CA2188126A1 - Reciprocating machine - Google Patents
Reciprocating machineInfo
- Publication number
- CA2188126A1 CA2188126A1 CA 2188126 CA2188126A CA2188126A1 CA 2188126 A1 CA2188126 A1 CA 2188126A1 CA 2188126 CA2188126 CA 2188126 CA 2188126 A CA2188126 A CA 2188126A CA 2188126 A1 CA2188126 A1 CA 2188126A1
- Authority
- CA
- Canada
- Prior art keywords
- balance weight
- crankshaft
- weight means
- machine according
- piston
- 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.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
- F01B15/04—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 with oscillating cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
- F01B15/02—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 with reciprocating cylinders
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
A reciprocating machine comprising a working piston (10) and cylinder (12) assembly, a counter rotating crank drive having an inner crankshaft (22) carrying an eccentric in driving connection with the piston (10), the eccentric being rotatable within a big end bearing housing and the piston (10) being connected to said bearing housing, wherein the inner crank shaft (22) is eccentrically journalled about an intermediate axis in a single outer crankshaft (26) which is rotatably mounted relative to a crank case (28) of the machine for rotation about a main axis the inner crank shaft (22) having an inner gear (56) in engagement with an outer ring gear stationary (54) with respect to the crank case (28).
Description
~ WO 95129323 . ~, ~, . 'I
IStle: ~rt ,, ~ Machinel This invention relatcs to IC~ UlU aLi~l~; r~achines, h.,.c;~l~l referred to as being of the kind specified, comprising a working piston and cylinder assembly, a counter rotating crarlk drive having an inner crankshaft carrying an eccentric in driving ~nnn~m with the piston, the eccentric being rotatable within a big end bearing housing and the piston being connected to said bearing housing.
The machine may be, for example, an internal or ex~ernal engine or a I , c~ ul.
GB-B-2û8û483 discloses a ~..u-u~Li--~ machine of the kind specified in which the eccentric is connected by spaced webs to opposed journals disposed on opposite sides of the eccentric whereby the inner crank is ~ journalled in two outer ~ r~ which are axially aligned and are rotatably mounted relative to a crarlkcase. The inner crankshaft has a gear associated with each journal and engaged with a respective stationary gear.
Such a machine suffers from the 1;~ that it is necessary accurately to align not only the axes of rotation of the two separate outer . .~. L~ rl~ but, in additdon, the ~ 6~ between the gears associated with the journals of the single crankshaft must be accurately ~, ' ~ L;ally mUtltallyaligned. The alignment of such relatively widely separated ~ to the required degree of accuracy is difficult to achieve in practioe. Moreover, it isrelatively expensive to , -, . r 1,,, c such an engine, not only because of the need to attempt to achieve such alignment, but because of the number of parts required. rl~lLh~ lul~, the overall size of the machine in the direction of the axis of rotation of the pair of outer ' ' ' is relatively great.
In addition, such a machme when having a single or a small number of pistorls is prone to vibration due to out-of-balance forces and cyclic illC~ aliLi.,il.
An object of the invention is to provide a machine of the kind specified whereby the above mentioned .l;~aJvd-lL~ are overcome or reduced.
A subsidiary object of the invention is to provide a machine of the kind specified woss/29323 2 1 ~ 1 26 ' wherein the above mentioned additional d;a~lVdlli~ .S are overcome or are }educed.
According to the present invention, we provide a lc~ilJIO d~ g machine of the kind specified wherein the inner crank shaft is ~ y journalled about an i~ axis in a single outer crankshaft which is rotatably mouMed relative to a crank case of the machine for rotation about a main axis, the iMercrank shaft having an imler gear in ~ ~ with an outer ring gear stationary with respect to the crank case.
The irmer and outer gears may be provided Ic~l,.,.,Li.~ with external and internal spur or ~elical or bevel gear teeth.
The outer crankshaft may be journalled in the crank case by two bearings disposed at positions spaced 1.,.,~ of the crankshaft and preferably disposed on opposite sides of said externally toothed gear.
The outer crankshaft may be provided with bearing means at positions spaced apart 1.. ~ lly thereof in which spaced apart journals of the im~er crankshaft are rotatably mounted.
Said spaced apart journals of the inner crankshaft may be disposed on opposite sides of said externally toothed gear.
The outer crankshaft may be provided with a cut-out to r ' the irmer gear.
The ecceMric may be mounted in cantilever by the inner crankshaft.
The inner crankshaft may be provided with a further journal, on the opposite side of the eccentric to the bearings whereby the inner cranlcshaft is rotatablymountedontheoutercrankshaft,saidfurtherjournalbeingec.. ~,1.; -'l~
relative to a sub-shaft and the sub-shaft being mounted for rotation relative to the crank case about the axis of rotation of the outer crankshaft.
The machine may have a further worlcing piston and cylinder aasembly, the further piston being connected to a further big end bearing housing within whichsaid eCCeMric is rotatable.
Alternatively, when the inner crankshaft is provided with said further journal rotatable relative to said sub-shaft, the machine may have a second -wo ssl2s323 r~
IStle: ~rt ,, ~ Machinel This invention relatcs to IC~ UlU aLi~l~; r~achines, h.,.c;~l~l referred to as being of the kind specified, comprising a working piston and cylinder assembly, a counter rotating crarlk drive having an inner crankshaft carrying an eccentric in driving ~nnn~m with the piston, the eccentric being rotatable within a big end bearing housing and the piston being connected to said bearing housing.
The machine may be, for example, an internal or ex~ernal engine or a I , c~ ul.
GB-B-2û8û483 discloses a ~..u-u~Li--~ machine of the kind specified in which the eccentric is connected by spaced webs to opposed journals disposed on opposite sides of the eccentric whereby the inner crank is ~ journalled in two outer ~ r~ which are axially aligned and are rotatably mounted relative to a crarlkcase. The inner crankshaft has a gear associated with each journal and engaged with a respective stationary gear.
Such a machine suffers from the 1;~ that it is necessary accurately to align not only the axes of rotation of the two separate outer . .~. L~ rl~ but, in additdon, the ~ 6~ between the gears associated with the journals of the single crankshaft must be accurately ~, ' ~ L;ally mUtltallyaligned. The alignment of such relatively widely separated ~ to the required degree of accuracy is difficult to achieve in practioe. Moreover, it isrelatively expensive to , -, . r 1,,, c such an engine, not only because of the need to attempt to achieve such alignment, but because of the number of parts required. rl~lLh~ lul~, the overall size of the machine in the direction of the axis of rotation of the pair of outer ' ' ' is relatively great.
In addition, such a machme when having a single or a small number of pistorls is prone to vibration due to out-of-balance forces and cyclic illC~ aliLi.,il.
An object of the invention is to provide a machine of the kind specified whereby the above mentioned .l;~aJvd-lL~ are overcome or reduced.
A subsidiary object of the invention is to provide a machine of the kind specified woss/29323 2 1 ~ 1 26 ' wherein the above mentioned additional d;a~lVdlli~ .S are overcome or are }educed.
According to the present invention, we provide a lc~ilJIO d~ g machine of the kind specified wherein the inner crank shaft is ~ y journalled about an i~ axis in a single outer crankshaft which is rotatably mouMed relative to a crank case of the machine for rotation about a main axis, the iMercrank shaft having an imler gear in ~ ~ with an outer ring gear stationary with respect to the crank case.
The irmer and outer gears may be provided Ic~l,.,.,Li.~ with external and internal spur or ~elical or bevel gear teeth.
The outer crankshaft may be journalled in the crank case by two bearings disposed at positions spaced 1.,.,~ of the crankshaft and preferably disposed on opposite sides of said externally toothed gear.
The outer crankshaft may be provided with bearing means at positions spaced apart 1.. ~ lly thereof in which spaced apart journals of the im~er crankshaft are rotatably mounted.
Said spaced apart journals of the inner crankshaft may be disposed on opposite sides of said externally toothed gear.
The outer crankshaft may be provided with a cut-out to r ' the irmer gear.
The ecceMric may be mounted in cantilever by the inner crankshaft.
The inner crankshaft may be provided with a further journal, on the opposite side of the eccentric to the bearings whereby the inner cranlcshaft is rotatablymountedontheoutercrankshaft,saidfurtherjournalbeingec.. ~,1.; -'l~
relative to a sub-shaft and the sub-shaft being mounted for rotation relative to the crank case about the axis of rotation of the outer crankshaft.
The machine may have a further worlcing piston and cylinder aasembly, the further piston being connected to a further big end bearing housing within whichsaid eCCeMric is rotatable.
Alternatively, when the inner crankshaft is provided with said further journal rotatable relative to said sub-shaft, the machine may have a second -wo ssl2s323 r~
woricing piston and cylinder assembly, the second piston being connected to a second big end housing within which a second eccentric is rotatable, the second eccentric being carried by a second journai which is ~ y joumailed in a second sub-shaft, which is rotatably mounted relative to the crani~case and by a second further journai and wherein the further journais are each in eccentric rotatable c :~lio..~L;~ with said sub-shaft with the respective further journais being disposed in a ~ d angular . ~ ' ' . such as ~ oppositely disposed.
Such a further joumai or journais may be provided if, for example, a power take-off shaft is required at the end of the machine provided with the further journal; or a second in-line piston and cylinder assembly is required; or two pistons or groups of pistons, each having a ~.~ cd eccentric, are mounted in axiai .cl ' . . for example to provide double the power input; or to couple two machine with different functions, for example an engine and a CCIIIII.-Ie~J~.
In aii such c^qses where a further journal is provided it is not necessary to provide a second pair of gears in qcc,.~qtir,n with the further journal.
r~ when the machine has a single or smail number of pistons it is prone to vibration due to outer baiance forces and cydic i..c, ' a~.~i;..~;l~, to overcome this additionai problem an imner baiance weight means may be provided to at least partly ~4 Ily balance the masses which are rotatable about the ' axis and an outer balance weight means may be provided to at least partly ~ balance the masses which are rotatable about the main axis.
Preferably the imner and outer baiance weight meanS are provided so that their respective resultant centre of gravity is co-axial with the ' axis and the main axis .~ 4.
Accordingly, the inner cranicshaft has an inner balance weight means and the outer crankshaft has an outer balamce weight means having its centre of gravity radiaily opposite the resultant centre of gravity of the inner cranicshaft and the inner balance weight means.
W0 95/29323 r~
~188126 The inner balance weight means may comprise firsl and second inner balance weight means disposed on either side of the piston centre line so as to avoid or reduce any couple around the piston centre line.
The inner balance weight means may comprise a single inner balance weight means or a pluraliy of In~itlltii"-~lly spaced inner balance weight means.
Said pluraliy of inner balance weight means may comprise first and second balance weight means l~ c;~ ly spaced on opposite sides of the piston or pistons.
The single, or at least one of the, inmer balance weight means may comprise a pluraliy of radially spaced balance weights.
The outer balance weight means may comprise a single outer balance weight means or a pluraliy of 1~ " lly spaced outer balance weight means.
Said pluraliy of outer balance weight means may comprise first and second outer balance weight means disposed at positions spaced apart '-~ei~ 'Iy of the outer crankshaft.
The single, or at least one of the, outer balance weight means may comprise a pluraliy of radially spaced balance weights.
The outer balance weight means may comprise a first and a second outer balance weight means each having a centre of graviy disposed at positions spacedapart 1~ " lly of the outer crankshaft and disposed on radially opposite sides thereo The balance weight or weights which comprise the single or said pluraliy of outer balance weight means may be disposed at any desired position or positions l~ Iy of the axis of rotation of the outer crankshaft and/or may be provided on an auxiliary element separate from the outer crankshaft and arranged to rotate therewith, such as an auxiliary drive shaft.
The auxiliary element may be mounted by bearing means and provided with a drive means so as to be driven by the outer crankshaft at the same speed as tbe speed of rotation of the outer crankshaft.
Where the machine has a sub-shaft at least part of the outer balance weight means may be provided thereon.
~ WO 9~/29323 2 1 8 8 t 2 6 . ~1 .
s The outer baiance weight means may comprise first and second y spaced outer balance weight means, the first l -~ ~C;h l ~ ly spaced outer baiance weight means may be provided on said outer crani~shaft and the second I ,, " '1~ spaced outer baiance weight means may be provided on said sub-shaft.
A ~ J.u.a~ machine ~ the invention will now be described by way of example with reference to the ~ drawings, wherein:
FIGURE 1 is a " ~ - cross-section through an internai, engine embodying the present invention;
Fi~GURE 1_ is a r ~ cross-section showing the engine of Figure 1 in more detaii;
FIGURE 2 is a r ~ ' y ~ ''~ end view of the engine of Figure 1;
FIGURE 3 is a ' " y cross-section through a second ~ i ' of the invention;
FIGURE 4 is a r~a~ y cross-section through a third . ' . " of the invention;
FIGURE S is a, ' _ cross-section through a founh L - "
showing an internal . ' engine of narrow V-2 5v - .
FIGURE 6 is a ' ~ - end view of the engine of Figure S;
FIGURE 7 is a ~' v cross sc~liundi view through a fifth .I....I:. -: of the invention showing an engine of h~vin opposed cylinder FIGURE 8 is a ~ cross-section showing an engine as described with reference to Figure 7 in more detail;
FIGURE 9 is a,' ., cross-section through another ~ L
of the invention;
FIGURE 10 is a ' ~ - cross-section showing a further internai combuston engine embodying the invention;
FIGURE lO~L shows the engine of Figure 10 in more detail;
wo9s/~s323 2 1 88 1 26 FlGURE l l is a ~ , A ",~ cross-section through a further ~ -~ ,o.l;,. ,:
of the invention;
FIGURE 12 is a ~ cross-section through a still furtber ' ~ ' of the invention;
FIGURE 12~Lshows the engine of Figure 12 in more detail;
FIGURE 13 is a ' ~ cross-section of a yet further .l.
of the invention; and FIGURE 14 is a d;..,j. transverse cross-section of the engine of Figure 13.
The same reference numerals have been used Lll-l "' the drawings to refer to .,ull~-r " parts.
Referring to Figure 1, 1~Land 2, there is shown an engine which comprises a wûrking piston and cylinder assembly ~ a piston 10 c. ;~,.u~l,l~, within a cylinder 12 provided with a cylinder liner 14. A ~ chamber 16 is provided in . .,..~iu..~l manner.
The piston 10 is rigidly comnected to a rod 17 and is rigidly connected by the rod to a big end bearing housing 18 and is drivingly comnected to an eccentric 20 carried on an inner crankshaft æ rotatable abûut an ' axis Y-Y.
If desired the piston 10 can be connected by a ~little end" to the rod 17 but this is not necessary.
The inner crankshaft 22 carries f~rst and second l. ~ ly spaced imner balance weight means which each comprise an inner balance weight 24 which are disposed directly l ~ ' "y adjacent and on opposite sides of the eccentric 20 amd are arranged to balance the weight of the eccentric, piston bearing and housing assembly 20, 10, 17 and 18 so that the masses rotating about the axis Y-Y
have a resultant centre of gravity which is coincident with the axis Y-Y.
The inner crankshaft æ is ~crl~ntrirslly joumalled in an outer crankshaft 26 for rotation about the axis Y-Y. The outer crankshaft 26 is itself rotatably mounted in a crankcase 28 by main bearings 30, 32 for rotation about a main axisX-~
W0 95129323 r~
The outcr crankshaft 26 is relatively elongated and has first and secondjournals 34, 36 which are disposed at positions which are spaced l~ of the outer crankshaft and are engaged by the inner races of roller element bearings which provide the main bearings 30, 32. The outcr races being received in seats 38, 40 r~ in the crank case 28.
The outer crankshaft 26 is provided with plain bearings 41, 42 disposed in seats 44, 46 disposed at positions which are spaced l" ~ of the outer crankshaft 26 and are rotatably engaged with journals 48, 50 of the inner crankshaft 22 which are spaced I ~ , apart thereof so that the eccentric 20 is mounted in cantilever by the remainder of the imner crankshaft 22.
The outer crankshaft 26 is provided with a cut-out 52 to 7! ' ''''' ''''1~l~ an externally toothed spur or helical gear 54 fixed relative to the inner crankshaft Z
which meshes with a ~ ul l~ r " ~ internal ring gear 56 provided fixed relative to the crank case 28. If desired bevel gear teeth may be provided.
In operation, the inner crankshaft 22 rotates about its axis Y-Y in the opposite direction to the direction of rotation of the outer crankshaft 26 about its a~ds X-X. The gear ratio of the externally toothed gear 54 to the ring gear 56 is 2: 1 so that the inner crankshaft 22 rotates, relative to the outer crankshaft 26, in the opposite direction and at twice the speed to that at which the outer crankshaft 26 rotates relative to the crankcase. The geûmetric centre of the ecceMric 20, shown at Y-Y, IC,.;UIU~ ~ alorg a straight line indicated at A and the piston 10 thus accurately r~,~,;,u~u~ along its respective axis.
As the - . ..,~,. and operation of a counter rotating crank drive is well known, it will not be further described herein. Such a drive can be completely dynanucally balanced by inner counter weight means 24 and outer balance weight means now to be described.
Referring now to Figure 1, the outer crankshaft 26 is provided with a flywheel 57 which carries an outer balance weight means which comprises a frst outer balance weight means 58.
However, because of the cantilever design the balance weight means 58 is off-set axially relative to the masses to be balanced and to avoid an out-of-balance .
wo 9sl29323 r~ S c couple being created the weight 58 is made larger than needed for dynalnic balancing in a radial direction and a second outer balance weight means 60 is provided situated loneih~ n~lly outside the bearing 30 and radially opposite thefirst outer balance weight mearls 58. Thc t,, " '- of the first and second balance weight means 58, 60 are arranged so that the couple created by the off-centre position of the weight 58 is L~ d for by the weight 60 and the weights 58, 60 together ensure that the centre of gravity of the masses rotatingabout the axis X-X is coincident with the axis.
If desired, the weight 60 and/or the weight 58 may be provided in any suitable posiion along the outer crankshaft 26. r.~ uls either or both of the outer balance weight means 58 and 60 may be provided by a single weight or by a plurality of weights at different angular and/or 1~ 1 positions relative to the axis X-X so that the composite effect of the respective weight parts sumsto the desired mass and posiion.
For example, an altemative or additive position for weight 58 is indicated at 58' in Figure 1~, ln another example, shown in Figure 3, which is a section Ihrough an air cooled single cylinder diesel engine having a relatively long flywheel 57, i.e. a flywheel which is relatively long in the direction of the axis X-X, the first balarlce weight means 58 can be mounted on the inner face of the flywheel as shown at 58" instead of, or in addition to, a weight provided at a loQtion which LUII~:_r ' to the position of the first balance weight mearls 58' shown in Figure 1~, Of course, if a weight` is provided both at the location indicated at 58' inFigure l~and the location indicated at 58" the masses of the two weights is suchas to sum to the desired mass.
In another ex~unple, shown in Figure 4, where the flywheel 57 is formed by the rotor of a brushless generator, the first counter weight means can be fixed directly to a rotating canister C holding the pemmanent magnets of the brushlessgenerator (different magnet ~ul~ri5.1l~ a being shown in the top and bottom halves of Figure 4), as shown at 58"' in Figure 4. Again the weight shown at 58"' can be additive to or instead of the weight shown at 58 in Figure 4.
W0 95129323 r ~ 5 ~J~126 In another exarnple, where the engine has a drive to a camshaft and/or an oil pump or another auxiliary taken from the opposite end of the engine to the normal power take-off as is also illustrated in Figures 3 and 4 at 70, an auxiliary element or shaft ?0 is arranged to Qr y a weight 58_ which, as in the previouslydescribed examples, Qn provide tbe whole, or part of the weight required in ...... l. -~;.. with weights at least at one of the other loQtions described ,;..I,.,f~ to achieve dynamic balance of the masses rotating about Ihe axis X-X, Tl~e mass of the balance weight 60 is d~,t~,...,...'d so as to balance the 10't~ ' couple and is disposed radially opposite the balance weight 58, the mass of which is increased over that necessary to radially balance the machine by an amount equal to the mass of the weight 6Q
Correct balancing is achieved by i~ the masses (M,~) of the piston 10, connecting rod 17 and the crank pin journal 20 with the weight 24 of mass Mb, whereby the active radius of the parts to be balanced is the crank pin radius "R" (c~,c.,.~..;.,;i~ of 22 and 26). The active radius of the weight 24 does not need to be "Rn, but Qn be any length "Ln, as long as:
Mo~ ' R = Mb ' L
The axial position of the inner balance weight means 24 is preferably the same as Mo~ For that reason the weight 24 is split and is disposed on either side of the connecting rod. The inner crankshaft balance weight means 24 and the oscillating masses Qn then be added up and ' on axis Y-Y which is rotating and Qn ~herefore be balanced by the outer balance weight means as described.
In this ~ ,. when referring to masses of the balance weight, the effective mass at the radius of rotation of the respective centre of gravity is referred to.
Although the present example has only a single piston, if desired, the en0ine may be provided with more than one piston. Any crank pin positioned on the pitch diameter of the gear 54 will describe a straight line oscillating movement in a respective direction. Any piston mounted on such a crank or pins can be wo ss/2s323 r ~ r 2188~26 baianced by an ~ vlJlh~le inner counter weight means 24 of a mass and position to counteract the resultant oscillating masses. Al ~ v~,l.r, the connecting rod 17 may be extended in the ~ opposite direction to the rod 17 iilustrated and connected with another piston assembly. Of course, ~ ,.u~,.~ ., cylinders would also be provided in all cases.
Figures 5 and 6 illustrate another "1.~ of the invention of narrow V-2 cylinder ~"..r;~" "";,...
This engine differs from that shown in Figure 1 by virtue of being provided witb a compound eccentric assembly having eccentrics 20 which are anguiarly dispiaced, as shown in Figure 6, and there being a second big end bearing housing 18 associated with the second piston and cylinder assembly.
Figure 7 illustrates a further example having two opposed cy~inders and in which a single big end housing 18 has the piston rods 17 of two pistons 10 rigidly commected thereto. Again, of course, the piston may be pivotaily connected to the rod 17 by a "little end" bearing.
It is to be noted that in this . L ' the first outer counter weight means 58 is carried at the inner end of the outer cranicshaft 26 whilst the second outer counter weight means 60 is carried by the fiywheel 57.
Figure 8 illustrates the engine shown in Figure 7 in more detail.
In this example ail the rotary bearings of the engine can be rolling element type bearings. In particular, in this example, the bearings between the inner and outer ~,.~lhl.~ are roller bearings 41', 42' which correspond to plain bearings 41, 42 shown in Figure l_and 2 so that the eccentric 20 is mounted in cantileverby the remainder of the inner cranksha& 22.
An additionai support for the imner crankshaft Z may be provided on the opposite side of the or each piston if desired, for example, if a power take-off is required at that end of the engine, or if a second in-line piston assembly is required, or if an engine having a counter-rotating crank drive is provided in axial aiignment to provide twice the power output, or, for example, to couple two machines with different functions, for example an engine and a, . ~ v-.
.
W0 9~/29323 . ~
Figures 9, 10 and 10a illustrate two examples of machines having such an additional support for the iMer crankshaft.
In any of these cases it is not necessary to provide a second pair of iMer and outer gears, thereby avoiding the difficulty of achieving angular alignment referred to i-..,.c...i,~..u.~.
It is necessaiy only to provide the shaft of the said opposite end with an orbiting support by means of a sub-shaft rotatable about the axis of the outer crankshaft and c~ ,y carrying a further journal at said opposite end of the engine.
Figure 9 shows a four stroke in-line two cylinder engine in which tio eccentric 20 is elongated axially and rotatably received within a second big endbearing housing of the second piston lQ At this end the eccentric 20 is providedwith a further journai 51 which is rotatably ~rc~ntrir~lly mounted in a sub-shaft 53 rotatable about the axis X-X whilst the journal 51 is rotatable about the axis yy, Figures 10 and 10~ illustrate another example of the invention showing a ' of the invention having two side by side piston and cylinder . .-One of the pistons 10 is drivingly connected to an eccentric 20 associated with an iMer crankshaft 22 shown on the right-hand side of Figures 10 and lO~L
and is as described in CoMection with previous . ~ " except for the provision of a further journal 109 ~cc~ntrirS~ily rotatable relative to a sub-shaft lQ5. It may, however, be noted that the outer crankshaft 26 is provided with a gear 120 which meshes with a further gear 120~Lto provide a power take-off drive, for example to a cam shaft charger or generator.
The other piston 10 at the left-hand side of Figures 10 and 10_ has its big end bearing housing 18 rotatably received on a second eccentric 20 which is carried by a second journal 112 rotatably eccentricaliy mounted by bearings 113,114 in a second sub-shaft l lS which is rotatabiy mounted in the crankcase 28 bybearings 116, 117. The second journal 112 is u~yluvidc~i with a gear u~ ,uu,..l;..~, to the gear 54.
wo gs/29323 2 ~ 8 8 1 2 6 A dividing wall 100 between the adjacent cylinders 12 has seats 101, lQ2 for taper roller bearings 103, 104 which rotatably mount the sub-shaft 105 in Ihe wall 100. The sub-shaft 105 has a pair of generally cylindrical passages 106, 107 the centres of which are disposed on a diametral plane of the shaft 105 and on opposite sides of the centre 108 thereof. The passage 106 receives the further joumal 109 projecting from the inner crankshaft æ associated with one of the cylinders 12 whilst the other passage 107 receives a second further journal 110 projecting from the inner secorld eccentric 20 of the other piston lQ The further joumals 109,110 are thus each in eccentric rotatable .~I..liu.~ with said sub-shaft 105 with respective journals being disposed in a !"~.1. ~. ,..: d angular iUl.allil. such as ~ opposite.
Accordingly, firing and inertia loads from the respective inner cranks are supported by the relatively large bearings 103, 104 which support the common further sub-shaft 105 with which the further joumals 109, 110 are engaged.
Because of torque loads the inner crankshaft is provided with a small support bearing at the drive end as shown at 41.
Figure 11 illustrates another example of the invention where it is desired to provide a generator and charger facility. In this case, if a sub-shaft is provided on the opposite side of the piston or pistons, the flywheel 57 is preferably mounted on the side of the engine provided with the inter-engaging gears 54, 56 to avoid high loads on the " bearings 41, 42 due to torque '' To make the best use of the available space the flywheel 57 should preferably be of generally can shape, as illustrated in Figure 11 and in other Figures. Accordingly the generally cylindrical wall 57_ of the flywheel may contain a pemmanent ring magnet 130 with any desired number of poles. A
stationary ammature 131 may be mounted inside the ring to create an integrated brushless generator which may match the full power output of the engine. As the electrical energy generated is a proportion to the peripheral speed of the magnet ring and to avoid oversizing the flywheel flux ring, an epicyclic gearbox may beprovided between the engine output shaft and the flux ring to increase the speedof rotation of the latter. Such an e .,ll, " is illustrated in Figure 12 and 12~
~ WO 95129323 2 1 8 8 l 2 6 f `'~
An epicyclic Bear box 80 comprising a sun gear 81, planet gears 82 and an annulus 83 is provided to increase the output speed from the engine and the space around a tubular bearing extension 84 is used to house a brushless generator 85 provided on a drum 86 keyed to the shaft of the sun gear 81.
The f~ywheel illustrated in Figures 12 and 12~ may carry a further gear drive to drive a high speed coupled charger as is required for two stroke operation.
Referring now to Figures 13 and 14 there is illustrated a two stroke opposed cylinder ~ ~ with a charging piston.
The opposed pistons 10 are drivingly connected to an eccentric 20 carried by an inner crankshaft 22 as described ~ . The inner crankshaft 22 has a further eccentric 140 at the same radius as the axis of rotation Y-Y as the eccentric 20 but angularly offset therefrom and drivingly comnected by a furtherbearing housing 141 to a piston rod 14~ of a charging piston 144 slidable in a cylinder 145. The cylinder 145 is provided at oae end with an inlet valve 146 and an outlet valve 147 whilst at its other end it has an inlet valve 148 and an outlet valve 149. The outlet valve 147 is connected, via a first plenum chamber 150 to the interior of the cylinder 12 associated with one of the pistons 10 via an inlset valve 151 whilst the outlet Yalve 149 is connected via a second plenum chamber 152 to the interior of the cylinder 12 of the other piston 10 via a second inletvalve 153. Accordingly, as the pistons 10 ~.,;~ . so does the charging piston to alternately charge the working cylinders 12. The engine is also provided withan oil sump 154 and with exhaust valves 155 for the cylinders 12 in: ..
malmer.
The plenum chambers 150, læ are provided to take care of the 90 phase angle between the charging and working pistons but at high engine speeds these may not be required.
Although in some of the previously described, . ~".1:.,. !~ plain bearings have been described as being provided between the inner and outer rr~nl~h~frc if desired rolling element bearings may be provided ~
wo 9s/29323 218812~
Although all the illustrated examples are internal . b~ engines the invention and the structural features described arld illustrated herein can be applied to other ~ ,;,UlU~.Uly machines such as an external b~ engine or a . A C aaul or pump.
In all ~ , although only a single pair of inter-engaged immer arld outer gears 54, 56 are illustrated, if desired a plurality of axially spaced pairS of irlter-engaged inner and outer gears may be provided rotatable with the single inner crankshaft 22 on one axial side only of the piston or pistons. Such singlepair or said plurality of pairs of geara provide a single pair of inter-engaged inrler and outer gear means.
If desired, a machine may comprise a plurality of l~.~,;,u~u~l;-~ machines embodying the invention.
The features disclosed in the foregoing description, or the following claims, or the acw~ drawings, expressed in their specific forms or in the terms or means for p ~.,." .~,5 the desired function, or a methûd or process for attaining the disclosed result, may, separately or in any . ' of such features, be utilised for realising the invention in diverse forms thereof.
Such a further joumai or journais may be provided if, for example, a power take-off shaft is required at the end of the machine provided with the further journal; or a second in-line piston and cylinder assembly is required; or two pistons or groups of pistons, each having a ~.~ cd eccentric, are mounted in axiai .cl ' . . for example to provide double the power input; or to couple two machine with different functions, for example an engine and a CCIIIII.-Ie~J~.
In aii such c^qses where a further journal is provided it is not necessary to provide a second pair of gears in qcc,.~qtir,n with the further journal.
r~ when the machine has a single or smail number of pistons it is prone to vibration due to outer baiance forces and cydic i..c, ' a~.~i;..~;l~, to overcome this additionai problem an imner baiance weight means may be provided to at least partly ~4 Ily balance the masses which are rotatable about the ' axis and an outer balance weight means may be provided to at least partly ~ balance the masses which are rotatable about the main axis.
Preferably the imner and outer baiance weight meanS are provided so that their respective resultant centre of gravity is co-axial with the ' axis and the main axis .~ 4.
Accordingly, the inner cranicshaft has an inner balance weight means and the outer crankshaft has an outer balamce weight means having its centre of gravity radiaily opposite the resultant centre of gravity of the inner cranicshaft and the inner balance weight means.
W0 95/29323 r~
~188126 The inner balance weight means may comprise firsl and second inner balance weight means disposed on either side of the piston centre line so as to avoid or reduce any couple around the piston centre line.
The inner balance weight means may comprise a single inner balance weight means or a pluraliy of In~itlltii"-~lly spaced inner balance weight means.
Said pluraliy of inner balance weight means may comprise first and second balance weight means l~ c;~ ly spaced on opposite sides of the piston or pistons.
The single, or at least one of the, inmer balance weight means may comprise a pluraliy of radially spaced balance weights.
The outer balance weight means may comprise a single outer balance weight means or a pluraliy of 1~ " lly spaced outer balance weight means.
Said pluraliy of outer balance weight means may comprise first and second outer balance weight means disposed at positions spaced apart '-~ei~ 'Iy of the outer crankshaft.
The single, or at least one of the, outer balance weight means may comprise a pluraliy of radially spaced balance weights.
The outer balance weight means may comprise a first and a second outer balance weight means each having a centre of graviy disposed at positions spacedapart 1~ " lly of the outer crankshaft and disposed on radially opposite sides thereo The balance weight or weights which comprise the single or said pluraliy of outer balance weight means may be disposed at any desired position or positions l~ Iy of the axis of rotation of the outer crankshaft and/or may be provided on an auxiliary element separate from the outer crankshaft and arranged to rotate therewith, such as an auxiliary drive shaft.
The auxiliary element may be mounted by bearing means and provided with a drive means so as to be driven by the outer crankshaft at the same speed as tbe speed of rotation of the outer crankshaft.
Where the machine has a sub-shaft at least part of the outer balance weight means may be provided thereon.
~ WO 9~/29323 2 1 8 8 t 2 6 . ~1 .
s The outer baiance weight means may comprise first and second y spaced outer balance weight means, the first l -~ ~C;h l ~ ly spaced outer baiance weight means may be provided on said outer crani~shaft and the second I ,, " '1~ spaced outer baiance weight means may be provided on said sub-shaft.
A ~ J.u.a~ machine ~ the invention will now be described by way of example with reference to the ~ drawings, wherein:
FIGURE 1 is a " ~ - cross-section through an internai, engine embodying the present invention;
Fi~GURE 1_ is a r ~ cross-section showing the engine of Figure 1 in more detaii;
FIGURE 2 is a r ~ ' y ~ ''~ end view of the engine of Figure 1;
FIGURE 3 is a ' " y cross-section through a second ~ i ' of the invention;
FIGURE 4 is a r~a~ y cross-section through a third . ' . " of the invention;
FIGURE S is a, ' _ cross-section through a founh L - "
showing an internal . ' engine of narrow V-2 5v - .
FIGURE 6 is a ' ~ - end view of the engine of Figure S;
FIGURE 7 is a ~' v cross sc~liundi view through a fifth .I....I:. -: of the invention showing an engine of h~vin opposed cylinder FIGURE 8 is a ~ cross-section showing an engine as described with reference to Figure 7 in more detail;
FIGURE 9 is a,' ., cross-section through another ~ L
of the invention;
FIGURE 10 is a ' ~ - cross-section showing a further internai combuston engine embodying the invention;
FIGURE lO~L shows the engine of Figure 10 in more detail;
wo9s/~s323 2 1 88 1 26 FlGURE l l is a ~ , A ",~ cross-section through a further ~ -~ ,o.l;,. ,:
of the invention;
FIGURE 12 is a ~ cross-section through a still furtber ' ~ ' of the invention;
FIGURE 12~Lshows the engine of Figure 12 in more detail;
FIGURE 13 is a ' ~ cross-section of a yet further .l.
of the invention; and FIGURE 14 is a d;..,j. transverse cross-section of the engine of Figure 13.
The same reference numerals have been used Lll-l "' the drawings to refer to .,ull~-r " parts.
Referring to Figure 1, 1~Land 2, there is shown an engine which comprises a wûrking piston and cylinder assembly ~ a piston 10 c. ;~,.u~l,l~, within a cylinder 12 provided with a cylinder liner 14. A ~ chamber 16 is provided in . .,..~iu..~l manner.
The piston 10 is rigidly comnected to a rod 17 and is rigidly connected by the rod to a big end bearing housing 18 and is drivingly comnected to an eccentric 20 carried on an inner crankshaft æ rotatable abûut an ' axis Y-Y.
If desired the piston 10 can be connected by a ~little end" to the rod 17 but this is not necessary.
The inner crankshaft 22 carries f~rst and second l. ~ ly spaced imner balance weight means which each comprise an inner balance weight 24 which are disposed directly l ~ ' "y adjacent and on opposite sides of the eccentric 20 amd are arranged to balance the weight of the eccentric, piston bearing and housing assembly 20, 10, 17 and 18 so that the masses rotating about the axis Y-Y
have a resultant centre of gravity which is coincident with the axis Y-Y.
The inner crankshaft æ is ~crl~ntrirslly joumalled in an outer crankshaft 26 for rotation about the axis Y-Y. The outer crankshaft 26 is itself rotatably mounted in a crankcase 28 by main bearings 30, 32 for rotation about a main axisX-~
W0 95129323 r~
The outcr crankshaft 26 is relatively elongated and has first and secondjournals 34, 36 which are disposed at positions which are spaced l~ of the outer crankshaft and are engaged by the inner races of roller element bearings which provide the main bearings 30, 32. The outcr races being received in seats 38, 40 r~ in the crank case 28.
The outer crankshaft 26 is provided with plain bearings 41, 42 disposed in seats 44, 46 disposed at positions which are spaced l" ~ of the outer crankshaft 26 and are rotatably engaged with journals 48, 50 of the inner crankshaft 22 which are spaced I ~ , apart thereof so that the eccentric 20 is mounted in cantilever by the remainder of the imner crankshaft 22.
The outer crankshaft 26 is provided with a cut-out 52 to 7! ' ''''' ''''1~l~ an externally toothed spur or helical gear 54 fixed relative to the inner crankshaft Z
which meshes with a ~ ul l~ r " ~ internal ring gear 56 provided fixed relative to the crank case 28. If desired bevel gear teeth may be provided.
In operation, the inner crankshaft 22 rotates about its axis Y-Y in the opposite direction to the direction of rotation of the outer crankshaft 26 about its a~ds X-X. The gear ratio of the externally toothed gear 54 to the ring gear 56 is 2: 1 so that the inner crankshaft 22 rotates, relative to the outer crankshaft 26, in the opposite direction and at twice the speed to that at which the outer crankshaft 26 rotates relative to the crankcase. The geûmetric centre of the ecceMric 20, shown at Y-Y, IC,.;UIU~ ~ alorg a straight line indicated at A and the piston 10 thus accurately r~,~,;,u~u~ along its respective axis.
As the - . ..,~,. and operation of a counter rotating crank drive is well known, it will not be further described herein. Such a drive can be completely dynanucally balanced by inner counter weight means 24 and outer balance weight means now to be described.
Referring now to Figure 1, the outer crankshaft 26 is provided with a flywheel 57 which carries an outer balance weight means which comprises a frst outer balance weight means 58.
However, because of the cantilever design the balance weight means 58 is off-set axially relative to the masses to be balanced and to avoid an out-of-balance .
wo 9sl29323 r~ S c couple being created the weight 58 is made larger than needed for dynalnic balancing in a radial direction and a second outer balance weight means 60 is provided situated loneih~ n~lly outside the bearing 30 and radially opposite thefirst outer balance weight mearls 58. Thc t,, " '- of the first and second balance weight means 58, 60 are arranged so that the couple created by the off-centre position of the weight 58 is L~ d for by the weight 60 and the weights 58, 60 together ensure that the centre of gravity of the masses rotatingabout the axis X-X is coincident with the axis.
If desired, the weight 60 and/or the weight 58 may be provided in any suitable posiion along the outer crankshaft 26. r.~ uls either or both of the outer balance weight means 58 and 60 may be provided by a single weight or by a plurality of weights at different angular and/or 1~ 1 positions relative to the axis X-X so that the composite effect of the respective weight parts sumsto the desired mass and posiion.
For example, an altemative or additive position for weight 58 is indicated at 58' in Figure 1~, ln another example, shown in Figure 3, which is a section Ihrough an air cooled single cylinder diesel engine having a relatively long flywheel 57, i.e. a flywheel which is relatively long in the direction of the axis X-X, the first balarlce weight means 58 can be mounted on the inner face of the flywheel as shown at 58" instead of, or in addition to, a weight provided at a loQtion which LUII~:_r ' to the position of the first balance weight mearls 58' shown in Figure 1~, Of course, if a weight` is provided both at the location indicated at 58' inFigure l~and the location indicated at 58" the masses of the two weights is suchas to sum to the desired mass.
In another ex~unple, shown in Figure 4, where the flywheel 57 is formed by the rotor of a brushless generator, the first counter weight means can be fixed directly to a rotating canister C holding the pemmanent magnets of the brushlessgenerator (different magnet ~ul~ri5.1l~ a being shown in the top and bottom halves of Figure 4), as shown at 58"' in Figure 4. Again the weight shown at 58"' can be additive to or instead of the weight shown at 58 in Figure 4.
W0 95129323 r ~ 5 ~J~126 In another exarnple, where the engine has a drive to a camshaft and/or an oil pump or another auxiliary taken from the opposite end of the engine to the normal power take-off as is also illustrated in Figures 3 and 4 at 70, an auxiliary element or shaft ?0 is arranged to Qr y a weight 58_ which, as in the previouslydescribed examples, Qn provide tbe whole, or part of the weight required in ...... l. -~;.. with weights at least at one of the other loQtions described ,;..I,.,f~ to achieve dynamic balance of the masses rotating about Ihe axis X-X, Tl~e mass of the balance weight 60 is d~,t~,...,...'d so as to balance the 10't~ ' couple and is disposed radially opposite the balance weight 58, the mass of which is increased over that necessary to radially balance the machine by an amount equal to the mass of the weight 6Q
Correct balancing is achieved by i~ the masses (M,~) of the piston 10, connecting rod 17 and the crank pin journal 20 with the weight 24 of mass Mb, whereby the active radius of the parts to be balanced is the crank pin radius "R" (c~,c.,.~..;.,;i~ of 22 and 26). The active radius of the weight 24 does not need to be "Rn, but Qn be any length "Ln, as long as:
Mo~ ' R = Mb ' L
The axial position of the inner balance weight means 24 is preferably the same as Mo~ For that reason the weight 24 is split and is disposed on either side of the connecting rod. The inner crankshaft balance weight means 24 and the oscillating masses Qn then be added up and ' on axis Y-Y which is rotating and Qn ~herefore be balanced by the outer balance weight means as described.
In this ~ ,. when referring to masses of the balance weight, the effective mass at the radius of rotation of the respective centre of gravity is referred to.
Although the present example has only a single piston, if desired, the en0ine may be provided with more than one piston. Any crank pin positioned on the pitch diameter of the gear 54 will describe a straight line oscillating movement in a respective direction. Any piston mounted on such a crank or pins can be wo ss/2s323 r ~ r 2188~26 baianced by an ~ vlJlh~le inner counter weight means 24 of a mass and position to counteract the resultant oscillating masses. Al ~ v~,l.r, the connecting rod 17 may be extended in the ~ opposite direction to the rod 17 iilustrated and connected with another piston assembly. Of course, ~ ,.u~,.~ ., cylinders would also be provided in all cases.
Figures 5 and 6 illustrate another "1.~ of the invention of narrow V-2 cylinder ~"..r;~" "";,...
This engine differs from that shown in Figure 1 by virtue of being provided witb a compound eccentric assembly having eccentrics 20 which are anguiarly dispiaced, as shown in Figure 6, and there being a second big end bearing housing 18 associated with the second piston and cylinder assembly.
Figure 7 illustrates a further example having two opposed cy~inders and in which a single big end housing 18 has the piston rods 17 of two pistons 10 rigidly commected thereto. Again, of course, the piston may be pivotaily connected to the rod 17 by a "little end" bearing.
It is to be noted that in this . L ' the first outer counter weight means 58 is carried at the inner end of the outer cranicshaft 26 whilst the second outer counter weight means 60 is carried by the fiywheel 57.
Figure 8 illustrates the engine shown in Figure 7 in more detail.
In this example ail the rotary bearings of the engine can be rolling element type bearings. In particular, in this example, the bearings between the inner and outer ~,.~lhl.~ are roller bearings 41', 42' which correspond to plain bearings 41, 42 shown in Figure l_and 2 so that the eccentric 20 is mounted in cantileverby the remainder of the inner cranksha& 22.
An additionai support for the imner crankshaft Z may be provided on the opposite side of the or each piston if desired, for example, if a power take-off is required at that end of the engine, or if a second in-line piston assembly is required, or if an engine having a counter-rotating crank drive is provided in axial aiignment to provide twice the power output, or, for example, to couple two machines with different functions, for example an engine and a, . ~ v-.
.
W0 9~/29323 . ~
Figures 9, 10 and 10a illustrate two examples of machines having such an additional support for the iMer crankshaft.
In any of these cases it is not necessary to provide a second pair of iMer and outer gears, thereby avoiding the difficulty of achieving angular alignment referred to i-..,.c...i,~..u.~.
It is necessaiy only to provide the shaft of the said opposite end with an orbiting support by means of a sub-shaft rotatable about the axis of the outer crankshaft and c~ ,y carrying a further journal at said opposite end of the engine.
Figure 9 shows a four stroke in-line two cylinder engine in which tio eccentric 20 is elongated axially and rotatably received within a second big endbearing housing of the second piston lQ At this end the eccentric 20 is providedwith a further journai 51 which is rotatably ~rc~ntrir~lly mounted in a sub-shaft 53 rotatable about the axis X-X whilst the journal 51 is rotatable about the axis yy, Figures 10 and 10~ illustrate another example of the invention showing a ' of the invention having two side by side piston and cylinder . .-One of the pistons 10 is drivingly connected to an eccentric 20 associated with an iMer crankshaft 22 shown on the right-hand side of Figures 10 and lO~L
and is as described in CoMection with previous . ~ " except for the provision of a further journal 109 ~cc~ntrirS~ily rotatable relative to a sub-shaft lQ5. It may, however, be noted that the outer crankshaft 26 is provided with a gear 120 which meshes with a further gear 120~Lto provide a power take-off drive, for example to a cam shaft charger or generator.
The other piston 10 at the left-hand side of Figures 10 and 10_ has its big end bearing housing 18 rotatably received on a second eccentric 20 which is carried by a second journal 112 rotatably eccentricaliy mounted by bearings 113,114 in a second sub-shaft l lS which is rotatabiy mounted in the crankcase 28 bybearings 116, 117. The second journal 112 is u~yluvidc~i with a gear u~ ,uu,..l;..~, to the gear 54.
wo gs/29323 2 ~ 8 8 1 2 6 A dividing wall 100 between the adjacent cylinders 12 has seats 101, lQ2 for taper roller bearings 103, 104 which rotatably mount the sub-shaft 105 in Ihe wall 100. The sub-shaft 105 has a pair of generally cylindrical passages 106, 107 the centres of which are disposed on a diametral plane of the shaft 105 and on opposite sides of the centre 108 thereof. The passage 106 receives the further joumal 109 projecting from the inner crankshaft æ associated with one of the cylinders 12 whilst the other passage 107 receives a second further journal 110 projecting from the inner secorld eccentric 20 of the other piston lQ The further joumals 109,110 are thus each in eccentric rotatable .~I..liu.~ with said sub-shaft 105 with respective journals being disposed in a !"~.1. ~. ,..: d angular iUl.allil. such as ~ opposite.
Accordingly, firing and inertia loads from the respective inner cranks are supported by the relatively large bearings 103, 104 which support the common further sub-shaft 105 with which the further joumals 109, 110 are engaged.
Because of torque loads the inner crankshaft is provided with a small support bearing at the drive end as shown at 41.
Figure 11 illustrates another example of the invention where it is desired to provide a generator and charger facility. In this case, if a sub-shaft is provided on the opposite side of the piston or pistons, the flywheel 57 is preferably mounted on the side of the engine provided with the inter-engaging gears 54, 56 to avoid high loads on the " bearings 41, 42 due to torque '' To make the best use of the available space the flywheel 57 should preferably be of generally can shape, as illustrated in Figure 11 and in other Figures. Accordingly the generally cylindrical wall 57_ of the flywheel may contain a pemmanent ring magnet 130 with any desired number of poles. A
stationary ammature 131 may be mounted inside the ring to create an integrated brushless generator which may match the full power output of the engine. As the electrical energy generated is a proportion to the peripheral speed of the magnet ring and to avoid oversizing the flywheel flux ring, an epicyclic gearbox may beprovided between the engine output shaft and the flux ring to increase the speedof rotation of the latter. Such an e .,ll, " is illustrated in Figure 12 and 12~
~ WO 95129323 2 1 8 8 l 2 6 f `'~
An epicyclic Bear box 80 comprising a sun gear 81, planet gears 82 and an annulus 83 is provided to increase the output speed from the engine and the space around a tubular bearing extension 84 is used to house a brushless generator 85 provided on a drum 86 keyed to the shaft of the sun gear 81.
The f~ywheel illustrated in Figures 12 and 12~ may carry a further gear drive to drive a high speed coupled charger as is required for two stroke operation.
Referring now to Figures 13 and 14 there is illustrated a two stroke opposed cylinder ~ ~ with a charging piston.
The opposed pistons 10 are drivingly connected to an eccentric 20 carried by an inner crankshaft 22 as described ~ . The inner crankshaft 22 has a further eccentric 140 at the same radius as the axis of rotation Y-Y as the eccentric 20 but angularly offset therefrom and drivingly comnected by a furtherbearing housing 141 to a piston rod 14~ of a charging piston 144 slidable in a cylinder 145. The cylinder 145 is provided at oae end with an inlet valve 146 and an outlet valve 147 whilst at its other end it has an inlet valve 148 and an outlet valve 149. The outlet valve 147 is connected, via a first plenum chamber 150 to the interior of the cylinder 12 associated with one of the pistons 10 via an inlset valve 151 whilst the outlet Yalve 149 is connected via a second plenum chamber 152 to the interior of the cylinder 12 of the other piston 10 via a second inletvalve 153. Accordingly, as the pistons 10 ~.,;~ . so does the charging piston to alternately charge the working cylinders 12. The engine is also provided withan oil sump 154 and with exhaust valves 155 for the cylinders 12 in: ..
malmer.
The plenum chambers 150, læ are provided to take care of the 90 phase angle between the charging and working pistons but at high engine speeds these may not be required.
Although in some of the previously described, . ~".1:.,. !~ plain bearings have been described as being provided between the inner and outer rr~nl~h~frc if desired rolling element bearings may be provided ~
wo 9s/29323 218812~
Although all the illustrated examples are internal . b~ engines the invention and the structural features described arld illustrated herein can be applied to other ~ ,;,UlU~.Uly machines such as an external b~ engine or a . A C aaul or pump.
In all ~ , although only a single pair of inter-engaged immer arld outer gears 54, 56 are illustrated, if desired a plurality of axially spaced pairS of irlter-engaged inner and outer gears may be provided rotatable with the single inner crankshaft 22 on one axial side only of the piston or pistons. Such singlepair or said plurality of pairs of geara provide a single pair of inter-engaged inrler and outer gear means.
If desired, a machine may comprise a plurality of l~.~,;,u~u~l;-~ machines embodying the invention.
The features disclosed in the foregoing description, or the following claims, or the acw~ drawings, expressed in their specific forms or in the terms or means for p ~.,." .~,5 the desired function, or a methûd or process for attaining the disclosed result, may, separately or in any . ' of such features, be utilised for realising the invention in diverse forms thereof.
Claims (30)
1. A reciprocating machine comprising a working piston and cylinder assembly, a counter rotating crank drive having an inner crankshaft carrying an eccentric in driving connection with the piston, the eccentric being rotatable within a big end bearing housing and the piston being connected to said bearing housing, wherein the inner crank shaft is eccentrically journalled about an intermediate axis in a single outer crankshaft which is rotatably mounted relative to a crank case of the machine for rotation about a main axis, the inner crank shaft having an inner gear in engagement with an outer ring gear stationary withrespect to the crank case.
2. A machine according to claim 1 wherein the inner and outer gears are provided respectively with external and internal spur or helical or bevel teeth.
3. A machine according to claim 1 or claim 2 wherein the outer crankshaft is journalled in the crank case by two bearings disposed at positions spaced longitudinally of the crankshaft.
4. A machine according to claim 3 wherein said bearings are disposed on opposite sides of said externally toothed gear.
5. A machine according to any one of the preceding claims wherein the outer crankshaft is provided with bearing means at positions spaced apart longitudinally thereof in which spaced apart journals of the inner crankshaft are rotatably mounted.
6. A machine according to claim 5 wherein said spaced apart journals of the inner crankshaft are disposed on opposite sides of said externally toothed gear.
7. A machine according to any one of the preceding claims wherein the outer crankshaft is provided with a cut-out to accommodate the inner gear.
8. A machine according to any one of the preceding claims wherein the eccentric is mounted in cantilever by the inner crankshaft.
9. A machine according to any one of the preceding claims wherein the inner crankshaft is provided with a further journal, on the opposite side of the eccentric to bearings whereby the inner crankshaft is rotatably mounted on the outer crankshaft, said further journal being eccentrically rotatable relative to a sub-shaft and the sub-shaft being mounted for rotation relative to the crank case about the axis of rotation of the outer crankshaft.
10. A machine according to any one of the preceding claims wherein the machine has a further working piston and cylinder assembly, the further piston being connected to a further big end bearing housing within which said eccentricis rotatable.
11. A machine according to claim 9 wherein the machine has a second working piston and cylinder assembly, the second piston being connected to a second big end housing within which a second eccentric is rotatable, the second eccentric being carried by a second journal which is eccentrically journalled in a second sub-shaft, which is rotatably mounted relative to the crankcase and by a second further journal and wherein the further journals are each in eccentric rotatablerelationship with said sub-shaft with the respective further journals being disposed in a predetermined angular relationship.
12. A machine according to any one of the preceding claims wherein an inner balance weight means is provided to at least partly dynamically balance the masses which are rotatable about the intermediate axis and an outer balance weight means is provided to at least partly dynamically balance the masses whichare rotatable about the main axis.
13. A machine according to claim 12 wherein the inner and outer balance weight means are provided so that their respective resultant centre of gravity is co-axial with the intermediate axis and the main axis respectively.
14. A machine according to claim 13 wherein the inner crankshaft has an inner balance weight means and the outer crankshaft has an outer balance weight means having its centre of gravity radially opposite the resultant centre of gravity of the inner crankshaft and the balance weight means.
15. A machine according to any one of claims 12 to 14 wherein the inner balance weight means comprises first and second inner balance weight means disposed on either side of the piston centre line.
16. A machine according to any one of claims 12 to 15 wherein the inner balance weight means comprises a single inner balance weight means.
17. A machine according to any one of claims 12 to 15 wherein the inner balance weight means comprises a plurality of longitudinally spaced inner balance weight means.
18. A machine according to claim 17 wherein said plurality of inner balance weight means comprises first and second balance weight means longitudinally spaced on opposite sides of the piston or pistons.
19. A machine according to any one of claims 16 to 18 wherein the single, or at least one of the, inner balance weight means comprises a plurality of radially spaced balance weights.
20. A machine according to any one of claims 12 to 19 wherein the outer balance weight means comprises a single outer balance weight means.
21. A machine according to any one of claims 12 to 19 wherein the outer balance weight means comprises a plurality of longitudinally spaced outer balance weight means.
22. A machine according to claim 21 wherein said plurality of outer balance weight means comprises first and second outer balance weight means disposed at positions spaced apart longitudinally of the outer crankshaft.
23. A machine according to any one of claims 20 to 22 wherein the single, or at least one of the, outer balance weight means comprises a plurality of radially spaced balance weights.
24. A machine according to claim 21 wherein the outer balance weight means comprises a first and a second outer balance weight means each having a centre of gravity disposed at positions spaced apart longitudinally of the outer crankshaft and disposed on radially opposite sides thereof.
25. A machine according to any one of claims 12 to 24 wherein the balance weight or weights which comprise the single or said plurality of outer balance weight means are disposed at any desired position or positions longitudinally ofthe axis of rotation of the outer crankshaft and/or are provided on an auxiliaryelement separate from the outer crankshaft and arranged to rotate therewith.
26. A machine according to claim 25 wherein the auxiliary element is mounted by bearing means and provided with a drive means so as to be driven by the outercrankshaft at the same speed as the speed of rotation of the outer crankshaft.
27. A machine according to any one of claims 12 to 25 when dependent on any one of claims 9 to 11 wherein at least part of the outer balance weight means isprovided on said sub-shaft.
28. A machine according to claim 27 wherein the outer balance weight means comprises first and second longitudinally spaced outer balance weight means, thefirst longitudinally spaced outer balance weight means being provided on said outer crankshaft and the second longitudinally spaced outer balance weight meansbeing provided on said sub-shaft.
29. A reciprocating machine substantially as hereinbefore described with reference to Figs. 1 to 2; Fig.3; Fig.4; Figs. 5 & 6; Figs. 7 & 8; Fig.9; Figs. 10 &
10a; Fig.11; Figs. 12 & 12a, or Figs. 13 & 14 of the accompanying drawings.
10a; Fig.11; Figs. 12 & 12a, or Figs. 13 & 14 of the accompanying drawings.
30. Any novel feature of novel combination of features described herein and/or in the accompanying drawings.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB9407966.2 | 1994-04-21 | ||
| GB9407966A GB9407966D0 (en) | 1994-04-21 | 1994-04-21 | Cantilevered crankshafts |
| GB9420891A GB9420891D0 (en) | 1994-10-17 | 1994-10-17 | Cantilevered crankshafts |
| GB9420891.5 | 1994-10-17 | ||
| GB9501948.5 | 1995-02-01 | ||
| GBGB9501948.5A GB9501948D0 (en) | 1995-02-01 | 1995-02-01 | Cantilevered crankshafts |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2188126A1 true CA2188126A1 (en) | 1995-11-02 |
Family
ID=27267156
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2188126 Abandoned CA2188126A1 (en) | 1994-04-21 | 1995-04-19 | Reciprocating machine |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0749519A1 (en) |
| AU (1) | AU2261895A (en) |
| CA (1) | CA2188126A1 (en) |
| WO (1) | WO1995029323A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007034259A1 (en) * | 2005-09-21 | 2007-03-29 | Hery Nirina Rakotomalala | Semi-rotary internal combustion heat engine with double pedal discs |
| CN102135097A (en) * | 2010-01-22 | 2011-07-27 | 上海宝勒特压缩机有限公司 | Mobile screw machine driven by single cylinder diesel engine |
| CN109057866A (en) * | 2018-09-10 | 2018-12-21 | 刘锦峰 | A kind of air-powered motor and its method |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2271766A (en) * | 1940-05-06 | 1942-02-03 | Harry A Huebotter | Engine |
| US4026252A (en) * | 1975-08-08 | 1977-05-31 | Wrin John W | Engine construction |
| DE2947882A1 (en) * | 1979-11-28 | 1981-07-23 | Volkswagenwerk Ag, 3180 Wolfsburg | Piston engine crank drive without connecting rod - includes stationary surface formed by wheel concentric to lengthwise axis |
| GB2080483B (en) * | 1980-07-18 | 1984-06-13 | Rees John Douglas | Piston rods |
-
1995
- 1995-04-19 WO PCT/GB1995/000882 patent/WO1995029323A1/en not_active Application Discontinuation
- 1995-04-19 AU AU22618/95A patent/AU2261895A/en not_active Abandoned
- 1995-04-19 EP EP95915925A patent/EP0749519A1/en not_active Withdrawn
- 1995-04-19 CA CA 2188126 patent/CA2188126A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| EP0749519A1 (en) | 1996-12-27 |
| WO1995029323A1 (en) | 1995-11-02 |
| AU2261895A (en) | 1995-11-16 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Dead |