CN1865664A

CN1865664A - rotary piston engine

Info

Publication number: CN1865664A
Application number: CNA2005100874459A
Authority: CN
Inventors: 赫伯特·许特林
Original assignee: Individual
Current assignee: Individual
Priority date: 2005-05-17
Filing date: 2005-07-22
Publication date: 2006-11-22
Anticipated expiration: 2025-07-22
Also published as: EP1882082A1; WO2006122658A1; CN100480489C; DE102005023721B3

Abstract

A rotary piston engine having a housing (12) in which a first and at least one second piston (24, 26) are arranged, which are rotatable in the housing (12) about a housing-fixed axis of rotation (32) and which, when rotated about the axis of rotation (32), perform a back-and-forth rotary motion between a first end position and a second end position in opposition to one another about a piston-fixed axis of rotation (36) running perpendicularly to the axis of rotation and centrally through the housing, wherein the first and at least second piston (24, 26) define a working chamber (48), wherein the first piston (24) and/or the at least second piston (26) have at least one operating means (50, 52) which, when the first and/or second piston (24, 26) is rotated, are guided along at least one control cam (58) in order to produce the first and/or at least second piston (24, 26), 26) The rotary motion of (2). The control cam (58) can be positionally adjusted by means of an adjusting mechanism (74) in order to adjust at least one of the first and second end positions of at least one of the first and second pistons (24, 26).

Description

Oscillating piston engine

Technical field

The present invention relates to a kind of oscillating piston engine, have a shell, the inside is provided with one first and at least one second piston, they in the enclosure can be jointly around the fixing running shaft rotation of a shell, and they are when rotating around running shaft, oppositely between first end position and second end position, carry out back and forth rotation motion each other around the fixing turning axle of piston vertical with running shaft and by the shell central distribution, wherein, first and at least the second piston is determined a working room, wherein, the first piston and/or at least the second piston have at least one travelling mechanism, this mechanism controls cam guidance along at least one when first and/or second piston rotates, to produce the rotation motion of first and/or at least the second piston.

Background technique

This oscillating piston engine has disclosed by document WO 03/067033 A1.

Oscillating piston engine and particularly foundation internal-combustion engine of the present invention can be used as internal-combustion engine, pump or compressor and use.Preferably use and introduced in this manual according to oscillating piston engine of the present invention as this internal-combustion engine as internal-combustion engine.

Under the situation that oscillating piston engine uses as internal-combustion engine, each working stroke of facilitating the combustion mixture of combustion mixture air inlet, compression, igniting and burning to expand and discharge by back and forth the rotation motion between two end positions of single piston.

In the disclosed oscillating piston engine of document WO 03/067033 A1 by same claimant, four pistons are set in the enclosure, they rotate jointly around the fixing running shaft of a shell center shell, and the turning axle of fixing around a piston in the enclosure when rotated carries out rotation motion back and forth, wherein, two adjacent piston reverses direction revolutions separately.

" shell is fixed " meaning here be one be considered as geometrical axis the axle on, the axle constant with respect to the spatial position of shell.Corresponding therewith, the meaning of " piston is fixed " is the fixed spatial relationship of a geometrical axis and a piston.

Between right two the mutual close piston end surfaces separately of piston, form a working room, thereby this disclosed oscillating piston engine have two working rooms.Two working rooms that radially are oppositely arranged about the shell center enlarge in the same way when the rotation motion back and forth of piston and dwindle.

Piston ring is derived by a control mechanism around the rotatablely moving of running shaft from piston ring around the rotation motion of shared turning axle, this control mechanism comprise two in the enclosure on the wall control cam of moulding and piston near corresponding travelling mechanism on the outer casing inner wall face.In this disclosed oscillating piston engine, the stroke of piston rotation motion is predesignated by the curvilinear motion of two control cams immutablely.Therefore this disclosed oscillating piston engine has constant discharge capacity, and wherein, this discharge capacity is maximum volume or working room's maximum volume sum.

Carry out in the reciprocating engine of linear reciprocating motion at this its alleged piston, people attempt developing to have the variable-displacement motor, that is to say that the discharge capacity of this reciprocating engine can be adjusted at the duration of work of reciprocating engine.Therefore people attempt the removable formation of cylinder head, yet the shortcoming of doing like this is that cylinder head no longer can be used for acceptance point lighted torch or spark plug owing to removable, particularly no longer can use for accepting intake valve and exhaust valve.Having the variable-displacement reciprocating engine does not therefore have so far as the motor of producing in batches.

Summary of the invention

Therefore purpose of the present invention is, provide a kind of start described type have a variable-displacement oscillating piston engine.

According to the present invention, this purpose is being achieved aspect the described oscillating piston engine of beginning thus, promptly control cam and can carry out the position adjustment by means of a regulating mechanism, with adjust first and second pistons, first and second end positions one of at least one of at least.

Has variable discharge capacity according to oscillating piston engine of the present invention, wherein, fixing there and the incorporate control cam of outer casing inner wall that have had on the sort of disclosed oscillating piston engine constitute by means of a regulating mechanism adjustable positions now, can adjust first end position and/or second end position of at least one piston thus.

Be with the difference of traditional reciprocating engine, in foundation oscillating piston engine of the present invention, not having appearance point lighted torch or spark plug or air inlet and exhaust valve is to help the variability of discharge capacity and must be installed in other locational problems of rotary piston engine, because in the sort of disclosed oscillating piston engine, the control cam also has been arranged on and has been different from these before this on the spatial position of alleged parts, that is to say that the adjustable of control cam is not conflicted with these parts.

Providing the oscillating piston engine that a small amount of spending is only arranged on a kind of and the sort of disclosed oscillating piston engine structure compared now by the present invention, is that its discharge capacity is variable but compare the major advantage that has with the sort of disclosed oscillating piston engine.

Preferred constitute one, by means of regulating mechanism can adjust continuously first end position and second end position one of at least.

Advantage thus is that discharge capacity can change continuously, can make the stepless variation of discharge capacity of oscillating piston engine thus.

In another preferably constitutes, can adjust first and second end positions of first and at least the second piston by means of regulating mechanism.

Advantage thus is, no matter is that so-called upper dead center position (OT-position) or lower dead point position (UT-position) all can change.On the OT-position, swept volume of a single chamber minimum (igniting), and on the UT-position maximum (exhaust end/air inlet begins).If the UT-position is adjusted on the meaning of dwindling working stroke or discharge capacity now, what have advantage so is, following adjustment also can be done in the OT-position, make it still reach compression high as far as possible on the OT-position under situation of dwindling swept volume of a single chamber (discharge capacity), this point reaches by above-mentioned formation, and wherein no matter the OT-position still is the UT-position all can be adjusted.

In another preferably constitutes, but two sections of control cam oppositely each other around the fixing turning axle pivoting support of a shell in the enclosure.

In this formation, discharge capacity or maximum functional chamber volume are adjusted thus, make by the control cam that constitutes with fixing axisymmetric two sections of revolution of shell to be turned back in the second place from primary importance.The control cam can be simple on the structure around the advantage of the rotating this regulating mechanism of turning axle, to produce variable discharge capacity.

In another preferably constitutes, the the 3rd and the 4th piston is set in the shell, they and first and second pistons can rotate around running shaft in the enclosure jointly, and meanwhile between the 3rd end position and the 4th end position, carry out reverse each other rotation motion, third and fourth end position one of at least can be by means of the regulating mechanism adjustment.

In this formation, have four pistons of total and corresponding two working rooms equally according to oscillating piston engine of the present invention and the sort of disclosed oscillating piston engine, wherein, it is variable that therefore the maximum functional chamber volume of two working rooms also also has the total displacement of oscillating piston engine.

About third and fourth piston, preferably by means of regulating mechanism can adjust continuously the 3rd end position and the 4th end position one of at least.

Third and fourth end position of same whole third and fourth piston of preferred tunable.

In another preferably constituted, the 3rd piston and first piston were radially relative about the fixing turning axle of piston, and the 3rd end position can be synchronously with in the same way to the first end position adjustment.

Preferred in the same way the 4th piston and second piston are radially relative about the fixing turning axle of piston, the 4th end position can be synchronously with in the same way to the second end position adjustment.

No matter above-mentioned two kinds of measures are for itself or particularly under combination mutually, all guarantee the adjustment of piston end position and therefore also have being adjusted at of two working rooms maximum functional chamber volume not increase under the situation of control gear spending to carry out in an identical manner.

Control the rotation motion that cam can be controlled all four pistons for one in principle, wherein these pistons are interconnected accordingly, and on the contrary preferably, the 3rd piston and/or the 4th piston have at least one travelling mechanism, this mechanism controls cam guidance along second when the 3rd and/or the 4th piston rotates, to produce the rotation motion of the 3rd and/or the 4th piston, wherein, the second control cam can be adjusted by means of regulating mechanism then, with adjust third and fourth piston, third and fourth end position one of at least one of at least.

Advantage with second control cam of four pistons is the higher or complete symmetry of whole oscillating piston engine, and the roadability to rotary piston engine produces positive impact like this.The second control cam correspondingly also can carry out the position adjustment, and is identical with the situation of the control cam of first and second pistons.

But two sections of the same preferred second control cam oppositely each other around the fixing turning axle pivoting support of a shell in the enclosure.

In a particularly preferred formation, regulating mechanism has first cam member and second cam member, and wherein, first cam member and second cam member are shearing by intersecting reversed turning setting each other and have the first and second control cams.

By this measure, two control cams of four pistons realize that by two cam members they oppositely can turn round setting around turning axle is shearing each other by intersection, and wherein, but this turning quality is used to adjust the end position of piston rotation motion.This structure advantage structurally is simple and can makes the control cam realize a kind of simple adjustment as the back also will be introduced.

In this regard, the preferably common first control cam segment that constitutes first cam member of one of control cam is controlled cam segment with respect to this first period removable connection with second of second cam member.

Because single control cam is not a point symmetry about the fixing turning axle of shell, but distribute in the face of claiming about the fixing residing plane mirror of turning axle of shell, and therefore be provided with to the two sides of this symmetry plane, so the removable connection of two control cam segments can realize control cam continuous on a kind of one side space, wherein, on the other hand the first control cam segment and the second control cam segment around shell fixedly the reversed turning of turning axle be used for the end position of adjustment first and second pistons on the meaning that discharge capacity adjustment or the first working room swept volume of a single chamber are adjusted.

Corresponding therewith, preferably common the 3rd control cam segment that constitutes first cam member of another control cam is controlled cam segment with respect to the 4th period removable the connection with the 4th of second cam member.

Here the relatively moving property of two alleged control cam segments also can be used to the reversed turning of two control cam segments to adjust the end position of third and fourth piston each other, and guarantees to form the second control cam that connects on a kind of space of third and fourth piston simultaneously.

The first control cam segment and the second control cam segment or the 3rd control cam segment and being connected preferably that the 4th control cam segment can move relative to each other by this comb formulas connection of for example engagements of these control cam segments realization.

Particularly can adjust so as mentioned above by the engagement contact, min chamber volume is reduced on the OT-position, maximum functional chamber volume (UT-position) is dwindled the OT-position of first and second pistons or third and fourth piston.

In another preferably constituted, regulating mechanism had at least one hydraulic pressure, pneumatic and/or electronic transmission device.

Preferred especially at least one transmission device is a hydraulic pressure; The chamber of the variable volume that can supply with hydraulic fluid is set near at least one face of the outer casing inner wall of shell at cam member.

Advantage with hydraulic transmission is, hydraulic fluid is incompressible basically and utilize hydraulic transmission can also produce very high power, even so that cam member and the discharge capacity that therefore also has oscillating piston engine also can reliably obtain adjusting during around the high rotating speed of running shaft at piston ring.

In this regard further preferably by improving the range that indoor hydraulic pressure dwindles the range of piston and enlarges piston by the reduction hydraulic pressure.

Advantage thus is, transmission device only needs activity on an effective exercise direction for adjusting cam member, exactly be to dwindle on the effective exercise direction of discharge capacity, and the centrifugal force that will act on piston on the effective exercise direction that enlarges discharge capacity is used to act on the power of cam member, if the corresponding reduction of hydraulic pressure, this power can make cam member turn round mutually.Transmission device structurally can be very simple in this manner.

In another preferably constituted, at least one travelling mechanism and the such magnetic of at least one control cam came into force, and made between at least one travelling mechanism and at least one the control cam and produced magnetic pull.

Though because the quality of common piston that constitutes a functional unit and travelling mechanism has just been considered enough centrifugal force during around the slow-speed of revolution of running shaft at piston ring, and guarantee stable contact between travelling mechanism separately and the control cam, but the advantage of this measure is that this contact between travelling mechanism and the control cam is further enhanced.

" magnetic comes into force " should be understood thus like this, travelling mechanism and control cam are made up of the effective material of permanent magnetism or are had this effective material, perhaps travelling mechanism and control cam or the two be made of magnetisable material one of at least or have a this material.At least the two one of, just travelling mechanism or control cam should be permanent magnetism in this regard, do not need additionally to produce the parts in magnetic field thus in mode, just magnetic field generator with advantage.

The such magnetic of piston of same preferred at least one travelling mechanism and subordinate comes into force, and makes between the piston of at least one travelling mechanism and subordinate and produces magnetic pull.Make stable contact between the piston of travelling mechanism and subordinate by this measure, can cancel travelling mechanism thus and reasonably be connected with the moulding of subordinate piston.

According to above-mentioned formation, between travelling mechanism and the piston or the magnetic pull between travelling mechanism and the subordinate control cam should be such, promptly do not cancel the rotating freely property of the best travelling mechanism that constitutes as spheroid.

Description of drawings

By accompanying drawing other advantages and feature are described below.

Self-evident, the noted earlier and following feature that also will introduce and in other combinations or use in the position separately, and can not depart from framework of the present invention not only in cited separately combination.

Accompanying drawing illustrates one embodiment of the present of invention, now is elaborated by accompanying drawing.Wherein:

Fig. 1 is with along parallel with running shaft and with the section of the turning axle vertical plane of piston view according to oscillating piston engine of the present invention is shown, and wherein, this oscillating piston engine is in first working state of the regulating mechanism that is used to adjust piston control cam;

Fig. 2 illustrates the view identical with Fig. 1, is used to adjust second working state that piston is controlled the regulating mechanism of cam but be in;

Fig. 3 illustrates oscillating piston engine with the view identical with Fig. 1, but does not have piston and piston shelf;

Fig. 4 a) and b) with independent locational perspective view two cam members are shown;

Fig. 5 illustrates cam member among Fig. 4 with the setting of sectional drawing and combination;

The oscillating piston engine that Fig. 6 illustrates Fig. 1 is in around running shaft and rotates in about 45 ° enclosure location, and wherein the UT-position of piston from its Fig. 1 at about half stroke of direction revolution of its OT-position;

Fig. 7 illustrates the oscillating piston engine of Fig. 1 to be in the shell with respect to Fig. 1 half-twist, and wherein, piston is turned back in its OT-position; And

Fig. 8 illustrates another view of Fig. 1 oscillating piston engine, has piston shelf, but does not have piston.

Embodiment

Fig. 1-3 and Fig. 6-8 illustrate the oscillating piston engine with shared reference numeral 10 with different views.Figure 4 and 5 illustrate other details of this oscillating piston engine 10.

Oscillating piston engine 10 constitutes as internal-combustion engine in the present embodiment.

Oscillating piston engine 10 has by two

housing parts

14 and 16 shells of forming 12.

Housing parts

14 and 16 has a flange separately, wherein, the flange 18 of housing parts 14 only is shown in the accompanying drawing.In flange, has the hole 20a-20h that is used to pass bolt in a large number, so that two housing parts 14 are connected by the mutual bolt of flange with 16.

Enclosure is sphere or spherical symmetric structure, and wherein, ball's dead center adopts reference numeral 22 marks in Fig. 1.

Four

pistons

24,26,28 and 30 are set in the inside of shell 12.Piston 24-30 can rotate according to arrow 34 around the fixing running shaft 32 of a shell in shell 12 jointly.When this rotatablely moving, piston 24-30 carries out rotation motions a kind of and around running shaft 32 stacks around the fixing turning axle 36 of piston between two end positions, wherein, Fig. 1 illustrates an end position (so-called UT-position), and Fig. 7 illustrates another end position (so-called OT-position).Fig. 6 illustrates piston 24-30 and is in neutral position between UT-position and the OT-position.

No matter what be considered as geometrical axis is the shell central point 22 that running shaft 32 or turning axle 36 all pass shell 12.Turning axle 36 vertically is on the running shaft 32 all the time, but rotatablely moving of same and piston 24-30 correspondingly rotated around running shaft 32.

Two pistons are radially relative about turning axle 36 separately among the piston 24-30, exactly are on the rotary position of piston 24-30, and wherein, they are

piston

24 and 30 on the one hand, are

piston

26 and 28 on the other hand.

Piston 24-30 is bearing in separately in the shell 12, not that is to say to be rigidly connected mutually in pairs, although this point can be considered on meaning of the present invention equally.

Piston 24 has end face 38, and piston 26 has end face 40, and piston 28 has end face 42, and piston 30 has end face 44.

Piston

24 and 26 end face 38 and working rooms 46 of 40 restrictions close to each other, and

piston

28 and 30 end face 42 and working rooms 48 of 44 restrictions close to each

other.Working room

46 and 48 uses as the firing chamber of Carnot's cycle.Running shaft 32 passes two working

rooms

46 and 48, exactly is in each rotation and rotary position of piston 24 and 30.

Working room

46 and 48 particularly is symmetrical arranged with running shaft 32, that is to say, running shaft 32

passes working room

46 and 48 all the time from the center.

Because adjacent separately piston 24-30 carries out reverse each other rotation motion around running shaft 32 rotation the time, so enlarge in the same way each other all the time and dwindle working

room

46 and 48.

Maximum volume state from working room 46 shown in Figure 1 and 48,

piston

24 and 26 or 28 and 30 turns round toward each other, as shown in Figure 6, and wherein, working

room

46 and 48 volume meanwhile reduce, and enter its minimum volume state until working room shown in Figure 7 46 and 48.

Piston

24 and 26 remains at the left side of Fig. 1 middle conductor A when its rotation and rotation motion, and

piston

28 and 30 is in the right side of line segment A all the time.

Oscillating piston engine 10 also has a control mechanism, so as from piston 24-30 around the rotation motion of deriving piston 24-30 the rotatablely moving of running shaft 32.Each piston 24-30 has a travelling mechanism for this reason, and exactly, piston 24 has travelling mechanism 50, and piston 26 has travelling mechanism 52, and piston 28 has travelling mechanism 54 and piston 30 has travelling mechanism 56.Travelling mechanism 50-56 is a spheroid, and they are bearing in each piston 24-30 separately away from the spheric thrust bearing that constitutes on the end face 38-44 back side separately.

Travelling mechanism 50-56 can rotate freely in the mode of spheroid and be bearing in the spheric thrust bearing, and can remain on by adhesion in the spheric thrust bearing by means of lubricating film, perhaps travelling mechanism 50-56 can reasonably remain in the spheric thrust bearing in moulding, and the spheric thrust bearing diameter that surpasses spheroid 50-56 extends then for this reason.Such as already mentioned, but spheroid 50-56 under any circumstance all can rotate freely on all directions around its ball centre point.

As can the clearlyest seeing from Fig. 3, for distributing, travelling mechanism 50-56 amounts to two control cams 58 and 60, and travelling mechanism 50-56 is subjected to the guiding operation inside.In Fig. 3, for ease of understanding travelling mechanism 50-56 and piston 24-30 are not shown, thereby can see the control cam 58 and 60 that exposes.Self-evident, in Fig. 3 corresponding with sectional drawing only can see control cam 58 and 60 separately half.Control cam 58 and 60 exactly extends in the enclosure by 360 ° whole circumference.

Travelling

mechanism

50 and 52 operations in control cam 58 when

piston

24 and 26 rotates around running shaft 32, and the travelling mechanism 54 of

piston

28 and 30 and 56 moves along control cams 60.

Control cam 58 and 60 profile are selected like this, make it at travelling mechanism 50-56 during along control cam 58 and 60 operations, at piston 24-30 around the rotation motion of derivation piston 24-30 in the rotatablely moving of running shaft 32 around turning axle 36.

With this effect be Fig. 3 middle conductor A and the section 62 and 64 and the section 66 and 68 of control cam 60 that therefore comprises the control cam 58 that turning axle 36 is nearest accordingly with the figure plane vertical distribution, and the UT-position of definite piston 24-30.In contrast be line segment A and therefore with above-mentioned plane farthest apart section 70 and 72 (and corresponding section of the corresponding control cam of in sectional drawing, can't see by 30 ° of findings of whole circumference of control cam 58 and 60 58,60) and the OT-position of definite piston 24-30.

Piston 24 shown in Figure 1 and 26 first end position are determined in the position of section 62 and 64 therefore, and second end position of piston shown in Figure 7 24 and 26 is determined in the position of section 70.

The corresponding definite piston 28 in position of section 66 and 68 and 30 the 3rd end position, it is equivalent to first end position of

piston

24 and 26 and shown in Figure 1, and the 4th end position of

piston

28 and 30 is determined in section 72 position, and it is equivalent to second end position of

piston

24 and 26 and shown in Figure 7.

As following also to introduce in detail, control cam 50 and 60 can carry out the position adjustment by means of a regulating mechanism 74, so that like this to the above-mentioned first, second, third and the 4th end position of piston, just its OT-position and UT-position thereof are adjusted, and therefore adjust the discharge capacity of the maximum volume and the oscillating piston engine 10 of working

room

46 and 48.

According to Figure 4 and 5, regulating mechanism has two

cam members

76 and 78, constitutes control cam 58 and 60

above.Cam member

76 and 78 shearing by arranged in a crossed manner, as also seeing from Fig. 3 about the fixing turning axle 79 of shell.Cam member 76 has one first control cam segment 80 and one second control cam segment 82, and cam member 78 has one first control cam segment 84 and one second control cam segment 86.Control cam segment 80 and 86 constitutes control cams 58 jointly, and control cam segment 84 and 82 common formation control cams 60.

Cam member

76 and 78 around running shaft 32 rotation, not that is to say, the difference of turning axle 79 and turning axle 36 is that shell fixes.On two piston positions separately around running shaft 32, turning

axle

36 and 79 overlaps, and Fig. 1 shows one of them.

But

cam member

76 and 78 is bearing in the shell 12 of oscillating piston engine 10 around turning axle 79 reversed turnings, shown in double-head arrow 88 and double-head arrow 90.

Outwards turn round around turning axle 79 by

cam member

76 and 78, therefore the section 62-68 that controls cam 58 and 60 also removes from turning axle 79 from above-mentioned line segment A, and also therefore also has this plane near line segment A on the contrary by

cam member

76 and 78 inside revolutions.Therefore adjustment is removed from its turning axle 36 in the UT-position of piston 24-30 by

cam member

76 and 78 outside revolutions, thereby the maximum volume of working

room

46 and 48 reduces, as shown in Figure 2; And the maximum volume that inwardly turns round corresponding

expansion working room

46 and 48 by

cam member

76 and 78.

For making the cam member 76 can relative rotation motion with 78, control cam segment 80 and 86 or 84 and 82 can relatively move and be connected, exactly be control cam 58 with 60 sections 70 and 72 in be connected 92 and 94 by means of the comb formula.

The comb formula connects in an illustrated embodiment realization thus, promptly controls cam segment 84 and has a convex shoulder 96, and it embeds in the gap or space 98 of control cam segment 82, and inside can move on the direction of convex shoulder 96.Connect 92 corresponding formations, wherein, at Fig. 4 b) in can see belonging to and connect 92 convex shoulder 100.

Fig. 4 a) and b) in also can find out control cam 60 and same control cam 58 that in Fig. 4, can't see, the whole circumference by 360 ° under the assembled state of control cam 58 and 60 is extended.

Travelling mechanism 50-56 is with operation in the circular control piston 58 and 60 that constitutes of minimized friction appropriate section on the transverse section.

Have separately and 92 and 94 also can otherwise constitute being connected of a convex shoulder and a gap or space, the comb shape or the engagement that for example can have other modes form control cam segment 80 and 86 or 84 and 82 so muchly and control relatively moving property between the cam with the perforation of travelling mechanism 50-56.

At cam member 58 and 60 during, face toward the corresponding mobile of convex shoulder direction in control cam segment 86 and 84 the space of convex shoulder on control cam segment 80 and 82 around turning axle 79 revolution.

This relatively moving property also can be used for adjusting the second or the 4th end position of piston 24-30, just its OT-position.So this being adjusted under the situation that changes the UT-position of OT-position carried out automatically, exactly be on this meaning, if promptly the maximum volume of UT-position or working

room

46 and 48 reduces, working

room

46 and 48 minimum volume reduce on the OT-position of piston 24-30 equally.Reduce under the situation of discharge capacity at oscillating piston engine 10 thus, reach enough compression pressures when the petrol-air mixture of compression is lighted a fire in working

room

46 and 48.

In addition, regulating mechanism 74 has a transmission device 102 that is used for adjusting around turning axle 79

cam member

76 and 78.

Transmission device 102 is a kind of hydraulic transmissions.For this

reason cam member

76 and 78 at

cam member

76 and 78 near the

chambers

106 and 108 that have the variable volume that can supply with hydraulic fluid on the faces of outer casing inner wall 104.

A valving 110 is set in chamber 106 and a valving 112 is set in chamber 108, be used for being transported to hydraulic fluid in the chamber 106,108 or 106,108 discharges from the chamber.

Loading by

chamber

106 and 108, cam member 58 and 60 is outwards swung around turning axle 36, and when hydraulic pressure reduces in

chamber

106 and 108, cam member 58 and 60 utilizes the centrifugal force that acts on piston inwardly to turn round when piston 28-30 rotates, and centrifugal force is delivered on the

cam member

76,78 by control cam 58 and 60.In this manner at the run duration of oscillating piston engine 10, transmission device 102 is subjected to transmission for adjusting discharge capacity (working

room

46 and 48 maximum volume).

Can have a corresponding unshowned control gear in this regard, it adjusts

cam member

76 and 78 under piston 24-30 is around the speed conditions of running shaft 32 depending on.Preferably dwindle or on the contrary along with the discharge capacity of the increase oscillating piston engine 10 of piston 24-30 rotating speed.

Introduce other details of oscillating piston engine 10 below again.

Piston 24-30 at shell 12 internal supports at one around running shaft 32 jointly on the piston shelfs 114 along with piston 24-30 rotation.Fig. 8 illustrates the piston shelf 114 that does not have piston 24-30.

The also preferred in an illustrated embodiment as a whole parts of piston shelf 114 wherein, but replace the structure that whole structure also it is contemplated that a kind of many bodies.

Piston shelf 114 extends on the whole length of shell 12 along running shaft 32, and wherein, the crown of roll of piston shelf 114

shoulder

116 and 118 protrudes from shell 12.

Piston shelf 114 has

main bearing section

120 or 122 that is connected on the crown of

roll shoulder

116 and 118 separately, and piston shelf 114 can be around running shaft 32 rotating supports in shell 12 by them.Bearing section 120 is connected by an intermediate section 124 at the shell center with 122, and this section has a pin shape section 126 of extending along turning axle 36.Piston 24-30 can to shell central point 22 or to turning axle 36 mobile supports on pin shape section 126.

As shown in Figure 8, piston shelf 114 has two

holes

128 and 130, slide inside supporting piston 24-30.Exactly, sliding

bearing piston

24 and 26 in hole 128, sliding

bearing piston

28 and 30 in hole 130.

Hole

128 and 130 is circular on the transverse section to be constituted, and the same respective circular of the end face 38-44 of piston 24-30 constitutes.Piston 24-30 is bearing in hole 128 or 1340 by means of the piston ring that is used for

seal operation chamber

46 and 48, as shown in Figure 1, wherein shows the

Sealing

132 and 134 that for example is used for piston 24.

Hole

128 and 130 utilizes the common restraint of labour of the end face 38-44

chamber

46 and 48 of piston 24-30.

In the

hole

128 and 130 of piston shelf 114, piston 24-30 is connected with piston shelf 114 about running shaft 32 antitorquely, thereby piston 24-30 is jointly along with piston shelf 114 rotates around running shaft 32, and that the rotation motion that piston 24-30 and its carry out around turning axle 36 this moment is correspondingly

slided hole

128 and 130 in is mobile, to carry out each working stroke of air inlet, compression, expansion and exhaust.

Piston 24-30 arc basically constitutes, and working

room

46 and 48 also has general curved or the cylindrical shape of arc, and wherein, curvature is concentric with turning axle 36.

Together with what travelling mechanism 50-56 formed " internal engine " that constitutes oscillating piston engine 10 be set by piston shelf 114, piston 24-30, that is to say that this set comprises all movable parts of oscillating piston engine 10.

According to another scheme, travelling mechanism 50-56 and control cam 58,60 magnetic work, thereby between the control cam 58,60 of travelling mechanism 50-56 and subordinate separately a kind of magnetic pull of generation.

Preferably control cam 58 and 60, the

cam member

76 and 78 that exactly is regulating mechanism 74 is magnetized or the high strength alloy that is magnetized is made by " just ", and spherical travelling mechanism 50-56 is preferably magnetized by " bearing " or the pottery or the carbon fiber composite material that are magnetized are made.

Piston 24-30 is preferably magnetized by " just " or the aluminium or the magnesium alloy that are magnetized are made.In this manner, between the piston 24-30 of travelling mechanism 50-56 and subordinate, also there is a kind of magnetic pull.

In addition, for supporting on the one hand travelling mechanism 50-56 and control cam 58,60 and above-mentioned sucking action between travelling mechanism 50-56 and the piston 24-30 on the other hand, piston shelf 114 also has shell 12 to be magnetized by " just " when needing or the material that is magnetized is made.

Magnetization or magnetic action also can be selected on the contrary with above-mentioned distribution in that the polarity aspect " just " and " bearing " is self-evident.

For example as shown in Figure 8, in the

bearing section

120 and 122 of piston shelf 114, there are a large amount of

passages

136 or 138, they with cooling-/oiling agent connecting tube 140-146 (referring to Fig. 1) is communicated with so that for cooling and lubricated will the cooling-/lubricant delivery arrives in the piston shelf 114.Meanwhile, internal engine is also cooled off near working room 46 and 48.In the intermediate section 124 of piston shelf 114, also distribute a unshowned cooling-/lubricant passageway.

Self-evident, oscillating piston engine 10 also has suction tude and outlet pipe, is used for the air inlet of petrol-air mixture and the discharge of the mixed gas that burnt, and here repeats no more.These suction tude and outlet pipe are distributed to working

room

46 and 48 separately.

In addition, for each working

room

46 and 48 distributes a cheese stick or

spark plug

148 and 150, they are arranged on the running shaft 32 and with piston shelf 114 and rotate around running shaft 32 jointly.

Introduce the working principle of oscillating piston engine 10 below.

Fig. 1 illustrates oscillating piston engine 10 and is in piston 24-30 and is in the locational working position of its UT-.Meanwhile, Fig. 1 illustrates the working position of

cam member

76 and 78 maximum inside rotating oscillating piston engines 10.This means the discharge capacity of oscillating piston engine 10, just working

room

46 and 48 maximum volume maximum.

Fig. 2 illustrates the working state of oscillating piston engine 10 in contrast, wherein, though piston 24-30 is on the UT-position that its

working room

46 and 48 maximums open equally, but on the working position there,

cam member

76 and 78 is with about 20 ° of outwards revolutions, thereby the maximum volume of working

room

46 and 48 little than among Fig. 1 on the UT-position of piston 24-30 that is to say, the discharge capacity of oscillating piston engine 10 in Fig. 2 less than working state among Fig. 1.

Cam member 76 shown in Figure 2 and 78 rotary position also are the rotary position of the maximum possible of

cam member

76 and 78 in this regard, and on this position,

cam member

76 and 78 end faces are close in the respective voids in the outer casing inner wall 104.

Once more from Fig. 1, Fig. 6 illustrates a kind of running state of oscillating piston engine 10, carry out about 45 ° of rotations at this state lower piston 24-30 around running shaft 32, wherein, piston 24-30 inwardly turns round and makes an appointment with half, wherein, this rotation motion is derived at the control cam 56 or 58 of respective profile around the guiding by travelling

mechanism

50 and 56 the rotatablely moving of running shaft 32 from piston 24-30 as mentioned above.

In Fig. 7, piston 24-30 continues rotation with 45 ° around running shaft 32 once more, and piston is turned back in the OT-position now.

When continuing 45 ° of rotations around running shaft 32, piston 24-30 is outwards revolution again, exactly be with the rotary position of Fig. 6 contrast on, continuation is turned back in its UT-position again with 45 ° of rotary-piston 24-30, can contrast with Fig. 1, but be in about Fig. 1 with on 180 ° of positions of reversing or the like.

By transmission device 102 both can be under static state also can be at the run duration of oscillating piston engine 10, control cam 58 and 60 is around turning axle 79 revolutions, so that as the top discharge capacity of adjusting oscillating piston engine 10 having introduced.

The adjustment of oscillating piston engine 10 discharge capacities can depend on that particularly rotating speed carries out, exactly, the discharge capacity of the high more oscillating piston engine of rotating speed is more little, and rotating speed is low more then to become big, and this point can be by corresponding

supply chamber

106 and 108 hydraulic fluids and correspondingly control or adjust.

Claims

1. A rotary piston engine with a casing (12) in which a first and at least one second piston (24, 26) are arranged, which can jointly surround a casing-fixed rotating shaft (32) in the casing (12) ) rotation, and they rotate around the axis of rotation (32), around the axis of rotation (36) fixed to the piston perpendicular to the axis of rotation (32) and distributed through the center of the housing, opposite to each other in the first end position and the second end Rotational movement back and forth between positions, wherein the first and at least second pistons (24, 26) define a working chamber (48), wherein the first piston (24) and/or the at least second piston (26) have at least one operating mechanism (50, 52) guided along at least one control cam (58) when the first and/or second piston (24, 26) rotates to generate the first and/or at least second piston ( 24, 26) rotary motion, characterized in that the control cam (58) can be adjusted by means of an adjustment mechanism (74) to adjust the first and second pistons (24, 26) at least one of the first and second at least one of the second end positions.

2. The rotary piston engine as claimed in claim 1, wherein at least one of the first end position and the second end position is continuously adjustable by means of the adjustment mechanism (74).

3. The rotary piston engine as claimed in claim 1 or 2, wherein the first and the second end position of the first and at least the second piston (24, 26) are adjustable by means of the adjusting mechanism (74).

4. The rotary piston engine according to any one of claims 1-3, wherein the two sections (62, 64) of the control cam are rotatably supported on the casing around a casing-fixed rotary shaft (79) in opposite directions to each other (12).

5. The rotary piston engine according to any one of claims 1-4, wherein a third and a fourth piston (28, 30) are arranged in the housing (12), which are connected to the first and second pistons (24 , 26) in the housing (12) can be rotated around the axis of rotation (32) together, and at the same time between the third end position and the fourth end position between the rotary motion opposite to each other, wherein the third and fourth The piston defines a second working chamber (48); at least one of the third and fourth end positions is adjustable by means of an adjustment mechanism (74).

6. The rotary piston engine as claimed in claim 5, wherein at least one of the third end position and the fourth end position is continuously adjustable by means of the adjustment mechanism (74).

7. The rotary piston engine as claimed in claim 5 or 6, wherein the third and fourth end positions of the third and at least fourth pistons (28, 30) are adjustable by means of an adjusting mechanism (74).

8. The rotary piston engine according to any one of claims 5-7, wherein the third piston (30) is diametrically opposed to the first piston (24) with respect to the piston-fixed rotary axis (36), and the third terminal The position can be adjusted synchronously and in the same direction towards the first end position.

9. The rotary piston engine according to claim 8, wherein the fourth piston (28) is diametrically opposed to the second piston (26) with respect to the piston-fixed rotary axis (36), and the fourth end position can be synchronized and Adjust in the same direction to the second end position.

10. The rotary piston engine according to any one of claims 5-9, wherein the third piston (30) and/or the fourth piston (28) has at least one operating mechanism (54, 56), which mechanism The third and/or fourth pistons (28, 30) are guided along the second control cam (60) when rotating, to generate the rotary motion of the third and/or fourth pistons (28, 30); the second control cam (60) A position adjustment is possible by means of an adjustment mechanism (74) to adjust at least one of the third and fourth end positions of at least one of the third and fourth pistons (28, 30).

11. The rotary piston engine as claimed in claim 10, wherein the two segments (66, 68) of the second control cam (60) are rotatably mounted in opposite directions around a housing-fixed rotary shaft (79) Inside the housing (12).

12. The rotary piston engine according to any one of claims 5-11, wherein the adjustment mechanism (74) has a first cam element (76) and a second cam element (78), wherein the first cam element (76 ) and the second cam member (78) are sheared by intersecting and can rotate oppositely to each other and have first and second control cams (58, 60).

13. The rotary piston engine according to claim 12, wherein the first control cam segment (80) and the second cam member ( The second control cam segment (86) of 78) is movably connected relative to the second control cam segment.

14. The rotary piston engine according to claim 12 or 13, wherein the third control cam segment (82) of the first cam member (76) forming another control cam (58, 60) together with the second cam A fourth control cam segment (84) of member (78) is movably connected relative to the fourth control cam segment.

15. The rotary piston engine according to claim 13 or 14, wherein the first control cam segment (80) and the second control cam segment (86) and, if necessary, the third control cam segment (82) and the fourth control cam segment Cam section (84) comb type connection.

16. The rotary piston engine as claimed in claim 1, wherein the adjusting mechanism (74) has at least one hydraulic, pneumatic and/or electric transmission (102).

17. The rotary piston engine according to any one of claims 12-16, wherein at least one transmission (102) is hydraulic; where the cam member (74, 78) is close to the housing inner wall (104) of the housing (12) A variable-volume chamber (106, 108) for supplying hydraulic fluid is provided on at least one face of the hydraulic fluid.

18. The rotary piston engine according to claim 17, wherein the maximum stroke of the piston (24-30) is reduced by increasing the hydraulic pressure in the chamber (106, 108), and the piston (24) is enlarged by reducing the hydraulic pressure -30) maximum stroke.

19. The rotary piston engine according to any one of claims 1-18, wherein at least one operating mechanism (50, 52, 54, 56) and at least one control cam (58, 60) are magnetically activated such that at least one A magnetic attraction is generated between the operating mechanism (50, 52, 54, 56) and at least one control cam (58, 60).

20. The rotary piston engine according to any one of claims 1-19, wherein at least one operating mechanism (50, 52, 54, 56) and the associated piston (24, 26, 28, 30) are magnetically activated such that A magnetic attraction force is generated between at least one actuator (50, 52, 54, 56) and an associated piston (24, 26, 28, 30).