawls 1 11 are engageable with the ratchet teeth 110C as shown in FIG. 8 so as to transmit the advancing movement of the rotor member to the corresponding power transmitting member. The pawls 1110 are engageable with the ratchet teeth 1 10d as shown in FIG. 9 so as to prevent the power transmitting member from making a clockwise run when braking is applied to the engine. According to the arrangement of the other rotor member which is stationary, pawls 1 14 are engageable with the ratchet teeth 113 as shown in FIG. 11 so as to prevent the rotor member from making a backward movement. And the pawls 1140 are engageable with the ratchet teeth 113a as shown in FIG. 10 so as to prevent the stopped rotor member from being idly moved.

Each of the rotor members 105 and 105' includes three

sectorial windows

115a,115b and 115C (1 15a, l15b' and 115C). The pawls 111, Illa, 114 and 114a are attached to

pivots

152, 152a, 153 and 153a which are rotatably secured to the rotor members 105 and 105' in such a manner that the

pivots

152a and 153a associated with one rotor member particularly project through the windows of the other rotor member. The

pawls

111 and 111a swing themselves in such a manner that their ends are depressed on the surfaces of the ratchet teeth Il0c and 110d respectively. The pawls 114 and 1144 are urged by means of torsional springs (not shown) so as to be depressed on the surfaces of the ratchet teeth 1 13 and 1 13a.

The

rotor members

105 and 105 comprise disengaging members 160 which are so actuated that immediately before either of the rotor members 105 and 105' stops rotation, the corresponding disengaging members release the pawls 111a associated with the rotor member which is about to stand at rest from the ratchet teeth 1 10d.

The

rotor members

105 and 105 comprise other disengaging members 161 which are so operated that, immediately before either of the rotor members 105 and 105' stops rotation, the corresponding disengaging members release the pawls 114a associated with the rotor member which is stationary from the ratchet teeth 1 13a.

On one of the opposite inner walls of the annular chamber 102 are formed twelve pairs of intake ports 1 19a to 119l, and exhaust ports 120a to 1201 equally spaced from each other on a circular locus defined by the annular chamber. Each pair of the intake and exhaust ports includes

poppet valves

154 and 155 provided in the same manner as in the first mentioned embodiment.

A turn table 134 for controlling the respective poppet valves is attached to the end portion of a shaft 132 coaxially with the axis of the shaft 107 and journaled in a gear casing 156 mounted on the end portion of the engine body.

The shaft 132 has an internal gear 157 intermeshing with a spur gear 158 pivoted to the end portion of the housing. The spur gear 158 registers with another spur gear 159 mounted on the end portion of the shaft 107. On one side of the turn table 134 there are formed two parallel

circular guide portions

135 and 136 in a manner to face the guide heads 154a and 155a of each pair of the

poppet valves

154 and 155 used in the intake and exhaust ports.

The top surfaces of the

guide portions

135 and 136 are corrugated particularly in such a manner that the guide head of the poppet valve moves relative to the direction in which there is formed the corrugation so as to operate the poppet valve in the following time sequence.

When the runners of one group represented by reference characters 103a, 103k and 1030, together with the corresponding rotor member 105, make a first one-sixth revolution due to the force of compressed gas or steam introduced into the

areas

104b, 104d and 104]" through the valves 154 provided in the intake ports 119e, 119g and 119k, then the

areas

104a, 104c and 104e are shrunk by the advancing movement of the above-mentioned runners 1030, 103b and 1030. During the shrinkage of said

areas

104a, 104c and 104e, the valves 155 provided in the

exhaust ports

120b, 120j and 120j are opened so as to exhaust waste steam to the atmosphere or into a reservoir (not shown).

Next, when the runners of one group represented by reference characters 103a, 1031; and l03c'together with the corresponding rotor member 105', make a starting e motion as a result of collision between the

inertia imparting blocks

109a, 109b, and 109C and the

blocks

109a, 10% and 1090', and a one-sixth revolution due to the force of compressed gas or steam introduced into the areas 1040, 10 4c and 104ethrough the valves 154 provided in the

intake ports

119b, 119f and 119j, then the

areas

104b, 104d and 104)" are shrunk by the advancing movement of the above-mentioned

runners

103a, 103b' and 103c. During the shrinkage of said

areas

104b, 104d and 104f, the valves 155 provided in the exhaust ports 120a, 120e and 120i are opened so as to expel waste steam to the atmosphere or into a reservoir (not shown).

When the first mentioned runners 103a, l03b and 103C again make a one-sixth revolution, the same cycle of operation is conducted as in the preceding case by another set of runners immediately following the corresponding ones in the direction in which the runners peripherally advance.

When the

runners

103a, 103b and 103e, together with the rotor member 105, are advanced along the circular locus defined by the annular chamber in a clockwise direction shown in FIG. 8, their one-sixth revolution is imparted to the transmitting member 110 by the ratchet teeth 1 10 of the stop portion 11% engaged with the pawls 111. In this case, the rotor member 105' corresponding to the stopped runners 103a, 1031b and l03c' is not urged forward, regardless of the rotation of the shaft 107 by the power transmitting member 1 10 which is forcedly urged by the rotor member 105, because the ratchet teeth 1100 of the stop portion 110b are disengaged from the pawls 111 of the advancing member 110' coupled with the shaft 107.

Similarly, when the

runners

103a, 103b' and 103c', together with the rotor member 105', are advanced along the circular locus, their one-sixth revolution is imparted to the transmitting member 110' by the ratchet teeth 1100 of the stop portion 110b' engaged with the pawls 111. In this case, the rotor member 105 corresponding to the runners 103a, 1031) and 1036 is not urged by the ratchet teeth 1l0c of the stop portion 1 10b disengaged from the pawls 1 1 1.

When compressed steam is supplied to an operating area, the group of runners and rotor member which is stopped is prevented after start from making an anticlockwise movement shown in FIG. 11, by engagement with pawls 114 of the ratchet teeth 1 13 of stop portion corresponding to said group.

In order to better adjust the timing of the mutual action of each pair of the intake and exhaust valves, the engine device of this invention may involve guide

portions

135 and 136 constituted by separate members capable of being adjustably positioned on one side of a turn table 134.

What is claimed is:

l. A rotary engine comprising:

a. an engine housing having an annular chamber;

b. a power take-E shaft joumaled at the axis of said annular chamber;

c. a first rotor member and a second rotor member disposed oppositely to each other and loosely mounted for rotation on said shaft;

d. a plurality of runners provided on each of said rotor members in circumferentially spaced fashion and slidably inserted in said annular chamber, the runners on the first rotor member alternating with those on the second rotor member such that two adjacent runners and the inner wall of said annular chamber define a gas actuated area;

first and second power transmitting means fixedly connected to said shaft;

f first means causing the first and second rotor members to engage respectively with the first and second power transmitting means so as to prevent said transmitting means from idly moving backward with respect to said rotor members;

. second means causing the first and second rotor members to engage with the engine housing so as to prevent the backward idle movement of the rotor members;

h. a pair of third means causing the rotor members to engage with the engine housing so as to prevent the forward idle movement of the rotor members while the rotor members are kept stationary;

. means for operating the third means to disengage the rotor members from the engine housing so as to allow the rotor members to move forward;

j. means for connecting the running rotor member with the shaft to prevent the shaft from idly moving forward with respect to the running rotor member;

. at least one intake port on the annular chamber for introducing expansible gas into said gas actuated areas; and

. at least one exhaust port on the annular chamber for exhausting used gas from the actuated areas.

2. The rotary engine according to claim 1 wherein said connecting means comprises a gear wheel fixed to the shaft and telescopically movable between the rotor members and having on the both sides bevel gear teeth engageable with bevel gear teeth provided on the inner sides of the rotor members, said bevel gear teeth of the gear wheel being formed so as to engage with those of the rotor members while the rotor members are running and to disengage from those of the rotor members while the rotor members are kept stationary, whereby the gear wheel selectively engages with with the running rotor members to connect said running rotor members with the shaft so 7 as to prevent the idle forward movement of the shafi.

3. The rotary engine according to claim 2 wherein each of said third means comprises ratchet teeth arranged coaxially with the shaft on the inside of the engine housing and depressible pawls provided circumferentially on each of the rotor members so as to engage the corresponding ratchet teeth while the rotor rnembers are kept stationary; and said operating means comprises a plurality of disengaging members projecting laterally from each of the power transmitting means and arranged thereon in circumferentially spaced relationship to depress the pawls of the rotor members so as to disengage the rotor members from the corresponding power transmitting means while the rotor members are rotated.

4. The rotary engine according to claim 1 wherein said connecting means comprises first ratchet teeth arranged coaxially with the shaft on each of the power transmitting means, a plurality of first pawls provided and circumferentially spaced on the corresponding rotor member to engage with the first ratchet teeth so as to prevent the forward idle movement of the shaft while said corresponding rotor member is turnin and first disengaging members provided and crrcumferenti y spaced on the other rotor member to disengage the first pawls from the first ratchet teeth while said corresponding rotor member is kept stationary.

5. The rotary engine according to claim 4 wherein each of said third means comprises second ratchet teeth arranged coaxially with the shaft on the inside of the engine housing, a plurality of second pawls circumferentially spaced on the corresponding rotor member to engage with the second ratchet teeth so as to prevent the forward idle movement of the corresponding rotor member while it is kept stationary, and said operating means comprises second disengaging members circumferentially spaced on the other rotor member to disengage the second pawls from the second ratchet teeth while said corresponding rotor member is running.

6. The rotary engine according to claim 1 including a plurality of circumferentially spaced inertia imparting blocks on each of the inner sides of the first and second rotor members, the blocks on the first rotor member alternating with those of the second rotor member, the blocks on the running first or second member striking against the stationary second or first member, respectively.

7. The rotary engine according to claim 1 wherein said first runners, second runners, intake ports and exhaust ports are respectively four, four, six and six in number, said engine having six ignition plugs, six pairs of said intake and exhaust ports, said ignition plugs and pairs of ports being alternately arranged on, and communicating with, the annular chamber, said engine including means for operating said ignition plugs and pairs of intake and exhaust ports in timed relationship with the rotation of said shaft.

UNITED STATES PATENT OFFICE v CERTIFICATEOF CORRECTION Dated June 20, 1972 Patent No. 3 670 705 Inventor($) Masahiro SAITQ It is certified that error appears in the above-identified" patent. and that said- Letters Patent are hereby corrected as shown below:

r- Page 1 In the heading add the following Priority data:

-[30] Foreign Application Priority Data April 10,-1970fiapani-Qu..Q.Q....;... ..3 0316/70.--

Signed and sealed this 5th day of December 1972. I

(SEAL) Attest:

ROBERT GOTTSCHALK Attesting Officer Commissioner of Patents

Claims

1. A rotary engine comprising: a. an engine housing having an annular chamber; b. a power take-off shaft journaled at the axis of said annular chamber; c. a first rotor member and a second rotor member disposed oppositely to each other and loosely mounted for rotation on said shaft; d. a plurality of runners provided on each of said rotor members in circumferentially spaced fashion and slidably inserted in said annular chamber, the runners on the first rotor member alternating with those on the second rotor member such that two adjacent runners and the inner wall of said annular chamber define a gas actuated area; e. first and second power transmitting means fixedly connected to said shaft; f. first means causing the first and second rotor members to engage respectively with the first and second power transmitting means so as to prevent said transmitting means from idly moving backward with respect to said rotor members; g. second means causing the first and second rotor members to engage with the engine housing so as to prevent the backward idle movement of the rotor members; h. a pair of third means causing the rotor members to engage with the engine housing so as to prevent the forward idle movement of the rotor members while the rotor members are kept stationary; i. means for operating the third means to disengage the rotor members from the engine housing so as to allow the rotor members to move forward; j. means for connecting the running rotor member with the shaft to prevent the shaft from idly moving forward with respect to the running rotor member; k. at least one intake port on the annular chamber for introducing expansible gas into said gas actuated areas; and l. at least one exhaust port on the annular chamber for exhausting used gas from the actuated areas.

2. The rotary engine according to claim 1 wherein said connecting means comprises a gear wheel fixed to the shaft and telescopically movable between the rotor members and having on the both sides bevel gear teeth engageable with bevel gear teeth provided on the inner sides of the rotor members, said bevel gear teeth of the gear wheel being formed so as to engage with those of the rotor members while the rotor members are running and to disengage from those of the rotor members while the rotor members are kept stationary, whereby the gear wheel selectively engages with the running rotor members to connect said running rotor members with the shaft so as to prevent the idle forward movement of the shaft.

3. The rotary engine according to claim 2 wherein each of said third means comprises ratchet teeth arranged coaxially with the shaft on the inside of the engine housing and depressible pawls provided circumferentially on each of the rotor members so as to engage the corresponding ratchet teeth while the rotor members are kept stationary; and said operating means comprises a plurality of disengaging members projecting laterally from each of the power transmitting means and arranged thereon in circumferentially spaced relationship to depress the pawls of the rotor members so as to disengage the rotor members from the corresponding power transmitting means while the rotor members are rotated.

4. The rotary engine according to claim 1 wherein said connecting means comprises first ratchet teeth arranged coaxially with the shaft on each of tHe power transmitting means, a plurality of first pawls provided and circumferentially spaced on the corresponding rotor member to engage with the first ratchet teeth so as to prevent the forward idle movement of the shaft while said corresponding rotor member is turning, and first disengaging members provided and circumferentially spaced on the other rotor member to disengage the first pawls from the first ratchet teeth while said corresponding rotor member is kept stationary.