US3096746A

US3096746A - Intermediate half bearing for rotary mechanisms

Info

Publication number: US3096746A
Application number: US56369A
Authority: US
Inventors: Ferdinand P Sollinger
Original assignee: Curtiss Wright Corp
Current assignee: Curtiss Wright Corp
Priority date: 1960-09-16
Filing date: 1960-09-16
Publication date: 1963-07-09
Anticipated expiration: 1980-07-09
Also published as: CH386174A; GB974430A

Description

July 9, 1963 F. P. SOLLINGER 3,096,746

E HALF BEARING FOR ROTARY MECHANISMS 3 Sheets-Sheet 2 INVENT R. FERDINAND F suLLlKlsl-zn aw, *QMJMJ/W ATTDRNEY5 y 9, 1963 F. P. SOLLINGER 3,096,

INTERMEDIATE HALF BEARING FOR ROTARY MECHANISMS Filed Sept. 16, 1960 5 Sheets-Sheet 3 R HVVENTDR.

. FERDINAND F! EEILLINEER W4 PM,

ATTORNEYS United States Patent C) 3,096,746 INTERMEDIATE HALF BEARWG FOR RGTARY MECHANHSM Ferdinand P. Sollinger, Wayne, N..l., 'assignor to Curtiss- Wright Corporation, a corporation of Delaware Filed Sept. 16, 1960, Ser. No. 56,369 Claims. (Cl. Hit-8) The present invention relates to hearing means for rotary mechanisms and more particularly to an intermediate bearing for use with rotary mechanisms comprising two units which are arranged in tandem relationship and having a common one-piece shaft.

Although this invention is applicable to and useful with almost any type of a multi-unit rotary mechanism modifications which would be obvious to a person skilled in the art, the invention is equally applicable to other types of rotary mechanisms.

The present invention is particularly useful in rotary mechanisms of the type which comprise an outer body having an axis, axially-spaced end walls, and a peripheral wall interconnecting the end walls. In such rotary mechanism the inner surfaces of the peripheral wall and end walls form a cavity, and the mechanism also includes an inner body or rotor which is mounted within the cavity between its end walls.

The axis of the inner body or rotor is eccentric from and parallel to the axis of the cavity of the outer body, and the rotor has axially-spaced end faces disposed adjacent to the end walls of the outer body, and a plurality of circumferentially-spaced apex portions. The rotor is rotatable relative to the outer body, and its apex portions substantially continuously engage the inner surface of the outer body to form a plurality of working chambers which vary in volume during engine operation, as a result of relative rotation between the rotor and outer body.

The inner surface of the peripheral wall of the outer body has a multi-lobed profile which is preferably of an epitrochoid and the number of lobes of this epitrochoid is one less than the number of apex portions of the inner body or rotor.

By suitable arrangement of ports, such rotary mechanisms may be used as fluid motors, compressors, fluid pumps, or internal combustion engines. The invention is of particular importance when employed with a rotary mechanism which is designed for use as a rotating combustion engine, and accordingly, will be described in combination with such an engine. As the description proceeds, however, it will be apparent that the invention is not limited to this specific application.

When the rotary mechanism is designed for use as a rotating combustion engine, such engines also include an intake passage means for administering a fuel-air mixture to the variable volume working chambers, an exhaust passage means communicating with the working chambers, and suitable ignition means so that during engine operation the working chambers of the engine undergo a cycle of operation which includes the four phases of intake, compression, expansion, and exhaust. This cycle of operation is achieved as a result of the relative rotation of the inner body or rotor and outer body and for this purpose both the inner body or rotor and outer body 3,096,746 Patented July 9, 1963 may rotate at different speeds, but preferably the inner body or rotor rotates while the outer body is stationary.

For efiicient operation of the engine, its Working chambers should be sealed, and therefore an effective seal is provided between each rotor apex portion and the inner surface of the peripheral Wall of the outer body, as well as between the end faces of the rotor and the inner surfaces of the end walls of the outer body.

Between the apex portions of its outer surface the rotor has a contour which permits its rotation relative to the outer body free of mechanical interference with the multi-lobed inner surface of the outer body. The maximum profile which the outer surface of the rotor can have between its apex portions and still be free to rotate without interference is known as the inner envelope of the multi-lobed inner surface, and the profile of the rotor which is illustrated in the accompanying drawings approximates this inner envelope.

For purposes of illustration, the following description will be related to the present preferred embodiment of the engine in which the inner surface of the outer body defines a two-lobed epitrochoid, and in which the rotor or inner body has three apex portions and is generally triangular in cross section but has curved or arcuate sides.

It is not intended that the invention be limited, however, to the form in which the inner surface of the outer body approximates a two-lobed epitrochoid and the inner body or rotor has only three apex portions. In other embodiments of the invention the inner surface of the outer body may have a different plural number of lobes with a rotor having one more apex portions than the inner surface of the outer body has lobes.

The output of conventional piston and cylinder reciprocating type internal combustion engines can be increased by adding additional piston and cylinder combinations. Similarly, the output of rotary combustion engines of the type described can be increased by adding rotor and housing units. This may be done, for example, by coupling the shafts of a plurality of rotor and housing units together. Such a split shaft construction however, is structurally weak compared to a single-piece shaft.

In order that a single-piece shaft could be used in a multi-unit rotary combustion engine, it has been pro posed that no bearing be used for the shaft intermediate the eccentric portions of the shaft. This was found to be unsatisfactory since the high level of gas forces developed in such mechanisms resulted in deflection and bending of the shaft having obvious deleterious effects on the shaft. When deflected, the shaft also tended to be tilted or cooked in the end bearings which put an undesirable stress and strain on the end bearing resulting in poor shaft support and undue wear and eventual destruction of the end bearings.

It has also been proposed that a single-piece shaft be used which has a thickened cross section intermediate the eccentric portions of the shaft. Although this will reduce somewhat the bending and deflection of the shaft, deflection which does occur subjects the end bearings to an undesirable amount of stress resulting in poor bearing support of the shaft and eventual failure of the end bearmgs.

In the case of a one-piece shaft for a multi-unit rotary engine, a sectional or split bearing which included some means of removably engaging the sections of the hearing has been proposed. When using such sectional bearings intermediate the eccentric portions of the shaft of the multi-unit rotary engine, it was found necessary to construct the intermediate housing of a plurality of parts, generally two parts.

A two-piece intermediate housing was necessary in order to assemble the sectional bearing within the intermediate wall since to provide a bore in a unitary housing of sufficient diameter to permit assembly of the sectional bearing, would result in a decrease of bearing contact between the rotor and outer body end walls. The use 'of' such anenlarged bore would result in locating the oil seal" a substantial distance from the shaft, Whereas in order to reducethe centrifugal forces on the oil seal it is generallyrec'o'gnized' that the oil seal should be located adjacent-the inner edge of therotor and as close as possible to the shaft.

A two piec'eintermediate housing wall required additional cooling passages, one for each portion of the housinjg' intermediate wall, as Well as bolt means for joining the intermediate housing wall parts. This results in a multi unit construction having a relatively long length and a unit having 'an' increased number of parts.

In* accordance with the present invention, asemi-circula'r intermediate shaft bearing is provided which leads to new, useful and unexpected results.

In accordancewith the present invention the lobes on the outer body epitrochoid, the'intake ports, the exhaust ports and the combustion phases for two rotary engines are located so that when viewed along the axis of these units, they are substantially aligned behind one another.

The expanding gas force resulting from the combustion phase, will for each rotary combustion unit be in the same'direction on the rotor. The present invention contemplates the use of a semi-circular bearing for supporting'th'e portion of the shaft intermediate the eccentrics against that gas force.

The above alignment of elements and combustion phases-in combination with the semi-circular bearing permits the use of a single-piece relatively small diameter shaft which will resist bending and deflection substantially as well as-when the sectional type bearing discussed previously is used; The present invention has, however, an a'dditional advantage that the sectional bearing does'non in that the present semi-circular bearing can be used with a unitary inter-mediate housing, thereby reducing the overall length and complexity of the multi-unit combination. The semi circular bearing of the present invention can be easily assembled within the outer body intermediate" walls and requires a bore in the housing which is only slightly: greater than the diameter of the eccentric portion on the shaft. Thus, maximum permissible bearing contact between the rotor and the end walls'of' the outer body is maintained.

Thesemi circular bearing of the present invention providesa shaft which will resist gas deflection better than" a single-piece shaft having a thickened portion intermediate its eccentrics and will, therefore, prevent the end'bearings'front being subjected to undesirable wear and tear.

In view of the foregoing, it is an object of this invention to provide a'bearing'for a shaft intermediate its eccentric portions'which can be easily, expeditiously and efficiently assembled.

It is a further object of this invention to provide an intermediate bearingfor supporting a shaft intermediate its eccentric portions have novel means for preventing axial and rotative movement of the bearing with respect to'the outer member.

It isa' still further object of this invention to provide a bearing for supporting a shaft intermediate its eccentric portions which, when assembled within an outer member, is keyed to the outer member to prevent axial movement of thebearing with respect t'o the outer member.

iIt is another object of this invention to provide a semi circularbearing for supporting a shaft intermediate its eccentric portions having a semi-circular diameter such that itcan be assembled with the associated outer --member having a bore only slightly greater than the ,e'ccentric portions which will efficiently and effectively support its associated shaft from the stresses induced by the gas pressures developed during the combustion phase.

Another object of this invention is to provide a bearing for supporting a shaft intermediate its eccentric portions wherein the shaft is associated with a plurality of rotary combustion units having combustion phases located with respect to the bearing such that a semi-circular bearing may be used.

Still another object of this invention is to provide a bearing for use with two rotary combustion phases located with respect to the outer body in a manner whereby a semi-circular hearing may be mounted in the outer member in a position opposite to the combustion phases for supporting ashaft intermediate-its eccentric portions from the gases developed during combustionz A still further object of the present invention is to provide a plurality of rotary'combustion units arranged in tandem wherein each unit has its combustion phase located in a position relative'to its outer member so that a bearing having a substantially semi-circular contour, having novel means for preventing axial and rotative movement, is mounted in the outer body in a position opposite to'the combustion phasestfor supporting a shaft from the combustion gas force to which it is subjected.

Additional objects and advantages ofthe invention will be set forth in part in the description which follows and in part will be obvious from the description or may be learned by practice of the invention, the objects and advantages being realized and attained by means of the instrumentalities and combinations particularly pointed out in the" appended claims.

The invention consists in the novel parts, constructions and improvements shown and described.

In accordance with this invention,.asingle-piece shaft having eccentric portions spaced along its length is provided with a semi-circular bearing means for supporting the shaft intermediate the eccentric portions.

Briefly described, the bearing means is used with a plurality of rotary engine units'having acommon onepiece power shaft andhaving their combustion phases in the same position relative to their outer bodies, the bearing means having a substantially semi-circular profile removably engaged with the intermediate wall of the outer body in a position opposite from the location of the combustionph-ases for supporting the single-piece-power shaft intermediate eccentric portions on the shaft.

The accompanying drawings, which are incorporated in and constitute a part of this specification,- illustrate one embodiment of the invention :and, together with the description, serve toexplain the principles of the .invention.

Of the drawings:- 7

FIGURE 1 is a sectional view taken-:along-l-ine 1--1 of FIGURE 2 showing two rotary mechanisms in tandem relationship. I I

FIGURE 2 is a section view taken along line 22 of FIGURE 1.

FIGURE 3' is a sectional view taken-along line 3-'3 of FIGURE 1.

FIGURE 4 is a sectional view taken-1along-line 4'4 of FIGURE 3 showing the intake port construction.

FIGURE 5 is a side View of the-intermediate bearing.

FIGURE 6 is anend view of the intermediate'bearing.

FIGURE 7 is a schematic view showing the intermediate bearing being assembled within the outer body.

It is to. be understood that both the foregoing general description and the renewing detailed description are 'exem'plary and explanatory but are not restrictive of the invention. v

Reference will now be made in detail to the" present preferred embodiment of the invention, an'cxarnpl'e'of which is illustrated in the accompanying drawings.

In accordance with the present invention, two rotary combustion engines are provided which are in side by-si'de or tandem relationship; As embodied and shown in FIG- URES 1-3, the present preferred embodiment includes a rotary combustion engine unit comprising in tandem arrangement a pair of rotating combustion engines A and B, FIGURES 1-2, arranged and disposed coaxially of one another.

In order to simplify the drawings, portions of the engines A and B not essential to an understanding of the invention have been omitted and corresponding parts in engines A and B are designated by the same reference numerals, the reference numerals for engine B being primed. Accordingly, it will be understood that the section taken along 22 of FIGURE 1 and shown in FIG- URE 2 would serve equally well for engine B.

Both of the rotating combustion engines are of similar construction, and each comprises a generally triangular rotor 10, having .arcuate sides which are eccentrically supported for rotation within an outer body 12, 12'. Although in the present preferred embodiment the

outer body

12, 12 is fixed or stationary, the engine is not limited to this preferred embodiment, e.g., either body may be stationary or both bodies may rotate, one relative to the other.

As shown in FIGURES l and 2 and as here preferably embodied, the outer body 12, 12' comprises a peripheral wall 18, 18' the inner surface of which is substantially an epitroohoid in geometric shape, and includes two arched lobe-defining portions or lobes, the two epitrochoids being coaxial with their lobes aligned. In other words, the lobes of one epitrochoid are directly behind the lobes of the other epitr-ochoid when viewed in a direction parallel to the axis. The outer body also comprises a pair of axially-spaced end walls, 22, 22' and 24, 24' which are disposed on opposite sides of the

peripheral wall

18, 18. The two end walls 24, 24' have a one-piece construction forming an intermediate housing wall member.

The end walls 22, 22' and 24, 24' support a common shaft 26, the geometric center of which is coincident with the axis 16 of the outer body 12, 12'. This common shaft 26 is supported for rotation by the end walls 22, 22' on end bearings 28, 28'. A pair of eccentrics 30, 31' are rigidly attached to the common shaft 26, and the rotor 10, 10' is supported for rotation or rotatably mounted upon the eccentric 30, 31' by suitable anti-friction bearings 32, 32'. The

axis

14, 14 of the engine eccentrics is displaced a distance e from the axis 16.

As shown in FIGURE 1, an internally-toothed or ring gear 34, 34' is attached to the bearing 32, 32' which in turn is rigidly attached to the rotor 10, 10 to prevent relative rotation of the gear and rotor. The

ring gear

34, 34 is in mesh with an externally-toothed or

pinion gear

36, 36" which is rigidly attached to the

stationary end wall

22, 22 of the

outer body

12, 12.

From this construction it may be observed that the

gearing

34, 34' and 36, 36' does not drive or impart torque to the crankshaft but merely serves to index or register the position of the rotor with respect to the outer body and removes the positioning load which would otherwise be placed upon the apex portions of the rotor 10, 10';

As shown most clearly in FIGURE 2, the rotor 10, 10' includes three apex portions 38, 38' which carry radially movable sealing members 40, 40'. The sealing

members

40, 40 are in substantially continuous sliding, gas-sealing contact with the inner surface 20, 20' of the outer body 1 2, 12' as the rotor 10, 10 rotates within and relative to the

outer body

12, 12. The end walls of the rotor have mounted therein gas-sealing means 76, 76' so that by means of the rotation of the rotor 10, 10' relative to the outer body 12, 12' three variable volume working chambers 42, 42' are formed between the peripheral working faces 44, 44 of the rotor '10, 10' and the inner surface 20, 20' of the outer body 12, 12'. As embodied in FIGURE 2, the rotation of the rotorjreiative to the outer body is counter-clockwise and is so indicated by an arrow.

A spark plug 46, 46' is mounted in the

peripheral wall

18, 18 of the outer body 12, 12', and at the appropriate time in the engine cycle, the spark plug 46, 46' provides 6 ignition for a compressed combustible mixture which on expansion, drives the rotor in the direction of the arrow.

As shown most clearly in FIGURES l, 3 and 4 end Wall 24, 24' is provided with an intake port or

passage

48, 48 and the

peripheral wall

18, 18 is provided with an exhaust port 56, 50. As the rotor rotates, a fresh charge is drawn into the working

chambers

42, 42 through the

intake ports

48, 48. This charge is then successively compressed, ignited, expanded, and finally exhausted through the exhaust port 50, 50.

With reference to FIGURE 4 it can be seen that the adjacent end walls 24, 24' each have an intake port 48, 48' wherein these ports merge with a common inlet 47 at the outer periphery of the housing members. This arrangement provides a very compact arrangement for supplying a fresh charge to the working chambers of the engine.

All four successive phases of the engine cycle: intake, compression, expansion, and exhaust, take place within each one of the variable volume working chambers 42, 42' each time the rotor 10, 10 completes one revolution within the outer body, and for each revolution of the rotor, the engine completes a cycle.

The working faces 44, 44 of the rotor 10, 10' are provided with cut-out portions or channels 52, 52' which permit combustion gases to pass freely from one lobe of the epitrochoi-dal

inner surface

20, 20 to the other lobe, when the rotor is at or near the top dead center compression position. Also, the compression ratio of the engine may be controlled by adjusting the volume of the

channels

52, 52.

Since the gear ratio between the ring gear 34, 34' and the pinion gear 36, 36' is 3:2, each time the rotor 10, 10 completes one revolution about its own axis 14, 14' the shaft 26 rotates three times about its axis 16.

In accordance with this invention certain elements of the rotary combustion engines are aligned or arranged with respect to one another such that a semi-circular bearing can be used to provide new, useful and beneficial results.

In the preferred embodiment of the invention which is illustrated in the drawings, eccentrics 3t), 3% and perforce the rotors 10, 10' are rotatively displaced 180 with respect to one another. This is most clearly illustrated in FIGURE 1 and FIGURE 2. When the eccentrics are rotatively displaced 180 as illustrated, the loads on the intermediate portions of the shaft resulting from the centrifugal forces on the

eccentrics

30, 30, is at a minimum. On the other hand, the lobes on the inner surface 20, 20', the

intake port

48, 48, the exhaust port 50, 50 and the ignition means or spark plug 46, 46' are arranged so that when observed on a line parallel to the axis they are located one behind the other.

It will be recognized by those skilled in the art, however, that substantial alignment is all that is necessary. For example, the ignition means 46, 46 could be located on opposite sides of the adjacent junction point of the two lobes of their respective engine units without changing the relative position of the combustion phases for each engine. This arrangement of elements is such that although rotors are displaced 180 angularly with respect to one another and, therefore, the working chambers are also angu-larly displaced 180 with respect to one another, that the working phases of the units will always occur in working chambers having the same location with respect to the housing.

In other words, it is obvious that the combustion phase will always occur in the lower portion of [the housing adjacent the ignition means 46, 46 for each engine. Thus, the maximum gas pressure on the rotor, i.e., created by the combustion phase, will, for each engine unit, be in a direction which is upwardly or generally to- Ward the intake and exhaust ports. The shaft will, as

to the ignition means 46, 46'.

.face 64 on the half-bearing 56.

ragoaa-va-e in the same direction from each of the rotors 10, -of the twoengineunits.

The intermediate bearing means, as herein embodied,

centrics 30, 30'. It will be appreciated by those skilled in the art that where a one-piece shaft is used, it would not 'be possible to locate a single-piece annular-bearing in this position in a rotary mechanism of the-type described.

The half-bearing 56, as embodiedhas substantially a the shaft 26,on the side of the shaft which is opposite Means are provided in accordance with this invention for removably attaching the 'bearing to the housing.

As shown in FIGURES 1 and 4, an intennediate'housing member is formed from side walls 24, 24' which are joined by an annular flange or portion 60-which has a 'bore therein forming bearing engaging surface '62 for continuous engagement with the housing tengaging surrface 64 of the bearing. This bore'has virtually the identical radius of curvature as the housing engaging sur- The half-bearing is also provided with a tapered key means for engagement with the key-way 68 in the flange 60 of the housing. It can be observed in FIGURES 3 and 7 that'the key 66'hasthe same radius of curvature as :the outer surface 64 of the half-bearing but that the center 59 of the radius of key 66 is displaced toward the halfbearing from the center -61'of the bearing such that the key 66 is, in eifect, tapered with respect to the housexcessively large opening in'the end wall 24, 24' and hence without sacrificing a substantial amount of bearing surface between the end walls of the outer bodyand the rotor.

The preferred manner of assembling the semi-circular "bearing to the housing or outer member is shown in FIG- URE7. Although the bearing'56 has been described as semi-circular or a half-bearingas illustrated it is an armate segment which is somewhat less than a semi-circle.

Accordingly, the expressions semi-circular and *half bearing in the claims are'intended to be construed sufficiently broad to include a hearing which is somewhat less than a semi-circle. The half-bearing 56 is assembled by firstsplaoing the shaft 26 in the'rotative position'wi-thin the intermediate housing wall 24, 24', as shown in FIG- URE '7, and then laterally displacing the shaft, downwardly, as viewed in FIGURE 7, to the maximumextent permitted .-by the bore 62 in the housingwall. The half- .bearing 56 can then be moved axially overthe shaftinto position within the housing intermediate wall, as illustrated in FIGURE 7, with the key 66 in alignment with the key-way 68. :The semi-circular bearing need then' on'ly be moved a slight radial distance outward to engage the key 66 in the key-way 68.

As illustrated in FIGURE 7, the fact that the-key 66 randtrbearing'. engaging surfaces 62 have the :same: radius permits the bearing 56 to be assembled within the housing wherein the housing has a boreonly slightly larger than the diameter of the eccentric. By this relationship of curvatures, hereinbefore discussed, it is possible to provide a bore in the housing which permits maximum bearing contact between the end walls of the rotor 10, 10" and the intermediate end Walls 24, 24' of the outer memi8 -ber. This arrangement-salsmpermits the :oil seal 75, 75' ato be locatedaas :close as" rpossiblezto'l theshaft J26 thereby :reducing the centrifugal forceswnzthe .oiliseals.

After the intermediate bearing 56 has been assembled within the housing the rotor 10, 1'0 'with its bearing 32,

32' may be assembledromthe eccentrics 30, 30' and a the peripheral :

walls

18, 18 and-the end walls -22, 22':of the :outerbody placed in position. :Finally, the'end bearings 128, 28 canlbe bolted -or 'other-wise secured to .the end in walls -22, :22" of -theouter 'body.

'The key and key-way combination I66, 68 will, of course, preventaxial movement and/ or tilting-of the bearing within the honsing and insures that the bearing "will remain inucontinuous bearing contact with theshaft. It will beappreciated "-bythose skilled in'theart that'the invention is not limited -to a-construction where the key :ison'the bearing and the key-way i-n the housing and that-these elements may be reversed without departing from the principles of this invention.

In" order to maintain the bearing in assembled relationship with the housing during subsequent assembly steps --and for-preventing rotation of the bearing with respect to thesha'ft, means are' provided for locking the half-bearing to the housing. As ernbodied herein, this means comprises a screw means70 cooperating with aperture 72 in the housing-and threaded" aperture 74 in-the bearing. The screw means will, in an obvious manner, maintain the bearing andthe housing in tight "locking engagement.

' outer portions of said'firsttand saidtintermediate wall to form a Ifirst cavity between and, a second peripheral wall secured 'totand disposed between the outer portions of said second and. saidlintermediate wall toform a second cavity; a one-piece shaft coaxial with saidcavities and having apair o'f. eccentric portions, one'for each of said cavities; first and secondrotor members extending within saidfirst and secondv cavities respectively with each rotor 7 member. being journaledtonthelassociated shaft eccentric,

each rotor member having a plurality of. circumferentiallyspaced :apex1por tions .forrengagement with the inner surface lof its associated ,peripheral wall to divide the portions of its associated cavity between said rotor member andinner ,surfacerintoa pluralityof working chambers whichvary. in volume upon rotation ofthe rotor member .,-relat'ive.to .the :housing, saidfhousing fhaving intake and exhaust .ports communicating with theworking chambers .of .saidfirstcavity landihaving; intakeand exhaust ports vcommunicating withthe working chambers of the second cavitywith correspondingports of said first and second cavities.being:disposed.substantially: one behind the other when viewed in a directionparallelto said axis; and a semi-cylindricaL-half bearing -carried'by said intermediate wall for; bearing engagement with theportion of the shaft .between-said-shaft eccentrics and on theside of saidshaft forsuppontingsaid shaft portion against deflection by the forces transmitted against the shaft :by the rotor resulting from .the highgas pressures withineach workingchamber following combustion therein.

2. Arot-ary combustion engine comprising ,a multipart hou'sin-glhaving first andsecond axially-spaced end walls-an intermediate wall, acfirst peripheral wall secured to and disposed between the outer portions of said first and said intermediate wall to form a first cavity therebetween and a second peripheral wall secured to and disposed between the outer portions of said second and said intermediate Wall to form a second cavity therebetween co-axial with said first cavity; a one-piece shaft co-axial with said cavities and having a pair of eccentric portions, one for each of said cavities; first and second rotor members extending within said first and second cavities respectively with each rotor member being journaled on the associated shaft eccentric, each rotor member having a plurality of circumferentially-spaced apex portions for engagement with the inner surface of its associated peripheral wall to divide the portions of its associated cavity between said rotor member and inner surface into a plurality of working chambers which vary in volume upon rotation of the rotor member relative to the housing, said housing having intake and exhaust ports communicating with the working chambers of said first cavity and having intake and exhaust ports communicating with the working chambers of the second cavity with corresponding ports of said first and second cavities being disposed substantial-1y one behind the other when viewed in a direction parallel to said axis; and a semi-cylindrical half bearing carried by said intermediate wall for bearing engagement with the portion of the shaft between said shaft eccentrics and on the side of said shaft for supporting said shaft portion against deflection by the forces transmitted against the shaft by the rotor resulting from the high gas pressures within each working chamber followed combustion therein, and said semi-cylindrical hearing and said intermediate housing having a key and keyway means cooperating therewith for preventing axial movement of said semi-cylindrical bearing means with respect to said intermediate wall.

3. A rotary combustion engine comprising a multi-part housing having first and second axially-spaced end walls, an intermediate wall, a first peripheral wall secured to and disposed between the outer portions of said first and said intermediate wall to form a first cavity therebetween and a second peripheral wall secured to and disposed between the outer portions of said second and said intermediate wall to form a second cavity therebetween coaxial with said first cavity; a one-piece shaft co-axial with said cavities and having a pair of eccentric portions, one for each of said cavities; first and second rotor members extending within said first and second cavities respectively with each rotor member being journaled on the associated shaft eccentric, each rotor member having a plurality of circumferentiallyspaced apex portions for engagement with the inner surface of its associated peripheral wall to divide the portions of its associated cavity between said rotor member and inner surface into a plurality of working chambers which vary in volume upon rotation of the rotor member relative to the housing, said housing having intake and exhaust ports communicating with the working chambers of said first cavity and having intake and exhaust ports communicating with the working chambers of the second cavity with corresponding ports of said first and second cavities being disposed substantially one behind the other when Viewed in a direction parallel to said axis; and a semi-cylindrical half bearing carried by said intermediate wall for hearing engagement with the portion of the shaft between said shaft eccentrics and on the side of said shaft for supporting said shaft portion against deflection by the forces transmitted against the shaft by the rotor resulting from the high gas pressures within each working chamber following combustion therein, said semi-cylindrical bearing having an intermediate wall engaging surface and a key tapered with respect to said engaging surface and extending radially from said engaging surface for preventing axial movement of said semi-cylindrical bearing.

4. A rotary combustion engine as defined in claim 3 wherein the intermediate Wall has a bearing engaging surface having the same radius of curvature as the key.

5. A rotary combustion engine as defined in claim 4 including means for preventing rotative movement of said semi-cylindrical bearing with respect to said intermediate Wall.

6. A rotary mechanism comprising a plurality of units each unit having a hollow outer body on a common axis, axially-spaced end walls, and a peripheral wall interconnecting the end walls; each unit also having an inner body mounted within the outer body for rotation relative to the outer body on an axis eccentric, spaced from and parallel to the axis of the outer body; each inner body having end faces disposed adjacent to the end wall and a plurality of circumferentially-spaced apex portions in sealing engagement with the inner surface of the peripheral wall to form a plurality of working chambers between the inner vbody and the peripheral wall which vary in volume upon relative rotation of the inner body within the outer body, the inner bodies for each unit being mounted on angularly displaced eccentric portions of a common single-piece shaft, means for forming combustion phases for each unit in the same position relative to their outer bodies so that the combustion gases will be directed against each inner body in the same direction and semi-cylindrical bearing means carried by said outer bodies for supporting said single-piece shaft intermediate said eccentric portions from deflection by the forces transmitted against the shaft resulting from the combustion gases.

7. A bearing for supporting the intermediate portion of a shaft in rotary mechanisms having a housing and a shaft with eccentric portions thereon mounted within the housing comprising: a substantially semi-circular profiled bearing surface and a substantially semi-circular pro filed housing engaging surface, said housing engaging surface including a key means having the same radius of curvature as said housing engaging surface, said key extending from one end to the other of said bearing and having its maximum radial depth disposed intermediate the ends of the bearing.

8. A rotary combustion engine comprising a multi-part housing having first and second axially-spaced end walls, an intermediate wall having a one-piece construction and an axial bore therein, a first peripheral wall secured to and disposed between the outer portions of said first and said intermediate wall to form a first cavity therebetween and a second peripheral wall secured to and disposed between the outer portions of said second and said intermediate wall to form a second cavity therebetween coaxial with said first cavity; a one-piece shaft co-axial with said cavities and having a pair of eccentric portions, one for each of said cavities; first and second rotor members extending Within said first and second cavities respectively with each rotor member being journaled on the associated shaft eccentric, said rotor members cooperating with their walls of the housing cavities to form a plurality of working chambers 'therebet-ween which vary in volume upon relative rotation of said rotor members and housing; means providing for combustion in said working chambers such that the maximum combustion gas forces on said rotor member are in substantially the same direction relative to the axis of said shaft; and a semi-circular bearing carried by said intermediate wall for hearing engagement with the portion of the shaft between said shaft eccentrics and on the side of said shaft for supporting said shaft portion against said combustion gas forces.

9. In combination with a rotary mechanism having a housing with a bore and a shaft with eccentric portions spaced axially of said shaft, a bearing comprising: a semi-circular housing engaging surface, said housing engaging surface including key means, said key means, said housing engaging surface and said bore having virtually identical radii of curvature said radii of curvature being the minimum permissible radii for passing said eccentrics through said bore.

10. A rotary combustion engine comprising a multi- 11' part housing having first and second axially-spaced end walls, an intermediate wall having an axial bore therein, afirst peripheral Wall secured to and disposed between the outer portions of said first and said intermediate wall to form a' first cavity therebetween and a second periphenal wal'l secured to and disposed between the outer portions of said second and said intermediate wall to form a second-cavity therebetween co-axial with said first cavity; a shaft coaxial with said cavities and having a pair of eccentric portions, one for each of said cavities; first and second rotor membe-rsextending within said first and second cavities respectively with each rotor member being journaled on the associated shaft eccentric, each rotor member having a plurality of circumferentiallyspacedapexportions for engagement with the inner surface of its associated peripheral wall to divide the portions ofits-asso'ciated cavity between said rotor member andinner surface into a plurality of working chambers which-vary in volume upon rotation of the rotor member relative to the housing,'sai'd housing having intakeand exhaust ports communicating with the working chambers of said first cavity (and having intake and exhaust ports communicating with the working chamber of the second cavity with corresponding ports of said first and second cavities being disposed substantially one behind the other vwhen viewed in a-direction parallel to said axis; and an .arcuate bearing segment carried by said intermediate wall for hearing engagement withthe portion of the shaft between said shaft eccentrics and on the side of said shaft for supporting said shaft portion against deflection by the forces transmitted-against the shaft by the rotor members resulting from the high gas pressures within each working chamber following combustion therein.

References Cited in-the file of this patent UNITED STATES PATENTS 90,156 Daniels May 18, 1869