WO2016124431A1 - Engine with a piston guided on a double-cam cam disk - Google Patents

Abstract

The invention relates to an engine with a transmission for coupling a back and forth movement of a piston to a rotational movement of a double-cam cam disk (12). In one example, four rollers (14) are positively guided via roller bodies (18), which have a radius R and roll on an inner-side housing track (22a) with a radius 2R, to implement back and forth movements in the radial direction with respect to a center axis of the transmission (10). The four rollers (14) thereby run on an approximately figure-8 shaped double-cam cam disk (12). A piston (16) is guided via a roller (14) on the double-cam cam disk. Due to the coupling with the roller bodies (18), a straight guiding of the piston is effected, and the occurrence of lateral forces on the piston is prevented. As two-stroke or four-stroke engine, the engine enables a complete mass balancing, regardless of the number of pistons. In the case of a two-stroke engine, a lot of time for the combustion or gas exchange is available at the top or bottom dead centers of the piston.

Description

 MOTOR GUIDED ON A DOUBLE CURVE

 PISTON

The invention relates to a motor, comprising: at least one lifting element in the form of a piston; and a gear for coupling a reciprocating motion of the piston with a rotational movement of a double cam cam of the transmission.

 An engine with the above features is known in the form of the Fairchild Caminez engine, for example, "Unusual Engines", Stefan Zima, Reinhold Ficht, 3rd edition 2010, Vogel book publishing, ISBN 978-3-8343-3140-3, pages 220-222. The Fairchild Caminez engine described there is an air-cooled four-stroke four-cylinder engine with valve control. The pistons of the Fairchild Caminez engine mesh with roller bearings on a lisciskatenförmige cam and are connected by tie rods together to ensure the adhesion of the rollers with the cam on the upward stroke of the piston. Since two opposing pistons work in opposite directions, the result is a perfect mass balance. The disadvantage, however, is that high piston side forces can occur.

 The object of the invention is to provide a novel engine of the type mentioned, in which the transmission is particularly well suited to avoid the occurrence or transfer of lateral forces in the reciprocation of the piston.

 According to one aspect of the invention, an engine of the type mentioned is for

Provided, in which the transmission further comprises:

 four arranged to slide on the double cam cam slider with round, with respect to a respective central axis part circular track-shaped sliding contour or for rolling on the double cam cam arranged rollers, and

a straight-line transmission comprising a housing and four rolling elements annularly connected to an articulated chain and each having an outside, smooth rolling contour with a rolling radius R and each adapted to unroll on an inside path of the housing of radius 2R,

 wherein at least two of the rolling bodies have a toothed circular arc which is in engagement with a toothed circular arc of the housing,

wherein the rolling bodies are pivotally connected to one another on axes of rotation, which, when the rolling bodies roll on the inside track of the housing, form a rectilinear movement. exporting, and wherein these axes of rotation coincide with axes of rotation at which the respective rollers are rotatably coupled to the rolling bodies, or coincide with central axes of the part-circular sliding contours of the respective sliding body,

 wherein with the respective piston, a respective one of the rollers and a respective one of the sliding bodies is rotatably coupled about the respective axis of rotation.

 In particular, the object is achieved by a motor, comprising:

 at least one lifting element in the form of a piston; and

 a transmission for coupling a reciprocating movement of the piston with a rotational movement of a double cam cam of the transmission,

 the transmission further comprising:

 four rollers arranged to roll on the double cam cam, and a Geradführungsgetriebe with a housing and four rolling elements, which are annularly connected to an articulated chain and each have an outside, smooth rolling contour with a rolling radius R and are each adapted to one on unroll the inner side of the housing with the radius 2R,

 wherein at least two of the rolling elements have a toothed circular arc which is in engagement with a toothed circular arc of the housing,

 wherein the rolling elements are articulated to one another on axes of rotation which, when the rolling elements roll on the inside track of the housing, execute a rectilinear movement, and wherein these axes of rotation coincide with axes of rotation at which the rollers are rotatably coupled to the rolling bodies,

 wherein a respective one of the rollers is rotatably coupled to the respective piston about the respective axis of rotation.

 Instead of the rollers and the slider can be provided. These can be formed, for example, by the outer contour of the respective rolling bodies. The sliding bodies may for example be adapted to slide hydrodynamically on the double cam cam.

According to a further development of the invention, the feature of rolling the rolling bodies with an outside, smooth rolling contour with rolling radius R on a innenseiti- gene track of the housing with radius 2R can be omitted. In a further aspect of the invention, therefore, an engine of the aforementioned type is provided, in which the transmission further comprises: four arranged to slide on the double cam cam slider with round, with respect to a respective central axis part circular track-shaped sliding contour or for rolling on the double cam cam arranged rollers, and

 a linear guide transmission with a housing and four arcs, which are connected in a ring to form an articulated chain,

 wherein at least two of the arched bodies have a toothed circular arc which is in engagement with a toothed circular arc of the housing, the arched bodies possibly being supported directly on the housing via the toothed circular arches,

 wherein the arches are pivotally connected to each other at axes of rotation, which execute a rectilinear motion during the passage of the arches on the respective tooth arcs of the housing, and wherein these axes of rotation coincide with axes of rotation at which the respective rollers are rotatably coupled to the rolling elements Center axes of the part-circular sliding contours of the respective sliding bodies,

 wherein with the respective piston, a respective one of the rollers and a respective one of the sliding bodies is rotatably coupled about the respective axis of rotation.

 The toothing acts, for example, as a torque arm. According to the further development, in particular, no further support of the arched body on the inside of the housing is required: In contrast to the variant with rolling bodies, the arched bodies have no outside, smooth rolling contours with rolling radius R, which roll on an inside path of the housing with the radius 2R.

 In particular, the object is achieved by a motor, comprising:

 at least one lifting element in the form of a piston; and

 a transmission for coupling a reciprocating movement of the piston with a rotational movement of a double cam cam of the transmission,

 the transmission further comprising:

four sliding bodies with a round, part-track-shaped sliding contour with respect to a respective central axis, arranged for sliding on the double-cam cam, and a straight-line transmission with a housing and four curved bodies, which are connected in a ring to form an articulated chain, wherein at least two of the arched bodies have a toothed circular arc which is in engagement with a toothed circular arc of the housing, the arched bodies possibly being supported directly on the housing via the toothed circular arches,

 wherein the arches are pivotally connected to one another on axes of rotation, which execute a linear movement when the arches of the bodies extend at the respective tooth arcs, and wherein these axes of rotation coincide with central axes of the part-circular path-shaped sliding contours of the sliding bodies,

 wherein with the respective piston, a respective one of the sliding bodies is rotatably coupled about the respective axis of rotation.

 The axis of rotation about which the relevant roller or the sliding body is rotatably coupled to the respective piston thus coincides with one of the axes of rotation, on which two rolling elements or curved bodies are hinged together. The result is a straightforward positive guidance of the respective roller or the central axis of the sliding contour of the slider. The transmission of lateral forces is thus avoided both in the coupling between the piston and the respective roller or sliding body as well as in the coupling between the piston or the roller / slider and the Rollkör- pern / bow bodies. This is advantageous over a piston engine with connecting rods, since the friction caused at an inclined connecting rod on the piston wall is omitted here due to the straight guide. The mechanical friction losses can thus be reduced considerably. This is also advantageous over the Fairchild Caminez engine, in which each piston two hinge axes are provided for each tie rods for connection to the next piston and no straight guide takes place. There, therefore, reaction forces can be transmitted as lateral forces and as tilting moments on the piston.

 If here or in the following of a rotary or articulated axis is mentioned, it is always understood a straight line around which the joint movement or rotation of the respective components takes place. The position of this line is fixed with respect to the component. In the case of a rotation of a shaft, the axis of rotation corresponds to the axis of rotation of the shaft.

The transmission for coupling a reciprocating motion of the piston with a rotational movement of the double cam cam may also be referred to as a cam gear. When the double cam cam is driven as a driven element, the forces are supported on the housing over the smooth rolling contours of the rolling elements on the housing by the coupling of the double cam cam on the rollers or sliding body in the case of rolling elements with the rolling elements, and the torque is applied to the Tooth arcs are distributed and supported on the housing. All forces and torques caused in the gearbox are then supported inside the gearbox, and any lateral forces occurring at the coupling to the piston, which occur due to the attack of the roller / slider on the double cam cam, are also supported on the housing. The motor can thus be described as a motor with linear piston movement with integrated torque and lateral force support.

 Depending on the choice of the curve shape of the double cam cam can be achieved that with continuously rotating double cam cam as the output element of the transmission, the piston at the outer and inner reversal point of the reciprocating motion performs a temporary stoppage or an uninterrupted reciprocation performs.

 The engine converts a linear piston stroke caused by volume change of the working space, for example combustion chamber, via the engagement of the straightforward positively driven engagement element, i. the roller or the slider on the cam directly into a rotational movement of the cam.

 The engine may, for example, have one, two, three or four pistons, each guided over an associated roller / slider on the double cam cam.

 In one embodiment, the motor has at least two lifting elements in the form of pistons, which are arranged opposite one another with respect to the axis of rotation of the double-lobe cam, and with the respective piston a respective one of the rollers or a respective one of the sliding bodies about the respective axis of rotation is rotatably coupled.

 Preferred embodiments and further developments of the invention are given below and in the subclaims.

 Preferably, in a first transmission plane of the transmission, the double cam

Cam and the four rollers or sliding bodies arranged, and in at least a second, parallel to the first plane and laterally offset transmission plane are the four Roller body or the arch body or at least the tooth arcs arranged in the housing.

 Preferably, a shaft on which the double-cam cam is arranged passes through a free space in the middle of the chain of the respective interconnected rolling bodies / bow bodies.

 Preferably, the double-cam plate is formed with two convex and two concave curve parts, wherein convex and concave curve parts follow each other alternately.

 In the case of those rolling bodies which have the toothed circular arc, the toothed circular arc is preferably arranged next to the smooth rolling contour at the same radius R, relative to an axis of symmetry of the smooth rolling contour.

 Preferably, at least one lifting element is coupled to a spring element, wherein in a movement section of the reciprocating movement of the lifting element, the spring force of the spring element in the direction of movement of the lifting element is effective. In this movement section, the movement of the lifting element is thus supported by a spring force of the spring element. Accordingly, in another movement portion of the reciprocation of the lifting element, the spring force of the spring element against the direction of movement of the lifting element is effective, i. the movement of the lifting element takes place in the other movement section against a restoring spring force of the spring element. The spring element stores kinetic energy. Due to the forced due to the spring element vibration improved smoothness can be achieved. It may be provided, the spring element and / or a leveling compound. The double cam cam and the spring element are part of a mechanical vibration system, wherein the spring element forms an energy store.

 A piston chamber, in which the respective piston is accommodated, may be limited at the rear by the piston alone. The piston chamber may also have a back bottom.

In one embodiment, the respective piston is received in a respective piston chamber, and a piston rod via which the piston is connected to the respective roller / slider passes through an opening in the bottom of the piston chamber. The piston is preferably rigidly connected via the piston rod to the axis of rotation of the respective roller or one coinciding with the central axis of the slider Rotary axis connected, ie the piston rod determines the relative position of the piston and roller / slider. The piston forms, together with a head portion of the piston chamber a closed cavity, which can also be referred to as a working space or pressure chamber, eg combustion chamber. The term "head" or "bottom" is to be understood from the perspective of the oscillating piston and corresponds to the front side or the rear side of the piston The rear side of the piston faces the transmission.

 Preferably, the piston chamber is formed by a bottom, a side wall and a bottom opposite the head part of a piston housing.

 Preferably, the piston forms a further closed cavity together with a bottom section of the piston chamber. The piston may be, for example, a double-acting piston. There are two working or combustion chambers separated by the piston.

 Preferably, the piston rod is sealed by a seal against the bottom of the piston chamber.

 Preferably, the motor has at least one piston guide, which guides the respective piston rod at a position which is spaced from the axis of rotation, at which the piston rod is coupled to the relevant roller / sliding body concerned. A degree of freedom present at the axis of rotation is thereby removed, and the piston rod and thus the piston are guided at two positions in the rectilinear direction, i. at the coupling with the rolling bodies and at the piston guide. The piston guide is arranged on a side of the piston facing the transmission. The piston guide may be a sliding guide or sliding sleeve. In one example, the piston guide seals the piston rod against the bottom of the piston chamber.

 The respective piston is preferably accommodated in a respective piston chamber and is arranged at its circumference at a distance from a side wall of the piston chamber surrounding it. In particular, the at least one piston is adapted to be guided over a rectilinearly guided piston rod, to be moved without contact to and spaced from the side wall of the piston chamber of the respective piston along the side wall.

Preferably, the engine comprises at least one supply means for supplying a fuel and an evaporation medium from separate reservoirs into a combustion chamber which passes through the side wall of the piston chamber within the piston chamber. chamber, the front of the piston and an opposite top wall of the piston chamber is limited. The supply means may comprise separate feed openings for the fuel and the evaporation medium, and may include a timing control to synchronize the supply with the duty cycle of the piston. It can be supplied to fuel, evaporation medium or simultaneously fuel and evaporation medium. The motor is preferably designed for a working temperature of the combustion chamber, in which the evaporation medium evaporates explosively.

 In an engine, for example, two of the motor units described may be coupled together, for example, the respective double cam cams may be coupled together, such as a common shaft. The engine may include, for example: at least a first piston, at least one second piston, and at least first and second transmissions for coupling reciprocation of a respective piston with rotational movement of a respective dual cam cam of the respective transmission, the transmission respectively has the features of the transmission of the engine of the type described above, and wherein the double cam cams of the transmission are coupled together via a common shaft.

 Preferred embodiments of the invention are explained below with reference to the drawing. In the examples described below with reference to the figures, in particular those features are explained by which the examples differ from conventional internal combustion engines. Show it:

 Figure 1 is a schematic view of an open engine with a gear with double cam cam and four rolls rolling thereon.

 Fig. 2 is a schematic view of a Geradführungsgetriebes of the engine of Fig. 1;

 Fig. 3 is a schematic sectional view through the engine;

 Fig. 4 is a schematic representation of an electric vehicle with the motor as an auxiliary motor;

 Fig. 5 is an example of a rolling body of the transmission of the motor of Fig. 1-3;

 Fig. 6 is a schematic representation of an embodiment of the rollers of

Gearbox of the engine;

Fig. 7 is an example of a motor having a plurality of motor units; 8 shows an example of a motor with a spring element as an energy store; and FIG. 9 shows a schematic illustration of a piston chamber of an example of an internal combustion engine with internal cooling.

 The motor shown in part in FIG. 1 has a cam gear 10 and an engine block 11. The gear 10 has in a first, central gear plane a double cam cam 12, which is arranged on a shaft 12A with rotation axis 13 and a Form that is approximately liscinate-shaped or 8-shaped, ie has approximately the shape of an eight (8), with two convex curve parts and two concave curve parts. Here, convex and concave curve parts follow each other alternately. As a result, two cams are formed, on which the radius of the cam disk 12 is increased in relation to the adjacent sections. The curve shape of the outer contour of the double cam cam 12 is 180 ° rotationally symmetrical about the axis of rotation 13 and has two levels of mirror symmetry, each comprising the axis of rotation 13. It is thus point-symmetrical.

 On the double cam cam 12 four rollers 14 roll off. They each have the same radius. They are arranged at mutually offset by 90 ° about the rotational axis 13 of the double cam cam 12 positions and adapted to each perform a reciprocating motion in the radial direction, based on the axis of rotation 13, as will be explained below. The rollers 14 are rotatably coupled at their respective axis of rotation 15 to a respective lifting element in the form of a piston 16. A lifting element is understood to be an element of the motor which is adapted to carry out a lifting movement, in this case especially a piston of the motor ,

 Fig. 2 shows a Geradführungsgetriebe 17 of the transmission 10 with arranged in a second, lateral plane of the transmission 10 rolling elements 18. The rolling elements 18 are pivotally connected to each other to form a closed chain. In this case, the axes of rotation at which two adjacent rolling elements 18 are connected to one another correspond to a rotation axis 15 of a respective roller 14. The axes of rotation are designated 15 in FIG. 1 and FIG. In each case two axes of rotation 15 are connected to each other in a straight line via a connecting portion 18 D of the respective rolling body 18. The connection sections 18D form a parallelogram.

The rolling elements 18 are arranged in a housing 22 which is fixedly connected to the engine block 11. The rolling elements 18 each have at least one outside, smooth Rolling contour 18 A with a radius R, relative to an axis of symmetry 24 of the rolling contour, and they roll in the housing 22 on an inside partial circular path 22 A of the housing 22 from. This track 22A has a radius 2R, with respect to the center axis of the gearbox and the motor, which corresponds to the rotational axis 13 of the double-cam plate 12. The axes of rotation 15, on which the rollers 18 are coupled to each other pivotally, are located on the radius R, relative to the axis of symmetry 24 of the respective roller 18. As a result, describe these joints or axes of rotation 15 when rolling the roller 18 a precisely straight line. Thus, they perform in a forward and backward rolling movement of the rolling elements 18 on the web 22A a straight-ahead reciprocating motion in the radial direction, relative to the rotational axis 13 of the double cam cam 12 from. The gear 17 with the coupled rolling elements 18 thus causes a straight guide of each of the rollers 14, ie a forced guidance of the axes of rotation 15 of the rollers 14, and thus the coupled piston 16, in straight directions. Each piston 16 performs a rectilinear reciprocation. The directions of movement are mutually offset by 90 °. In the engine block 11, also referred to as a cylinder block, the preferably circular cylindrical piston 16 are guided in a respective radial bore.

 The rolling elements 18 also each have a toothed circular arc 18B whose teeth engage the radius R, with respect to the symmetry axis 24, in teeth of a toothed circular arc 22B of the housing 22. In particular, the Zahnkreisbögen 18 B are arranged laterally offset in parallel with the smooth rolling contours 18 A next to these, and the Zahnkreisbögen 22 B are concurrently with the smooth tracks 22 A at the radius 2 R, based on the transmission center or the axis of rotation 13 of the double cam disc 12 laterally offset next the respective web 22A arranged. The smooth rolling contours 18A and smooth tracks 22A are configured to transmit forces. The intermeshing tooth arcs 18B and 22B are configured to transmit torques and force a slip-free run. The smooth rolling contours 18A and tracks 22A also prevent radial loading of the tooth flanks of the tooth arcs 18B, 22B.

 The housing 22 is also referred to as a control housing because it controls the movement of the rolling elements 18. The toothed circular arc 22B is an internal toothing in the recess of the housing 22, in which the rolling body 18 is received.

The chain formed by the four connected rolling elements 18 is also referred to as a timing chain. The toothed circular arcs 18B of the rolling elements 18 each form an external perforation. The intermeshing tooth arcs 18B, 22B thus help to prevent jamming of the linear guide gear and slippage of the rollers 18 on the tracks 22A. Preferably, the tooth arcs 18B of the four rolling bodies lie in one plane.

 The Zahnkreisbögen 18 B and rolling contours 18 A and the corresponding

Tooth arcs 22B and pitch circles 22A are formed according to the amount of rolling motion, i. the rocking angle, only required on a sub-segment of less than 90 °, for example, on a sub-segment of 45 °, based on the web 22A of the housing, ie 90 ° relative to the rolling contour 18 A.

 The shape of the double-cam disc 12 is structurally determined by the outer and inner extreme positions of the rollers 14 and the center position of the rollers 14 shown in FIG. At the extreme positions, the tangents of the double cam cam 12 are given. In Fig. 1, the positions of rollers 14 are shown in dashed lines at outer and inner dead centers with a corresponding position of the double cam cam. The concave curve part of the double cam cam 12 determines the course at the outer dead center of the piston 16, and the convex part of the double cam cam determines the course at the inner dead center of the movement of the piston 16. The shape of both cam parts is characterized by the coupling of the rollers fourteenth ie the always constant distance between two adjacent rollers 14, mutually conditional. The shape of the curve of the double cam cam disc 12 can influence which time course of the reciprocating movement of the respective roller 14 and thus of the piston 16 corresponds to a uniform rotation of the double cam cam disc 12. The shape of the double cam cam 12 is chosen so that the rollers 14 always rest against the cam.

 The rollers 14 transmit the forces between the respective piston 16 and the

Double Cam Cam 12. As the double cam cam 12 rotates, each piston 16 reciprocates in a straight line on a straight line passing through the rotational axis of the double cam cam 12. The respectively opposing pistons 16 move in opposite directions on a common straight line. The movements are synchronized, so that the mass forces completely compensate each other, without additional masses are required. In the example shown, the rollers 14 are connected to the rolling elements 18 and the piston 16 by a respective shaft 28. The axes of rotation 15 are the central axes of the shafts 28. For example, the rollers 14, the piston 16 and the rolling elements 18 are each connected by rolling bearings with the shaft 28. Optionally, for example, the elements of one of said groups of elements are fixedly connected to the shaft 28, such as the pistons 16.

 In the schematic sectional illustration in FIG. 3, in the first gear plane the double cam cam 12 and the rollers 14 are shown with a view of their running surfaces, while on both sides thereof in each case in a second or third plane of the gear a FIG corresponding straight-line transmission 17 is arranged with four rolling elements 18. The arranged on both sides of the transmission rollers 18 are connected by the shafts 28 with each other and with the rollers 14. The respective piston 16 is also connected via a respective one of the shafts 28 with the respective roller 16 and the respective rolling elements 18. The camshaft 13 is mounted on the housing 22, for example via roller bearings. The toothings or toothed circular arcs 18B and 22B bring about, in particular, synchronous operation of all the rolling bodies 18 of the two linear guide gears 17.

 In this example, each rolling element 18 has two laterally offset, co-rotating, smooth rolling contours 18A, between which the toothed circular arc 18B is arranged. The respective rolling body 18 may be constructed, for example, of three plates fixedly connected to each other, of which one middle forms the toothed circular arc 18B and two outer ones each form a smooth rolling contour 18A. The rolling elements 18 are connected to each other by the middle plate of a rolling body projects into a gap 29 between the outer plates of the next rolling body.

 In the example shown, the rolling elements 18 and the double cam cam 12 are each provided with recesses in order to reduce the mass of the moving parts.

 The respective housing 22 may for example be shaped in the form of a recess provided with a flat plate and fixedly connected to the engine block 11. This allows a very dimensionally stable, rigid construction.

The camshaft, ie, the shaft 12A of the double cam cam 12, is straight, unlike a crankshaft of a conventional reciprocating engine. It runs in the section in which they on the cam 12 and the respective role 14 is coupled to the piston 16, straight on its axis of rotation. In addition, due to the described structure of the engine, the shaft 12A can be made comparatively short. It can also be made thick, so that it is insensitive to deflection and twisting, again in contrast to the conventional crank drive motor. It is also advantageous that the shaft 12A and the double cam cam 12 is constructed with two point-symmetrical with respect to the axis of rotation cam. As a result, the center of gravity of the double cam cam 12 lies on the axis of rotation and causes no imbalance.

 While in the described engine with pairwise opposing piston 16 a perfect mass balance is possible, for example in two pistons and four pistons, at a different number of pistons, such as a one-piston engine, mass balance by an additional mass or balancing mass on the piston 16 take place opposite roller 14, such as in the form of another lifting element 16th

 In contrast to the Fairchild Caminez motor, the rollers are guided in a straight line by the rolling elements 18 and the linear guide transmission, so that no transverse forces are exerted on the wall of the piston 16 or the surrounding bore in the engine block 11. This reduces wear and improves mechanical efficiency. In particular, there is no tilting of the piston, and the piston may have a reduced mass due to the simpler structure.

 Preferably, the engine is an internal combustion engine, in particular a two-stroke engine or a four-stroke engine. It is advantageous that at the top dead center of the piston much time is available for the combustion and at the bottom dead center of the piston is a lot of time for the gas exchange available. Due to the shape of the double cam cam, the times for combustion and the gas exchange can be significantly influenced. This is particularly advantageous over a conventional crank drive motor. The described motor therefore enables an improvement of the efficiency and a reduction of the energy consumption. For example, air inlets and exhaust gas outlets may be provided which are connected to the combustion space at the bottom dead center of the movement of respective pistons 16.

It is also advantageous that the double cam cam per piston and per revolution produces twice as many strokes as a conventional crank gear. The The mentioned liter power can therefore be doubled at the same speed, or it can be achieved at half speed the same liter performance.

 By making it possible to achieve a perfect mass balance in a simple way, new possibilities for the development of small engines are created. The engine may for example be connected to a generator for power generation, to a heat pump, to an aggregate for the coupling of electricity and heat generation, or to an emergency generator. Also, a lift member may be part of a motor-connected linear generator 26 (FIG. 4) for power generation and may include, for example, a magnet 26A configured to perform a reciprocation in a conductor coil 26B or conductor loop.

 For example, as shown in FIG. 4, the engine may be provided in an electric vehicle as an auxiliary or backup motor 25 and via a linear generator 26 connected to the engine or a conventional rotary driven generator when the state of charge of the battery BATT of the electric vehicle falls below a threshold current to recharge the battery. The engine thus serves as an emergency unit. This is where the compact design and the smoothness of the engine comes in handy. The engine can be operated efficiently at a constant speed. He can e.g. at the same time also serve to generate heat for heating the electric vehicle or for cooling. The energy consumption for heating or cooling can therefore be optimized compared to a conventional electric vehicle.

 However, the engine is not arranged to mechanically directly drive the wheels of the vehicle, unlike an internal combustion engine of a conventional hybrid vehicle. It is thus not set up for mechanical coupling with the mechanical drive train. Rather, the electric vehicle comprises, for example, in a manner known per se to the driven wheels associated motors M, which are supplied under the control of a drive train controller CON from the battery BATT with energy. A regeneration of braking energy is also possible.

 Since compared to a conventional crank drive engine eliminates the space required for the projecting camshaft and the connecting rods, the described engine allows a very small volume and thus a low weight.

Instead of the described, rigid connection of two axes of rotation 15 via a roller 18, it is also conceivable, as shown in FIG. binding connecting portion 18 D of the respective rolling body 18 to arrange a pressure piece 30, so that the axes of rotation 15 are connected to the rolling body 18 via the pressure piece 30 with each other. The pressure piece may for example be made of a softer material than the surrounding part of the connecting portion 18D and serves to compensate for any game. As a result, the rollers 14 can be more easily held in contact with the double cam cam 12. A recess in the rolling body 18 is preferably provided when a pressure piece 30 is provided, so that the rolling body 18 has the connecting portion 18D with inserted pressure piece 30 in a straight connection line between the axes of rotation 15 and, separated therefrom by the recess, a bridge arch which forms the smooth one Rolling contour 18A and optionally the toothed circular arc 18B has. Also conceivable is the use of elastic rollers 14.

 Fig. 6 shows schematically the structure of an embodiment of a roller 14, wherein the roller consists of at least a first disc 32 and a second disc 34, wherein the discs 32, 34 have different material hardnesses. Preferably, a disc 32 is an inner disc disposed between two outer second discs 34. For example, a softer disc can be inserted between two harder discs. Conversely, a harder disk 32 may also be arranged between two softer disks 34. Preferably, the softer discs each have a slightly larger radius than the harder discs. This makes it possible to compensate for an inevitable game. For example, the first discs 32 may have a more wear resistant surface than the second discs 34. A soft coating of the second slices is also conceivable.

 The double cam cam 12 may be composed in a corresponding manner as the described roller 14 from several discs of different material hardness and / or with different wear-resistant surfaces.

In a continuation of the described examples, it is also possible to perform on the engine in addition to running as a piston of the engine lifting elements 16 another lifting element 16, for example as a piston pump, such as an air pump or pump to support the gas exchange. The motor may comprise a lifting element, for example, which can serve as a working piston of a compressor for the air supplied to the combustion chamber. A compressor can, for example, also serve to generate an air flow for cooling the engine. Hereinafter, further examples of the engine will be described. Unless otherwise stated, the structure corresponds to the above examples. Like or corresponding parts are identified by the same reference numerals. The characteristics of the individual examples can be combined with each other.

 Fig. 7 shows schematically a further embodiment of an engine in which a plurality, for example three gear 10 are provided with a common camshaft 12 A coupled double cam plates 12, wherein the respective double cam cam 12 four rollers 14 and the straight described above - Guide 17 are provided. There are thus several engine sections, each with a gear 10 and at least one piston 16 or 16 'are provided. The structure corresponds to the extent three coupled units that can be configured as two-stroke engines, four-stroke engines or pumps for gaseous and / or liquid media according to Figures 1 to 3, but with a respective piston 16 and 16 'with appropriate respective counterweight as opposite lifting element to obtain a mass balance. In a common intermediate wall of the motor sections, for example, a roller bearing for supporting the camshaft 12A may be provided, the inner diameter of which corresponds at least to the maximum diameter of the double cam cam 12. This simplifies assembly and improves the quality of storage. The camshaft 12A may be formed here, for example disc-shaped.

 The gear 10 are coupled together so that the pistons 16, 16 'of the individual

Motor sections work at different times. As a result, the time distribution of the drive torque of the engine is uniform. By means of different alignment of the double cam cams 12, a total of three times two, that is to say six piston strokes per revolution of the camshaft 12A can be carried out for one piston per double cam cam 12. The directions of movement of the respective pistons 16, 16 'of the motor sections are aligned parallel to one another. It results in a small volume of construction. In a favorable installation position all directions of movement of the pistons are vertical. This further reduces any lateral forces on the pistons due to their own weight. FIG. 8 shows an example of the motor in which at least one of the lifting elements 16 is coupled to a spring element 36. The spring element 36 is here a compression spring, which is connected at the other end to the transmission housing. At one downward movement of the respective lifting element 16, the spring is compressed and stores energy. This is released again during the inward movement of the lifting element 16. Alternatively, other types of springs or other elastic spring elements can be used.

 Fig. 9 shows a schematic partial representation of a motor according to a development of the invention. The engine corresponds for example to the examples described above with gear 10 and linear guide 17 and is a 2-stroke engine.

 The lifting element here comprises a round piston 16 and a piston rod 40 which is rigidly connected to the piston 16 and connects the piston 16 to the respective roller 14. The piston 16 is received in a cylindrical piston chamber 42 of the motor housing, with side wall 44, bottom 46 and top wall 48. The piston rod 40 is guided in a fixed housing fixed piston guide 50 between the piston chamber and the roller 14. The piston 16 is guided by the piston rod 40 in a straight line. The piston guide 50 also seals the piston chamber against the piston rod 40. It thus forms a seal for the rear part of the piston chamber. This is possible - in contrast to a crankshaft motor - due to the rectilinear reciprocation of the piston rod 40.

 The piston 16 is arranged at its entire circumference at a distance from the surrounding side wall 44. That is, the side wall 44 surrounds the piston 16 without contact. In other words, the piston 16 is received without contact in the piston 42 enclosed by the side wall 44 piston chamber. It is adapted to carry out the non-contact back and forth movement along side wall 44 with respect to side wall 44.

 A combustion chamber or combustion chamber 52 is bounded by the side wall 44, the front of the piston 16 and the opposite top wall 48. During operation of the engine, the at least one piston 16, guided by the rectilinearly guided piston rod 40, moves without contact and is spaced from the side wall 44 of the piston chamber 42 of the respective piston 16 along the side wall 44.

At the periphery of the piston 16, the piston chamber 42 between the piston 16 and the side wall 44 has a gap 54 with a labyrinth 56 which comprises at least one piston groove. The labyrinth 56 is formed in the outer circumferential surface of the piston 16. In its simplest form, the labyrinth 56 consists of a piston groove, which in turn Catching direction of the piston 16 extends. In the example, several circumferential piston grooves are present. The labyrinth 56 causes the stroke of the piston to extend the flow path through the gap 54 and thereby acts with the smooth side wall 44 as a gap-gap labyrinth seal. Thus, the engine has a nip labyrinth seal with at least one piston groove. The piston 16 is thereby sealed contactless against the side wall 44. The piston 16 is thus guided exclusively outside the portion of the side wall 44 swept by the piston 16. In particular, there is no piston ring to the seal. In the labyrinth 56, a post-combustion of penetrating gas can take place. Any passing gas or exhaust gas may be expelled at the bottom of the piston.

 On the outside of the wall 44, 46, 48 of the piston chamber 42 is an insulation in the form of a thermal barrier coating 58 made of a porous, refractory material. The material has a lower density than the material of the piston chamber wall 44, 46, 48. As a material such as ceramic fibers, high-temperature wool and / or other, solid thermal insulation materials into consideration. By a refractory material is meant a material capable of withstanding a stress of at least 500 ° C. The thermal barrier coating 58 serves to improve the thermal insulation of the piston chamber 42 from the environment, to allow a high operating temperature and a rapid heating of the piston chamber 42. This is for example at least 500 ° C or 600 ° C and is preferably in the range of about 800 ° C to 1000 ° C. Due to the straight guidance of the piston rod 40, the rear side of the piston chamber, that is to say the bottom 46 thereof, can also be provided with the thermal barrier coating 58. This allows a particularly good thermal shielding of the transmission 10 from the piston chamber 42. The engine may be referred to as a combustion chamber engine.

 The wall of the piston chamber, in particular the side wall 44 and the top wall

48, and the front surface of the piston 16 are preferably made of a refractory material such as a steel suitable for turbine blades. As materials and ceramics or other high temperature resistant materials into consideration. By adjusting the expansion coefficients of the materials, the gap width between the piston 16 and side wall 44 can be optimized.

The engine includes a first supply or injector 60 for supplying or injecting fuel from a first tank 62, such as gasoline or diesel, and a second supply or injection device 64 for supplying or injecting an evaporation medium in the form of water, in particular demineralized water, from a second tank 66, as well as inlet and outlet slots 67 for the gas exchange. Controlled by a control device 68 which is connected to an optional temperature sensor 70, the fuel and / or the evaporation medium is supplied to the piston chamber 42 synchronized with the cyclical piston movement. The feed takes place in the combustion chamber 52 in the front part of the piston chamber 42. Further details of the engine are known in the art from conventional engines and are not shown here in detail. The engine works on the two-stroke process.

For example, a supply of fuel and evaporation medium take place alternately. By injecting evaporation medium at an operating temperature of the combustion chamber, ie, the combustion chamber 52, which exceeds the boiling point of the evaporation medium, a sudden evaporation of the evaporation medium takes place. Free kinetic energy is transferred to the piston and used as drive energy. At the same time takes place by the evaporative cooling cooling of the piston and the piston chamber 42. It thus takes place both a burning of the fuel under displacement of the piston, as well as evaporation of the evaporation medium under displacement of the piston. The evaporation medium may be referred to as cooling fuel, the fuel as heating fuel. For example, the controller 68 is configured to control the fuel and evaporative media supply means to alternately supply fuel and evaporative medium to the combustor. In either cycle of reciprocation of the piston, either fuel or the evaporation medium is supplied. By controlling the sequence of supply of fuel and supply of evaporation medium, a working temperature range can be maintained by, for example, when an upper temperature value is exceeded, evaporation medium is supplied and fuel is supplied when a lower temperature value is undershot. The upper and lower temperature values may, for example, be 600 ° C. and 500 ° C., these values being given only as an example. A conventional radiator is not required. Also a simultaneous supply of fuel and evaporation medium is conceivable. Waste heat of an evaporation medium-containing exhaust gas can also be used in a heat exchanger for preheating the supplied combustion air. This increases the efficiency. Alternatively, or in addition to the second evaporative medium supply means 64, the motor may include a cooling medium supply means 80 for supplying a cooling medium to the back of the piston of the piston chamber 44. For example, the cooling medium may be supplied and discharged via a supply port 82 and an exhaust port 84 in the rear portion of the piston chamber, which are in fluid communication with a rear portion of the piston chamber 44 at least at a front piston position. As a result, the piston chamber 44 can be traversed and cooled with the cooling medium, for example air, on the rear side of the piston 16. In particular, the piston rod 40 can thereby be cooled. For example, it is also possible for the cooling air to flow downwards along the shaft (piston rod) 40 and to cool the piston guide 50. The cooling medium supply means 80 may be an active or passive supply means, passively made, for example, with check valves, or active with a blower device and / or actively controlled valves. It is also conceivable internal cooling of the piston via an inner cavity of the piston and the piston rod.

 The motor described can also be constructed with a double-acting piston, in which a combustion chamber 52 is provided on each side of the piston 16.

 In further embodiments, the elements identified by the reference numeral 14 in the drawing may be sliding bodies 14, which may, for example, be fixedly or integrally connected to a respective rolling body 18. They each have a round, with respect to a respective central axis 15 part-circular sliding contour (in the example shown formed by a peripheral portion of the barrel-shaped slider 14). This is arranged to slide on the double cam cam 12. The axes of rotation 15 of the rollers 18 coincide with the central axes 15 of the part-circular sliding contours of the respective sliding body 14. With the respective piston 16 is a respective of the slider 14 is rotatably coupled to the respective axis of rotation 15.

In further embodiments, the elements identified by the reference numeral 18 in the drawing may be arched bodies 18 which are connected in a ring shape to form an articulated chain. The toothed circular arcs 18B of the arched bodies 18 are respectively in engagement with a toothed circular arc 22B of the housing 22. The arched bodies 18 are pivotally connected to each other at the axes of rotation 15, which during the passage of the arched bodies 18 at the respective toothed circular arcs 22B of the housing 22 a rectilinear movement perform, with the arch body 18 at most on the tooth Support arcs 18B, 22B directly on the housing. That is, the rolling contours 18A of radius R and / or the inside tracks 22A of the housing 22 of radius 2R are omitted.

 The features of all examples described above may be combined with each other unless otherwise specified or mutually exclusive.

Claims

1st engine, comprising:  at least one lifting element in the form of a piston (16); and  a transmission (10) for coupling a reciprocating movement of the piston (16) with a rotational movement of a double cam cam (12) of the transmission (10),  wherein the transmission (10) further comprises:  four arranged to slide on the double cam cam (12) sliding body (14) with round, with respect to a respective central axis part circular track-shaped sliding contour or for rolling on the double cam cam (12) arranged rollers (14), and  a linear guide transmission (17) having a housing (22) and four rolling bodies (18) which are annularly connected to an articulated chain and each have an outer, smooth rolling contour (18A) with a rolling radius R and are each adapted to an inside Roll web (22A) of housing (22) with radius 2R,  wherein at least two of the rolling bodies (18) have a toothed circular arc (18B) which engages with a toothed circular arc (22B) of the housing (22),  wherein the rolling bodies (18) are pivotally connected to one another on axes of rotation (15) which, when the rolling bodies (18) roll on the inside web (22 A) of the housing (22), execute a rectilinear movement, and these axes of rotation (15) coincide with axes of rotation (15) on which the respective rollers (14) are rotatably coupled to the rolling bodies (18), or coincide with central axes of the part-circular sliding contours of the respective sliding bodies (14),  wherein a respective one of the rollers (14) or a respective one of the sliding bodies (14) is rotatably coupled to the respective piston (16) about the respective axis of rotation (15). 2nd engine, comprising:  at least one lifting element in the form of a piston (16); and  a transmission (10) for coupling a reciprocating movement of the piston (16) with a rotational movement of a double cam cam (12) of the transmission (10),  wherein the transmission (10) further comprises: - Four arranged to slide on the double cam cam (12) sliding body (14) with round, with respect to a respective central axis part circular track Gleitkon- or rolling on the double cam cam (12) arranged rollers (14), and  a linear guide transmission (17) having a housing (22) and four curved bodies (18), which are connected in a ring to form an articulated chain,  wherein at least two of the arcuate bodies (18) have a toothed circular arc (18B) which is in engagement with a toothed circular arc (22B) of the housing (22), wherein the arcuate bodies (18) at best over the Zahnkreisbögen (18B, 22B) directly to the housing support,  wherein the arcuate bodies (18) are pivotally connected to one another on axes of rotation (15) which, during the passage of the arcuate bodies (18) on the respective tooth arcs (22B) of the housing (22), execute a rectilinear motion, and wherein these axes of rotation (15) coincide with Rotary axes (15) on which the respective rollers (14) are rotatably coupled to the rolling bodies (18), or coincide with central axes of the part-circular sliding contours of the respective sliding bodies (14),  wherein a respective one of the rollers (14) or a smaller one of the sliding bodies (14) is rotatably coupled to the respective piston (16) about the respective axis of rotation (15). 3. Motor according to claim 1, wherein the four connected to a hinged chain rolling bodies (18) on one side of the double cam cam (12) are arranged and four correspondingly formed and connected to a hinged chain further rolling bodies (18 ) of the linear guide transmission (17) are arranged on another side of the double cam cam disc (12) and are arranged to unroll there on a further inside track (22A) of the housing (22) with the radius 2R,  wherein further tooth arcs (18B) of at least two of the further rolling bodies (18) engage with corresponding tooth arcs (22B) of the housing (22), and wherein the rolling bodies (18) of the one side of the gear (10) with the rolling bodies (18) of the other side of the transmission at common axes of rotation (15) and connected to the rollers (14) or sliding bodies are connected. 4. Motor according to claim 2, wherein the four connected to a hinged chain bow body (18) on one side of the double cam cam (12) are arranged and four correspondingly formed and connected to a hinged chain further arched bodies (18) of the linear guide transmission (17) are arranged on another side of the double cam cam disc (12),  wherein further tooth arcs (18B) of at least two of the further arcuate bodies (18) engage with corresponding tooth arcs (22B) of the housing (22), and  wherein the arcuate bodies (18) of one side of the transmission (10) are connected to the Bogenkör- pern (18) of the other side of the transmission to common axes of rotation (15) and connected to the rollers (14) or sliding bodies. 5. Motor according to claim 1 or 3, wherein in those rolling bodies (18) having the Zahnkreisbogen (18 B), the Zahnkreisbögen (18 B) between two smooth rolling contours (18 A) is arranged with the rolling radius R or the smooth rolling contour (18 A) is arranged between two tooth arcs (18B),  wherein the roll contours (18A) and tooth arcs (18B) extend laterally offset from one another at the same radius R relative to an axis of symmetry (24) of the respective rolling contour (18A) at least on a subsection of the circumference of the respective rolling bodies (18). 6. Motor according to one of the preceding claims, wherein the respective roller (14) and at its axis of rotation (15) coupled to it rolling body (18) or arcuate body (18) on a shaft (28) are arranged, which the coupling causes. 7. Engine according to one of the preceding claims, wherein the respective piston (16) in a respective piston chamber (42) is accommodated, and a piston rod (40) via which the piston (16) with the respective roller (14) or the respective sliding body is connected, through an opening in the bottom (46) of the piston chamber (42),  the motor further comprising a cooling medium supply means (80), the piston chamber (42) having a supply port (82) connectable to the supply means (80) for supplying the cooling medium, and a discharge port (84) for discharging the cooling medium, and wherein the supply port (82) and the discharge port (84) are arranged so that they are connectable to a piston back-side portion of the piston chamber (42) at least in a front position of the piston (16). 8. Motor according to one of the preceding claims, wherein the respective piston (16) in a respective piston chamber (42) is accommodated and at its periphery at a distance from a surrounding side wall (44) of the piston chamber (42) is arranged. 9. Engine according to claim 8, wherein the motor at the periphery of the respective piston (16) between the piston (16) and side wall (44) of the piston chamber (42) has a gap with a labyrinth (56) comprising at least one piston groove. 10. Motor according to one of the preceding claims, with a outside of a wall of the piston chamber (44) arranged heat-insulating layer (58). An engine as claimed in any preceding claim, including at least one supply means (60; 64) for supplying a fuel and an evaporation medium from separate reservoirs (62; 66) into a combustion chamber (52) within the piston chamber (42) through the side wall (44) of the piston chamber, the front of the piston (16) and an opposite head wall (48) of the piston chamber is limited. 12. Engine according to one of claims 1 to 11, with at least one first lifting element in the form of a first piston (16), at least one second lifting element in the form of a second piston (16 ') and at least a first and a second gear (10) for Coupling a reciprocating motion of a respective piston (16, 16 ') with a rotational movement of a respective double cam cam (12) of the respective transmission (10), wherein the transmission (10) respectively the features of the transmission (10) of the motor after the respective one of claims 1 to 9, and wherein the double cam cams (12) of the transmission (10) via a common shaft (12A) are coupled together, wherein a first piston (16) and a second piston (16 ') thereto are arranged to perform reciprocating movements in mutually parallel directions offset in time.