DE102010046621A1 - Opposed-piston engine e.g. four-stroke petrol engine, for vehicle i.e. hydraulically-propelled vehicle, has valve arranged in housing region and movable from housing region into axially limited side zones of combustion chamber - Google Patents

Abstract

The engine has an engine cylinder whose cylinder portions (Z1, Z2) are displaced relative to each other in a circumferential direction of a pitch circle. A combustion chamber (ZB) comprises engine pistons (K1, K2) arranged in the cylinder portions. The cylinder portions are surrounded by laterally adjacent housing regions. A valve (VT) of a valve controller (V) is arranged in the housing regions and movable from the housing region into axially limited side zones of the combustion chamber. The side zones are arranged on sides of an axial intersection zone of the cylinder portions.

Description

The invention relates to an opposed piston internal combustion engine having a plurality of arranged on a common pitch motor cylinders, in each of which a first engine piston and a second piston engine are longitudinally movable in opposite directions, which axially limit a volume variable combustion chamber and are in operative connection with a rotor assembly, which concentric to a partial circle and to the engine cylinders axially parallel axis of rotation, wherein the first engine piston is disposed in a first axial cylinder portion of the engine cylinder and the second engine piston is arranged in a subsequent to the first cylinder portion, the second axial cylinder portion of the engine cylinder and wherein the gas exchange in the combustion chamber, a valve control is provided ,

Opposed piston internal combustion engines with a rotation axis of the rotor assembly that is concentric to the engine cylinders and axis-parallel, d. H. with a circular arrangement of the engine cylinders, belong to the group of axial piston internal combustion engines, which can be referred to as "drum motors" due to arranged on a common pitch circle engine cylinder. Opposed piston internal combustion engines do not have a cylinder head. This results in a simple structure. Furthermore, the piston stroke of the opposed piston internal combustion engine is halved by the two-row structure with two groups of engine pistons in a cylinder chamber of equal size compared to single-row axial piston internal combustion engines. Each of the two engine pistons moving towards and away from each other only has to travel halfway. Accordingly, lower piston speeds and reduced material stress result.

Opposing piston internal combustion engines can provide the power generated in the form of shaft power, which can be tapped on a drive shaft. From the cited to the printed prior art DE 28 20 552 A1 is an application known in which not only shaft power but also hydraulic power is provided. For this purpose, the engine pistons of at least one of the piston groups via a tilting disc ("swash plate") are coupled with positive displacement piston of a positive displacement pump ( 5 the cited document). This known opposed piston internal combustion engine whose dimensions in the axial direction both in a design with only one positive displacement pump and in a design with two positive displacement pumps ( 4 the cited document) are determined by the positive displacement pump (s), works according to the two-stroke process, wherein a slot control is provided for gas exchange.

It is also already known to provide opposed piston internal combustion engines with a valve control for the gas exchange, in particular to allow operation after the four-stroke cycle. So is a generic opposed piston internal combustion engine in the DE 1 906 171 A1 disclosed, which is operated in contrast to a two-stroke engine with slot control realized opposed piston internal combustion engine in the four-stroke process and is provided for this purpose with a valve disposed in the radially outer region valve control.

The present invention is based on the object to provide an opposed piston engine of the type mentioned above, which claimed a smaller space with a simple design.

This object is achieved in that the cylinder sections of each engine cylinder are offset in the circumferential direction of the pitch circle to each other, each of the combustion chamber - seen in cross section through the piston engine - an axially limited by the engine piston overlap zone of the two cylinder sections and two in the circumferential direction of the pitch circle on both sides Side zones adjoining the overlapping zone, each associated with one of the cylinder sections and axially delimited by the engine piston arranged in this cylinder section and by a housing section laterally adjacent to the opposite cylinder section, at least one valve of the valve control being arranged in at least one of the two housing sections the housing region axially limited side zone of the combustion chamber is movable into it.

The idea essential to the invention therefore consists of not executing each engine cylinder as a continuous axial bore, as is known from the prior art, but to form axially offset and overlapping axial bore portions in the circumferential direction of the pitch circle, in which case laterally to the cylinder sections of the engine cylinder produced in this way the valves of the valve control are arranged. As a result, the space required in the radial direction compared to the known from the prior art and provided with a radially outwardly arranged valve control, generic opposed piston internal combustion engine significantly reduced. Rather, the valve control is located within a machine area where only the engine cylinders (and the engine piston longitudinally movable therein) are located in the prior art opposed piston internal combustion engine of the prior art. The opposed piston internal combustion engine according to the invention, the axial cylinder sections and thus also the piston groups in the circumferential direction to each other are particularly suitable for operation as a four-stroke gasoline engine or as a four-stroke diesel engine. However, in principle, an operation with other combustion methods is conceivable in which a valve control is used.

If in each case two side valves of a combustion chamber are assigned two valves, a four-valve control results, whereby a high gas throughput can be achieved, which enables a correspondingly high output of the piston engine.

In principle, it is also within the scope of the invention, when the cylinder sections are not offset from each other exclusively in the circumferential direction of the pitch circle but also radially to the rotational axis of the rotor assembly, d. h., outward or inward.

In an advantageous embodiment of the invention, the valves are actuated by radially or approximately radially to the axis of rotation of the rotor assembly tilting lever and is provided by the rotor assembly drivable, to the axis of rotation coaxial cam rotor, which is in operative connection with the inner ends of the rocker arm.

It is expedient according to an embodiment of the invention, when the cam rotor has a first and an axially adjacent, second cam rotor sleeve, which are provided with frontal axial cam for actuating a group of rocker arms and driven by a hollow shaft of the rotor assembly, wherein in the power flow between the hollow shaft and the cam rotor sleeves reduction gear are connected. The reduction gears provide a speed bisection with respect to the speed of the rotor assembly, whereby the opposed piston internal combustion engine can be operated in the four-stroke process.

It proves to be advantageous if a first lifting disk designed as a swashplate is assigned to the first engine piston and a second lifting disk designed as a swashplate is the second engine piston, whereby the lifting disks are components of the rotor assembly and are in operative connection with the engine pistons by means of sliding bodies, in particular hydrostatically relieved sliding bodies stand.

The lifting discs designed as swash plates ensure the conversion of the lifting movement of the engine pistons into a rotational movement of the rotor assembly and vice versa. Due to the design with sliding bodies, this results in a functionally reliable, smooth-running operative connection between the engine piston and the rotor assembly, on the one hand, and lateral forces resulting from the force separation at the lifting disks, on the other hand, can be introduced into the engine cylinders. The engine pistons are guided and supported laterally and tangentially by the associated axial cylinder sections of the engine cylinders.

The use of lifting discs in the opposed piston internal combustion engine according to the invention also makes it possible in a simple manner, in spite of the phase offset of the group of the first engine piston to the group of second engine pistons in the circumferential direction to synchronize the strokes of the mutually opposed engine pistons. For this purpose, the lifting discs are also out of phase in the circumferential direction. The arranged inside of an engine cylinder engine pistons thus move simultaneously towards and away from each other, so there is no engine piston ahead.

With regard to use of the opposed piston engine according to the invention for driving a hydraulic pump (generation of hydraulic power), it is particularly advantageous if the first and / or the second engine pistons are each connected to a hydraulic displacement piston and respectively the strokes of the engine piston in the cylinder portion of the engine cylinder and connected to the engine piston, in a displacer longitudinally movable displacement piston are equal in movement and correlate directly to each other, wherein the displacer is at least partially disposed within the engine piston.

An embodiment is preferred in which both the first engine pistons and the second engine pistons are each connected to a hydraulic displacement piston. As a result, an opposed piston internal combustion engine with two integrated hydraulic displacement pumps is formed, which can be used in many applications. Thus, it is possible to use such a reciprocating internal combustion engine for driving a vehicle, which is provided with a hydrostatic drive. Here, one of the positive displacement pumps can be assigned to the traction drive in a closed circuit, while the other positive displacement pump in the open circuit serves to drive a working hydraulics. However, it is also possible for both positive-displacement pumps to be assigned to a hydrostatic travel drive, for example in the case of a caterpillar drive, in which each positive-displacement pump is integrated in a closed hydrostatic circuit. Here each cycle drives one of the two tracks. It is also possible, if necessary, to hydraulically interconnect the two positive displacement pumps.

The integration according to the invention of at least one positive displacement pump into the opposed piston internal combustion engine does not only result in a Space requirement, which is considerably lower than in the aforementioned opposed piston internal combustion engine with arranged behind the tilting disc displacement pump, but also an improved efficiency. Since the strokes of the engine pistons and the displacer are identical in movement and correlate to each other, each expansion movement of a motor piston with an equal and pointing in the same direction of movement compression movement of the associated displacer associated. Conversely, each compression movement of an engine piston corresponds to an expansion movement of the displacer piston of the same size and pointing in the same direction of movement. The strokes of the engine piston and the displacer are in opposite directions with respect to their function in the engine cylinder or displacer - expansion or compression - in opposite directions. The force generated from the combustion process in the engine cylinder and acting on the engine piston is introduced without conversion into other forms of movement (eg rotational movement) and consequently with the lowest possible losses and with a maximum efficiency directly (ie without intermediate components) in the displacer and in the sequence Pressure medium displaced and generates a hydraulic pressure.

Thus, an energy conversion of combustion energy into hydraulic energy takes place, in which there is, in principle, a linear flux of force between the engine piston and displacer piston. In doing so, hydraulic power is generated directly. The stroke of the associated piston group has the task to match the strokes of the associated engine pistons to each other, to transfer the forces required for the compression of the engine pistons (and the four-stroke process and the necessary for the discharge of combustion gases in an exhaust collector forces applied) and mechanical power To transmit to a drive shaft to drive by means of shaft power, the valve control and possibly ancillaries (in this context, it is also possible to drive by the opposed piston internal combustion engine another, eg flanged positive displacement pump). It is therefore necessary to be able to pick up a certain proportion of the total power provided by the opposed piston internal combustion engine in the form of mechanical power, in particular shaft power.

The displacers and the displacer cylinders are preferably arranged radially outside of the sliding body position with respect to the radial distance to the axis of rotation of the rotor assembly. This makes it possible to keep the diameter of the lifting discs low, which is favorable in terms of high speeds, because due to the small Hubscheibendurchmessers gentle sliding velocities are achieved in the operative connection between the engine piston and the Hubscheiben.

For the pressure medium supply of the displacement cylinder, d. H. for the control of the positive displacement pump, so the type of reversal between the pressure and suction side, known from the prior art principles are used. So probably the simplest type of reversal is to provide per displacement cylinder in each case two oppositely acting check valves. A control by rotation of the displacement piston (from row injection pumps for fuel injection in diesel engines known) is possible.

In a preferred embodiment of the invention, at least one drivable by the rotor assembly flat rotary valve is provided for controlling the pressure medium supply of the displacer cylinder. This rotary control level is suitable for both open and closed hydraulic circuits.

Nevertheless, a no less favorable variant is also possible according to which a longitudinal slide valve is hydraulically connected to each positive displacement cylinder for controlling the pressure medium supply of the displacement cylinder, wherein at least one of the rotor assembly drivable control rotor is provided for actuating the longitudinal slide valves. For a high reliability and space reasons, the longitudinal slide valves are preferably arranged radially to the axis of rotation and the control rotor is coaxial with the axis of rotation.

When working on the four-stroke principle (gasoline or diesel) reciprocating internal combustion engine is to be noted that only every second expansion stroke of the engine piston is a power stroke, in each case the performance of the engine piston on the associated displacement piston of the positive displacement pump as a pressure-generating and thus work verrichtender Compression stroke (power stroke) of the displacer is transmitted.

To take this fact into account, according to a particularly simple design of the opposed piston internal combustion engine is provided that the individual, each consisting of a displacer and a displacer hydraulic working units in their recording power only to a maximum of half in the power output expansion stroke of the engine piston of the opposed piston internal combustion engine piston power available the engine pistons are designed. It is then possible, in spite of the four-stroke process of the reciprocating internal combustion engine, to control the displacement pump (s) according to the two-stroke principle, ie each compression stroke of the displacement piston is a working stroke in which Pressure medium is promoted to a hydraulic consumer and there work. Each engine piston located in the expansion stroke delivers only half of its available piston output to the displacer directly connected to it. The other half of the piston power of the engine piston is transmitted via the lifting disc to those displacement piston whose engine pistons are not in the phase of the expansion stroke.

In this respect, this is therefore an internal power split in the engine piston.

In order to allow for the best possible efficiency, a design of the reciprocating internal combustion engine in which each engine piston of the reciprocating internal combustion engine during expansion stroke a maximum portion of the piston power can be transferred to the associated displacer, it makes sense to form the reversal of the displacer according to the four-stroke principle, so for it to ensure that each displacer performs work only on every second compression stroke, while the compression strokes in between promote the pressure medium largely unpressurized in the tank or to the suction side of the displacer currently located in the suction stroke and thus represent no strokes.

In the case of the reversal by longitudinal slide valves, which are actuated by control cam of a control rotor, this can be easily achieved in a favorable embodiment of the invention by a reduction gear in the power flow between the rotor assembly and the control rotor.

In particular, with a relatively low number of engine cylinders or engine pistons of the operating according to the four-stroke principle reciprocating internal combustion engine and controlled by the four-stroke principle positive displacement pump (s), it may be useful to smooth out pulsations of the hydraulic flow of the positive displacement pump (s) to provide appropriate measures, eg. As hydraulic storage or Tilgerräume.

For many applications, it is desirable if the flow rate of the positive displacement pump (s) can be adjusted and regulated. In this context, according to an expedient embodiment of the invention, it is provided that the control rotor is axially movable and has a lateral surface which is provided with conical cams - seen in longitudinal section of the control rotor - in operative connection with the longitudinal slide valves, the longitudinal slide valves being radial to the axis of rotation the rotor assembly are arranged. This solution with radially acting control cams is suitable both for reversed according to the two-stroke principle as well as for the four-stroke principle positive displacement.

According to an alternative embodiment of the invention, which is provided for reciprocating internal combustion engines with positive displacement pumps reversed according to the two-stroke principle, an adjustability and controllability of the displacement of the positive displacement pump (s) is achieved in that at least one in the stroke volume adjustable, with the Rotorbaugrupppe mechanically in driving connection or movable superposition pump whose flow is reversible and variable, in particular adjustable and reversible axial piston pump in swash plate design, hydraulically connected or connectable with the displacement cylinders. By superimposing the delivery flow or the delivery flows of the displacement pump (s), which is integrated into the opposed piston internal combustion engine and can not be adjusted in the specific delivery volume (i.e., in the delivery volume per revolution) with the reversible and controllable delivery flow of the superimposition pump (s), a total variable delivery volume results.

If according to a particularly advantageous development of this embodiment of the invention, a switchable coupling is arranged in the power flow between the rotor assembly and the at least one overlay pump, the overlay pump is in drive connection with an electric machine designed in particular as a flywheel starter generator and the hydraulic connection between the displacement cylinders and the superposition pump can be shut off by a switchable valve device, the opposed piston internal combustion engine can be decoupled from the superposition pump and turned off.

It is then possible in the presence of a sufficiently large electrical energy storage device (eg battery or capacitor) and sufficient filling with electrical energy to electrically operate the superposition pump (s) without parallel operation of the positive displacement pump (s), for example one with the According to the invention, reciprocating internal combustion engine equipped, hydraulically powered vehicle to drive temporarily electrically. In the blocking position, the switchable valve device ensures that, in addition to the mechanical decoupling of the opposed piston internal combustion engine, the positive displacement pump (s) is / are hydraulically decoupled from the overlay pump (s), and thus the opposed piston internal combustion engine does not start unintentionally.

Independently of this, a hydraulic energy store, ie a pressure accumulator, can be present in which kinetic energy can be fed in when the vehicle is decelerating. This recovered braking energy can both in purely internal combustion engine-hydraulic driving operation and - when the clutch is released - be used in purely electro-hydraulic driving to accelerate the vehicle. Moreover, when the clutch is closed, it is also possible to interconnect all three types of energy, ie combustion engine energy, energy from the hydraulic pressure accumulator and energy from the electrical accumulator, for a short time and depending on the filling states of the electrical and hydraulic energy accumulators during acceleration of the vehicle to achieve a maximum booster effect.

Further advantages and details of the invention will be explained in more detail with reference to the embodiments illustrated in the schematic figures. It shows

1 a longitudinal section through an opposed piston internal combustion engine according to the invention,

2 a partial development of the piston engine in the area of the combustion chambers,

3 a partial cross section through the opposed piston internal combustion engine in the field of valve timing and

4 a longitudinal section through a variant of the opposed piston internal combustion engine.

The opposed piston internal combustion engine according to the invention has a machine housing G, in which several, on a pitch circle ZK (see 3 ) are arranged over the circumference preferably evenly distributed, housing-fixed motor cylinder Z are. In each engine cylinder Z, a first engine piston K1 and a second engine piston K2 are arranged longitudinally movable. The first engine piston K1 is located in a first axial cylinder section Z1 of the engine cylinder Z and belongs to a first piston group which is associated with a first, designed as a swash plate and with the engine piston K1 operatively connected to the lifting plate T1 rotor assembly. Similarly, the second engine piston K2, which is located in a second axial cylinder section Z2 of the engine cylinder Z, to a second piston group, which is associated with a second, also designed as a swash plate and operatively connected to the engine piston K2 stroke disk T2 of the rotor assembly.

The lifting discs T1, T2 are integrally formed on rotor bodies RK1, RK2 of the rotor assembly. The rotor assembly further includes as an integral part a hollow shaft WH connected to the rotor bodies RK1, RK2, which is capable of absorbing longitudinal forces and bending forces. The rotor assembly is centrally disposed within the opposed piston internal combustion engine and rotatably supported by means arranged in the region of the rotor body RK1, RK2 bearings about a to the motor cylinders Z axis parallel and the pitch circle ZK concentric axis of rotation D in the machine housing G.

Due to the design of the opposed piston internal combustion engine, the axial forces are substantially balanced ("Axialkraftkompensation") and remain within the connected to the rotor bodies RK1, RK2 hollow shaft WH. So there are no large axial forces that would have to be absorbed by the bearing of the rotor assembly. The bearing of the rotor assembly can therefore be relatively small dimensions.

The engine pistons K1, K2 respectively engage around the hub-side end of the associated Hubscheibe T1 and T2. In this case, a spherical-segment-shaped, hydrostatically relieved sliding body KG is arranged between the engine piston K1 or K2 and the lifting disk T1 or T2 on the front side and on the rear side of the lifting disk T1 or T2. Thus, the engine pistons K1, K2 are in sliding engagement with the lifting disk T1 or T2. The fact that the oblique to the rotation axis D lifting discs T1 and T2 are rotationally offset from each other by 180, respectively, the engine pistons Z arranged in an engine cylinder K1 and K2 move in opposite directions to or away from each other.

Axially between the engine pistons K1 and K2, a combustion chamber ZB is formed in each engine cylinder Z. The resulting by the combustion process in the combustion chamber ZB strokes of the engine pistons K1 and K2 generate due to the geometric conditions in the decomposition of the axially directed piston forces torques, which cause a rotational movement of the Hubscheiben T1 and T2 and thus the rotor body RK1, RK2 of the rotor assembly about the axis of rotation D. , As a result, the engine pistons K1, K2 located in the expansion stroke can transmit drive power to those engine pistons K1, K2 via the lifting disks T1, T2 and the rotor bodies RK1, RK2, which are located in the compression stroke or in the exhaust stroke. Furthermore, can be tapped by the rotor assembly to be described valve timing V of the opposed piston internal combustion engine and beyond mechanical shaft power at a arranged within the hollow shaft WH drive shaft WT can be tapped.

In order to prevent the engine pistons K1, K2 from rotating about their piston center axis (avoiding self-rotation of the engine pistons K1, K2), each engine piston K can be provided with an axial groove in which a radial pin mounted in the engine housing G engages (in the drawings not shown). That way is one Piston rotation formed. Other types of anti-rotation are conceivable.

As it turned out 2 which represents a partial development of the piston engine, the respective axial cylinder sections Z1 and Z2 of each engine cylinder Z assigned to one of the engine pistons K1 and K2 are offset relative to one another in the circumferential direction of the pitch circle ZK. The engine cylinders Z are therefore not designed as continuous axial bores, as is known from the prior art, but consist of longitudinal bores offset from one another in the circumferential direction of the pitch circle ZK and only partially overlapping, each forming one of the axial cylinder sections Z1 and Z2.

In this case, the combustion chamber ZB, which is arranged axially between the engine pistons K1 and K2, is seen in cross-section through the opposed piston internal combustion engine (see FIG 3 ) - an overlap zone ZBU of the two cylinder sections Z1, Z2 and two in the circumferential direction of the pitch circle ZK on both sides of the overlap zone ZBU subsequent side zones ZB1 and ZB2, which are each associated with one of the cylinder sections Z1 and Z2.

The overlapping zone ZBU is limited at the axial ends by the two engine pistons K1, K2 (see 2 ). The side zone ZB1 is bounded axially at one end by the motor piston K1 arranged in the first cylinder section Z1 and at the opposite end by a housing section GV2, which is laterally adjacent to the opposite second cylinder section Z2. The side zone ZB2 is bounded axially at one end by the motor piston K2 arranged in the second cylinder section Z2 and at the opposite end by a housing section GV1 laterally adjacent to the opposite first cylinder section Z1.

In the housing areas GV1, GV2, which are laterally adjacent to the cylinder sections Z1, Z2, there is sufficient space for the arrangement of plate-shaped or mushroom-shaped valves VT of a valve control V. The valves VT are in the axially bounded by housing areas GV2, GV1 Side zones ZB1, ZB2 of the combustion chamber ZB axially movable into it (see 2 ). A deviating from the axial direction, inclined arrangement of the valves VT is possible in principle, if space permits. The valves VT are controlled so that the valve movement is tuned to the piston movement, ie, the valves VT move into the space that the engine pistons K1, K2 release during expansion or suction. The valves VT, which is arranged in the side region ZB1 of the combustion chamber ZB limiting housing portion GV2, move into the cylinder portion Z1 in and out again. The valves VT, which are arranged in the side zone ZB2 of the combustion chamber ZB limiting housing portion GV1, move into the cylinder portion Z2 in and out again.

In the present exemplary embodiment, each side zone ZB1 or ZB2 of a combustion chamber ZB is assigned in each case two valves VT (see FIG 3 ). This arrangement represents a four-valve control for each combustion chamber ZB. Here, the radially inner valves VT serve as intake valves and the radially outer valves VT as exhaust valves. In the housing areas GV1, GV2 may also injection nozzles VE are located and possibly spark plugs. With regard to the best possible mixing in the combustion gas and optimum combustion, an embodiment is preferred in which an injection nozzle is arranged in each housing region GV1, GV2. Analogously, a spark plug can also be arranged in each housing region GV1, GV2.

The valves VT can be actuated by rocker arms VK arranged radially or approximately radially relative to the axis of rotation D of the rotor assembly R. Since the valves VT arranged laterally adjacent to the first cylinder section Z1 in the housing area GV1 move opposite to the valves VT arranged laterally adjacent to the second cylinder section Z2 in the housing area GV2, there are two groups of valves. Accordingly, there are also two groups of rocker arms VK which are driven by a cam rotor VN coaxial with the axis of rotation D of the rotor assembly. For assembly reasons, the cam rotor VN has a first cam rotor sleeve VN1 and an axially adjacent second cam rotor sleeve VN2. The two cam rotor sleeves VN1, VN2 are provided on the end faces, which face the rocker arms VK, with axial cams VNA, which are in operative connection with the radially inner ends of the rocker arms VK.

Since the opposed piston internal combustion engine is operated according to the four-stroke cycle in the present embodiment, each cam rotor sleeve VN1 or VN2 is preceded by a first or second reduction gear VU1 or VU2 which can be driven by the rotor assembly and provides a speed bisection with respect to the rotational speed of the rotor assembly. The structure of the reduction gear VU1 or VU2 results from the synopsis of 1 and 3 : The rotor bodies RK1, RK2 of the rotor assembly are non-interruption-free (here: via splines) connected to the hollow shaft WH. The hollow shaft WH meshes with input side spur gears VUE of the reduction gear VU1, VU2, the output side spur gears VUA each have a hollow toothing drive the cam rotor sleeve VN1 or VN2. The cam rotor sleeves VN1, VN2 rotate synchronously.

Spatially within the engine piston K1 of the first piston group (see 1 ) In each case a displacement piston PK1 is arranged in the axis-parallel alignment, which is connected within the engine piston K1 with this and longitudinally movable in a displacement cylinder PZ1. The hydraulic units of the group of the first engine pistons K1, each consisting of a displacement cylinder PZ1 and a displacement piston PK1 disposed therein, together form a first displacement pump. Similarly, spatially within the engine piston K2 of the second piston group in axially parallel alignment in each case a displacer PK2 is arranged, which is connected within the engine piston K2 with this and longitudinally movable in a displacer cylinder PZ2. The hydraulic units of the group of the second engine pistons K2, each consisting of a displacement cylinder PZ2 and a displacement piston PK2 disposed therein, together form a second displacement pump.

The displacers PK1, PK2 are located radially in relation to the radial distance to the axis of rotation D within the position of the sliding body KG. The displacer cylinders PZ1 are connected to or integrally formed with a base plate PG1 forming an axial end cover of the machine housing G, and the displacer cylinders PZ2 are connected or integrally formed with a base plate PG2 having an axial end cover of the machine housing G disposed at the other end of the opposed piston internal combustion engine forms.

The displacement cylinders PZ1 and PZ2 are largely integrated into the engine pistons K1 and K2 (completely integrated in the radial direction to the axis of rotation D, completely integrated in the axial direction with the engine pistons K1 and K2 located at bottom dead center). As a result of the axis-parallel arrangement of the displacer PK1 or PK2 and the direct connection between engine pistons K1 and K2 and displacer PK1 and PK2 correlate the same movements strokes of the engine piston K1 and K2 and the displacer PK1 or PK2 each other, d. H. With each stroke movement of the engine piston K1 or K2 in the respective cylinder section Z1 or Z2 of the engine cylinder Z, there is an equally large stroke movement of the displacer PK1 or PK2 in the displacer cylinder PZ1 or PZ2 pointing in the same direction of movement. The opposing to the displacement cylinder PZ1 or PZ2 arranged end of the displacement piston PK1 or PK2 is hingedly connected to the engine piston K1 and K2 on the piston head to compensate for a zwängungsfreien operation even with any parallelism or misalignment.

Axially directed forces generated by the combustion process in the combustion chamber ZB of the engine cylinder Z and acting on the engine pistons K1 and K2 can be directly and directly introduced into the displacer PK1 or PK2, ie without the detour via a crankshaft or the lifting disks T1 and T2 ,

The base plate PG1 connected to the displacement cylinders PZ1 is provided with passage channels, with the aid of which the displacement cylinders PZ1 are connected to an axial control surface PS1 provided for reversing between the suction and pressure sides of the first displacement pump. Similarly, the associated with the displacement cylinders PZ2 base plate PG2 is provided with through channels, by means of which the displacement cylinder PZ2 are connected to a provided for reversal between suction and pressure side of the second positive displacement pump, axial control surface PS2.

The control surface PS1 is formed on a rotatably connected to the rotor assembly structure, which thus in principle represents a rotating flat rotary valve RF1, which connects the displacement cylinder PZ1 with a suction channel AS1 and with a pressure channel AD1. The said channels are incorporated in the already mentioned base plate PG1. In the same way, the control surface PS2 is formed on a rotationally synchronous with the rotor assembly associated structure, which thus in principle represents a rotating rotary vane rotary valve RF2, which connects the displacement cylinder PZ2 with a suction channel AS2 and with a pressure channel AD2. The said channels are incorporated in the already mentioned base plate PG2.

In the pressure channel AD1 is a valve device ADV1, with the aid of which the direction of the flow of the first positive displacement pump can be reversed. But there are also applications possible in which for direction reversal an existing, arranged outside the opposed piston internal combustion engine valve device can be used. A valve device ADV1 arranged inside the opposed piston internal combustion engine is then not required. Analogously, there is a valve device ADV2 in the pressure channel AD2, with the aid of which the direction of the flow rate of the second positive displacement pump can be reversed. Again, however, a directional reversal could be carried out with a valve device arranged outside the opposed piston internal combustion engine, and the valve device ADV2 could be dispensed with.

For the aforementioned hydrostatic discharge and lubrication of the sliding body KG these are stored in Gleitkörperaufnahmen of the engine piston K1 or K2, in which piston side Open lubricant channels KS, which are connected to the displacer cylinder PZ1 or PZ2 connected to the engine piston K1 and K2 displacement piston PK1 or PK2 (via holes in the displacer). Furthermore, the sliding bodies KG are provided with a lubricant bore opening on the lifting disk surface (not shown). The arranged on the back of the lifting plate T1 and T2 slider KG each engine piston K1 or K2 has a pressure pocket in which a pressurized shim KGS ensures that wear is compensated and always functionally reliable engagement conditions between engine pistons K1 and K2, sliding bodies KG and Hubscheibe T1 and T2 are present.

The opposed piston internal combustion engine shown in the embodiments operates on the four-stroke principle. This means that only at every second expansion stroke of the engine piston K1, K2 piston power can be transmitted directly to the associated displacement piston PK1 or PK2 of the first and second displacement pump. Since the means of flat rotary valve RF1 or RF2 (rotating control surface PS1 or PS2) effected reversal between suction and pressure side of the integrated piston in the piston internal positive displacement pump works on the two-stroke principle, however, each compression stroke of the displacer PK1, PK2 is a working stroke, wherein the pressure medium in the pressure channel AD1 or AD2 is promoted. Therefore, a compensation is required here.

For this reason, it is possible in the simplest case that the displacement pumps are each designed so that each of the displacement piston PK1 or PK2 only half of the piston piston K1 or K2 respectively discharged directly from the respective directly connected engine piston K1 or K2 during an expansion stroke K2 takes up. The other half of the piston power of the engine piston K1 or K2 is transmitted via the lifting plate T1 and T2 mechanically to the displacer PK1 or PK2 those engine pistons K1 and K2, which is not in the phase of the expansion stroke but the intake stroke (aspiration of fresh Fuel gases are) and therefore can not deliver any piston power to the respective associated displacer PK1 or PK2. However, these other displacement pistons PK1 and PK2 also perform a pressure-generating stroke due to acting on the two-stroke principle control of positive displacement and get the required drive power through the lifting plate T1 and T2. The mechanical transmission of 50% of the piston power of each engine piston K1 or K2 via the lifting disk T1 or T2 (internal power split in the engine piston K1 or K2) is unproblematic due to the short transmission paths.

In the rotor body RK2 the rotor assembly, a clutch cage of a clutch C is formed or fixed. In the clutch cage are acted upon by spring force in the closed position, hydraulically disengageable slats CL, which are alternately rotatably connected to the clutch cage (ie with the rotor body RK2) and with the axis of rotation D arranged within the hollow shaft WH drive shaft WT (here: under Interposition of a hollow intermediate shaft WZ).

The drive shaft WT is connected to the cylinder blocks of two preferably designed as adjustable and reversible axial piston pumps in swashplate design overlay pumps U1 and U2 and a rotor ER preferably designed as a flywheel starter generator electric machine E. The adjacent to the base plate PG2 electric machine E united in a single unit, the functions flywheel of the opposed piston internal combustion engine, generator and electric motor, which is also used as a starter device for the opposed piston internal combustion engine. The first superposition pump U1 is located inside the first rotor body RK1. The second overlay pump U2 is spatially integrated in the base plate PG2 and the electric machine E.

With the help of each designed as adjustable and reversible axial piston pump in swash plate design overlay pumps U1, U2, the flow rates of the two integrated in the opposed piston internal combustion engine positive displacement pumps can be controlled (addition / subtraction of the flow rates of the positive displacement pumps and superposition pumps). The first superposition pump U1 is arranged for this purpose between the suction side and pressure side of the integrated in the piston internal combustion engine first positive displacement pump in hydraulic parallel connection, wherein in the suction AS1 valve means ASV1 is arranged, which ensures in normal operation that the suction side of the first superposition pump U1 both to the Suction channel AS1 as well as to the pressure side of the first positive displacement pump is connected. Analogously, the second superposition pump U2 between the suction and pressure side of the integrated in the opposed piston internal combustion engine second positive displacement pump is arranged in hydraulic parallel connection, wherein in the suction AS2 valve means ASV2 is arranged, which ensures in normal operation that the suction side of the second superposition pump U2 both to the Suction channel AS2 as well as to the pressure side of the second positive displacement pump is connected

The valve devices ASV1, ASV2 can each in a certain switching position, the connection between the superposition pump U1 and Disconnect U2 and the assigned positive displacement pump. This interruption is required when the clutch C is opened to stop the opposed piston internal combustion engine and to provide hydraulic power with the aid of the electric machine E and the superimposed pumps U1, U2 mechanically connected thereto, consisting of a power connected to the electric machine E, is fed in the figures, not shown energy storage. In this case, it is prevented by the valve device ASV1, ASV2 that the superimposed pumps U1, U2 act on the displacement pumps with pressure medium and thereby start the counter-piston internal combustion engine electro-hydraulically.

For the lubrication of sliding and running partners of the reciprocating internal combustion engine by targeted spray oil and for the operation of the switchable clutch C (opening the clutch C) designed as a gear or gerotor pump, hydraulic auxiliary pump PH is provided which also for the oil extraction from the machine housing G can be used. The auxiliary pump PH, which is integrated in the base plate PG1 and can be driven by the drive shaft WT, can also be used to build up hydrostatic relief fields within the superposition pumps U1, U2. Thus, even then hydrostatic relief pressure is available when the superposition pumps U1, U2 are set to zero delivery volume and therefore promote no pressure oil.

In the embodiment of the opposed piston internal combustion engine according to the invention 4 the control of the two integrated displacement pumps is not done by means of flat rotary valves, but it is now each of the displacement cylinder PZ1, PZ2 each one arranged radially to the rotational axis D in the base plate PG1 and PG2 longitudinal slide valve PV hydraulically connected downstream. The longitudinal slide valves PV of the displacement cylinder PZ1 of the first positive displacement pump are controllable by a first control rotor RS1 and connect with appropriate actuation of the associated valve spool by the radial control cam of the first control rotor RS1 each positive displacement cylinder PZ1 the first positive displacement alternately with a connected to the suction port AS1, suction side collecting Ring channel ASR1 and connected to the pressure channel AD1, the pressure-side collecting ring channel ADR1 (control according to the two-stroke principle). In the same way, the longitudinal slide valves PV of the displacement cylinder PZ2 of the second positive displacement pump are controllable by a second control rotor RS2 and connect with appropriate actuation of the associated valve spool by the control cam of the second control rotor RS2 each displacement cylinder PZ2 the second positive displacement alternately with a suction connected to the suction port AS2, suction side Collective ring channel ASR2 and a pressure-side collective ring channel ADR2 (control according to the two-stroke principle) connected to the pressure channel AD2.

Overlay pumps are not provided in this embodiment. Furthermore, there is also no clutch with which the connection between the electric machine E and the opposed piston internal combustion engine can be interrupted. Rather, instead of a one-piece drive shaft WT, two separate stub shafts WT1, WT2 are provided, of which one stub WT2 is coupled to the rotor ER of the electric machine E and the second control rotor RS2 and connected directly - ie without a coupling - to the hollow shaft WH of the rotor assembly , The second stub WT2 is also directly connected to the hollow shaft WH and serves only to drive the first control rotor RS1. The drive shaft thus consists of the two stub shafts WT1, WT2 and the hollow shaft WH.

In order to be able to control or regulate the flow rate of the positive displacement internal combustion engine positive displacement pump despite lack of superposition pumps, the control rotors RS1, RS2 axially movable and each have a lateral surface RSM1 and RSM2, which is provided with conical control cam, with which the longitudinal slide valves PV can be actuated. In an axial displacement of the control rotor RS1 or RS2, which can be caused by a suitable control or regulating device, the stroke of the valve spool of the longitudinal slide valve PV of the associated positive displacement pump and thus their intake and delivery is changed. The control rotors RS1, RS2 are each in the form of a sleeve and mounted on the shaft stubs WT1, WT2 designed as a control rotor carrier in a rotationally fixed manner relative thereto, but displaceable counter to spring force along the axis of rotation D by hydraulic control pressure. In the figure, one side of the control rotor RS1 and RS2 in the axially displaced state and maximum stroke of the valve spool of a longitudinal slide valve PV is shown (section through the control cam) and the other side in the axially non-displaced state and minimum travel of the valve spool of a longitudinal slide valve PV.

In an embodiment, not shown, it is possible by means of between the stub shaft WT1, WT2 and the control rotor carrier or control rotors RS1, RS2 connected reduction gear with reduction 2: 1 ensure that the positive displacement pumps are controlled by the four-stroke principle, ie only each second compression stroke of the displacement piston PK is then a pressure-generating working stroke. During the stroke between two working strokes, however, is a connection to Suction side made. Through this control of the positive displacement pump according to the four-stroke principle, it is possible to convert the piston output of the engine piston K1 or K2 to the greatest extent possible into hydraulic power of the displacer piston PK in the case of a power stroke of the displacer piston PK1 or PK2 running synchronously with the power output stroke of the engine piston K of the piston engine.

List of reference numbers used:

• AD1

  Pressure channel of the first positive displacement pump

  AD2

  Pressure channel of the second positive displacement pump

  ADR1

  pressure-side collecting ring channel of the first positive displacement pump

  ADR2

  pressure-side collecting ring channel of the second positive displacement pump

  ADV1

  Valve device in the pressure channel AD1

  ADV2

  Valve device in the pressure channel AD2

  AS1

  Suction channel of the first positive displacement pump

  AS2

  Suction channel of the second positive displacement pump

  ASR1

  suction-side collecting ring channel of the first positive displacement pump

  ASR2

  suction-side collecting ring channel of the second positive displacement pump

  ASV1

  Valve device in the suction channel AS1

  ASV2

  Valve device in the suction channel AS2

  C

  clutch

  CL

  Slats of the clutch C

  D

  Rotary axis of the rotor assembly

  e

  electric machine

  HE

  Rotor of electric machine E

  G

  machine housing

  GV1

  Housing portion laterally adjacent to the cylinder portion Z1

  GV1

  Housing portion laterally adjacent to the cylinder portion Z2

  K1

  Engine pistons of the first piston group

  K2

  Engine piston of the second piston group

  KG

  sliding

  KGS

  shim

  KS

  lubricant channel

  PG1

  first base plate

  PG2

  second base plate

  PH

  auxiliary pump

  PK1

  Displacement piston of the first positive displacement pump

  PK2

  Displacement piston of the second positive displacement pump

  PS1

  Control surface of the first positive displacement pump

  PS2

  Control surface of the second positive displacement pump

  PZ1

  Displacement cylinder of the first positive displacement pump

  PZ2

  Displacement cylinder of the second positive displacement pump

  PV

  Spool valve

  RF1

  Flat rotary valve of the first positive displacement pump

  RF2

  Flat rotary valve of the second positive displacement pump

  RK1

  first rotor body of the rotor assembly

  RK2

  second rotor body of the rotor assembly

  RS1

  first control rotor (the first positive displacement pump)

  RS2

  second control rotor of the (second displacement pump)

  RSM1

  Lateral surface of the control rotor RS1

  RSM2

  Lateral surface of the control rotor RS2

  T1

  first stroke disc (the first piston group)

  T2

  second lifting disc (the second piston group)

  U1

  first overlay pump

  U2

  second overlay pump

  V

  valve control

  VE

  injection

  VK

  rocker arm

  VN

  Cam rotor of the valve control V

  VN1

  first cam rotor sleeve of the cam rotor VN

  VN2

  second cam rotor sleeve of the cam rotor VN

  VT

  Valve

  VU1

  first reduction gear of the cam rotor VN

  VU2

  second reduction gear of the cam rotor VN

  VUE

  Input-side spur gears of the reduction gears VU1, VU2

  BOI

  Output-side spur gears of the reduction gearboxes VU1, VU2

  WH

  Hollow shaft of the rotor assembly

  WT

  Drive shaft of the opposed piston internal combustion engine

  WT1

  stub shaft

  WT2

  stub shaft

  WZ

  hollow intermediate shaft in the clutch C

  Z

  engine cylinder

  Z1

  first cylinder section (of the first engine piston K1)

  Z2

  second cylinder section (second engine piston K2)

  For example,

  combustion chamber

  ZB 1

  Side zone of the combustion chamber ZB

  ZB2

  Side zone of the combustion chamber ZB

  ZBU

  Intersection zone of the combustion chamber ZB

  ZK

  Partial circle of the engine cylinders Z

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 2820552 A1 [0003]
• DE 1906171 A1 [0004]

Claims (10)

Opposed piston internal combustion engine with a plurality of arranged on a common pitch motor cylinders, in each of which a first engine piston and a second piston engine are longitudinally movable in opposite directions, which axially limit a volume variable combustion chamber and are in operative connection with a rotor assembly, which concentric to one circle and the motor cylinders having axially parallel axis of rotation, wherein the first engine piston is arranged in a first axial cylinder portion of the engine cylinder and the second engine piston is arranged in a subsequent to the first cylinder portion, the second axial cylinder portion of the engine cylinder and wherein the gas exchange in the combustion chamber, a valve control is provided, characterized in that the cylinder sections (Z1, Z2) of each engine cylinder (Z) are offset relative to one another in the circumferential direction of the pitch circle (ZK), wherein in each case the combustion chamber (ZB) - in cross section through the Gegenkolbenbre nnkraftmotor seen - an axially of the engine piston (K1, K2) limited overlapping zone (ZBU) of the two cylinder sections (Z1, Z2) and two in the circumferential direction of the pitch circle (ZK) on both sides of the intersecting zone (ZBU) subsequent side zones (ZB1, ZB2) respectively associated with one of the cylinder sections (Z1, Z2) and axially by the engine piston (K1 or K2) arranged in this cylinder section (Z1 or Z2) and by a housing section (GV) laterally adjacent to the opposite cylinder section (Z1, Z2) are limited, wherein in at least one of the two housing portions (GV) at least one valve (VT) of the valve control (V) is arranged in the housing of the range (GV) axially limited side zone (ZB1 or ZB2) of the combustion chamber (ZB) inside is movable. Opposed piston internal combustion engine according to claim 1, characterized in that the valves (VT) can be actuated by rocker arms (VK) arranged radially or approximately radially to the axis of rotation (D) of the rotor assembly and a cam rotor (VN) drivable by the rotor assembly and coaxial with the axis of rotation (D). is provided, which is in operative connection with the inner ends of the rocker arms (VK). An opposed piston internal combustion engine according to claim 2, characterized in that the cam rotor (VN) has a first and an axially adjacent second cam rotor sleeve (VN1 or VN2) provided with front axial cams (VNA) for actuating a respective group of rocker arms (VK) and can be driven by a hollow shaft (WS) of the rotor assembly, wherein in the power flow between the hollow shaft (WS) and the cam rotor sleeves (VN1 or VN2) reduction gear (VU1 or VU2) are connected. An opposed piston internal combustion engine according to any one of claims 1 to 3, characterized in that a swash plate designed as the first stroke (T1) the first engine piston (K1) and designed as a swash plate second stroke (T2) the second engine piston (K2) is assigned, wherein the lifting discs (T1, T2) are components of the rotor assembly and by means of sliding bodies (KG), in particular hydrostatically relieved sliding bodies, are in operative connection with the engine pistons (K1, K2). Opposite piston motor according to one of claims 1 to 4, characterized in that the first and / or the second engine pistons (K1 and K2) are each connected to a hydraulic displacement piston (PK1 or PK2) and in each case the strokes of the engine piston (K1 or K2). K2) in the cylinder section (Z1 or Z2) of the engine cylinder (Z) and of the motor piston (K1 or K2) connected in a positive displacement cylinder (PZ1 or PZ2) longitudinally movable displacement piston (PK1 or PK2) are equal in movement and directly to each other correlate, wherein the displacer (PK1 or PK2) is at least partially disposed within the engine piston (K1 or K2). Opposite piston internal combustion engine according to claim 5, characterized in that for controlling the pressure medium supply of the displacement cylinder (PZ1, PZ2) at least one can be driven by the rotor assembly flat rotary valve (RF1 or RF2) is provided. Opposite piston internal combustion engine according to claim 5, characterized in that for controlling the pressure medium supply of the displacement cylinder (PZ1, PZ2) with each displacement cylinder (PZ1 or PZ2) each a longitudinal slide valve (PV) is hydraulically connected, wherein at least one of the rotor assembly drivable control rotor (RS1 or RS2) is provided for actuating the longitudinal slide valves (PV). Opposing piston internal combustion engine according to claim 7, characterized in that the control rotor (RS1 or RS2) is axially movable and has a lateral surface (RSM1 or RSM2) with - in the longitudinal section of the control rotor (RS1 or RS2) seen - conical, in operative connection provided with the longitudinal slide valves (PV) standing control cam, wherein the longitudinal slide valves (PV) are arranged radially to the rotational axis (D) of the rotor assembly. Opposed piston internal combustion engine according to claim 5, characterized in that at least one variable in the stroke volume, with the Rotorbaugrupppe mechanically in drive connection or bringable overlay pump (U1 or U2) whose flow is reversible and changeable, in particular adjustable and reversible axial piston pump in swash plate design, with the displacement cylinders (PZ1, PZ2) is hydraulically connected or connectable. Opposed piston internal combustion engine according to claim 9, characterized in that in the power flow between the rotor assembly and the at least one overlay pump (U1, U2) a switchable clutch (C) is arranged, the superposition pump (U1 or U2) with a particular flywheel starter Generator formed electrical machine (E) is in drive connection and the hydraulic connection between the displacement cylinders (PZ1, PZ2) and the superposition pump (U1 or U2) by a switchable valve device (ADS1 or ADS2) can be shut off.

Images