Working machine with a dynamic curved-shaft system

Abstract

The working machine according to the invention with a dynamic curved-shaft system for use as a prime mover, heat engine or working machine comprises a housing (1) with piston-cylinder units (14) and comprises a system curved shaft (20) having a curved track on which the end regions of the piston rods (9) are slidingly disposed. The peripheral system curved shaft (20) has a pulling track (2) and a pressing track (3) on which the force bridges (4, 5, 18) disposed at the end regions of the piston rods (9) are disposed with corresponding pressing rollers (6). The pistons (11, 13) by means of the piston rods (9) onto the force bridges (4, 5, 18), which run on the pressing track (3) of the peripheral system curved shaft (20), in a plane, with force splitting according to the lever size, and is convertible into a rotational motion by means of the axial piston forces twice per revolution, at opposite points, with different piston velocity decouplings. As a result of the pivoting in of the force bridges (4, 5, 18), the piston velocity is decoupled from the peripheral velocity of the pressing track (3) of the system curved shaft (20).

Description

Working machine with a dynamic cam-shaft system (DKWS)

[0001] The invention relates to a working machine with a dynamic camshaft system (DKWS), generally to opposed piston techniques for operation as an internal combustion engine and for use as a hydraulic motor, pump or compressor.

[0002] However, known variants predominantly use a coupled crankshaft drive, a swash plate, or a wobble plate to convert the axial piston force into rotary motion. With opposed-piston technology, the pressure forces act on two opposing pistons. This means that the generated force is utilized on two opposite sides.

[0003] The disadvantage is that the design always requires consideration of the wobbling piston rod compensation, and the opposing force directions must be laboriously combined with a pinion drive or internally with a central shaft to achieve usable rotary motion. Furthermore, the permanent coupling prevents the pistons from being decoupled at different speeds, for example, to achieve different control times or pulse smoothing. Furthermore, each piston assembly can only perform work once per revolution.

[0004] DE 20 2007 015 140 U1 discloses an internal combustion engine with a crankshaft-less drive unit, in which pairs of opposing pistons are arranged concentrically and coaxially around a drive shaft and connected to one another by a piston rod. The oscillating piston movement can be transmitted from the piston rods to a cam track carrier with a cam track arranged on the drive shaft, and the drive movement is generated by the cam track rotating away from the piston forces. The cam track carrier is a cylinder that is mounted in a torsionally rigid manner on the drive shaft, and the cam track consists of at least two parallel grooves in the cylinder jacket of the cam track carrier's cylinder. Pins are guided in the grooves, each of which is connected to a piston rod.

[0005] In DE 10 2010 056 125 A1 an opposed piston engine is described, wherein the opposed piston engine has two fixed holders with the positions arranged in the tangential direction, in each of which a pair of opposite cylinders Z (with a cylinder head ZK and a piston unit) is fixed and the holders symmetrically arranged relative to the central plane of the structure, a rotating cam disc H, which is fixed coaxially on the drive shaft TW, and each piston unit includes a rotating element RH rolling on the cam disc H with a support element X. The engine includes a second rotating cam disc H, which is fixed coaxially on the drive shaft TW, so that both cam discs H are arranged symmetrically relative to the central plane of the structure, and a sinusoidal guide profile is provided on one of the end faces of each cam disc H, wherein the guide profiles of the cam discs H are arranged in a mirror-like manner to one another. The components of the piston units and the gas exchange system in the opposite positions are arranged in a mirror-like manner relative to the central plane of the structure, so that the same working processes occur in the opposite cylinders Z at all times.

[0006] The disadvantage is that the pendulum or wobble offset for the piston rod is not well solved, since the run-off roller (RH) only has a rolling and sliding line contact and thus there is no force distribution for the wear protection that is so important for higher force utilization.

[0007] DE 10 2010 006 197 A1 relates to a power machine for storing and releasing energy using weights rotating on a flywheel. The purpose of the weights is to generate increased torque with guided, movable weights in conjunction with a geometric imbalance on one half of the rotating circle related to the center of gravity of a rotating circle. The displacement of the weights in the upward rotation range and against gravity is intended to occur with minimal energy consumption due to shorter force arms than in the analogous mirror-image rotation angle, so that an excess torque is maintained in the system for a longer period.

[0008] A stand supports a rotor, which acts as a guide for the masses. By incorporating a spring and a slideway, the mass reaches the pivot point early and is in the quadrant with the positive moments before 180 degrees have passed. The design of the main components as modules and their arranging in any number in series enhances the performance of the device.

[0009] Although the solution describes a cam track in a plane, it doesn't feature a piston with a force bridge. Instead, it uses only tappets in the center with the aid of a spring. Furthermore, the cam track is fixed, and the tappet assembly rotates.

[0010] Current combustion engine technologies have limited energy utilization, achieve low efficiencies, and require numerous additional components. The basic principle of the crankshaft only allows for a limited lever deflection due to the clearance between the connecting rod and the cylinder liner, and thus, an extended torque design cannot be adapted.

[0011] Based on the prior art, the object of the invention is to further develop a working machine with a dynamic cam-shaft system (DKWS) in such a way that the disadvantages of the existing prior art are overcome in order to create a new mechanical drive unit in which an oscillating piston movement is converted into a rotating drive shaft movement via a cam track.

[0012] This object is achieved with the features of the first claim; advantageous embodiments are the subject of the subclaims and the following description.

[0013] The working machine according to the invention with a dynamic cam-shaft system (DKWS) for use as a power machine, heat engine or working machine comprises a housing with piston-cylinder units and a system cam shaft with a curved track on which the end regions of the piston rods are arranged to slide.The rotating system camshaft has a tension and a compression track on which the force bridges arranged at the end areas of the piston rods are arranged with corresponding sliding elements, whereby the pistons are actuated via the piston rods on the force bridges, which run in a plane on the compression track of the rotating system camshaft in a force-distributing manner according to the lever size and can be converted into a rotary movement twice per revolution by the axial piston forces and oppositely with different piston speed decouplings, whereby the piston speed is decoupled from the peripheral speed of the compression track of the system camshaft by pivoting in the force bridges.

[0014] Alternatively, the pressure rollers of the force bridges can be replaced by movable slide shoes. The pressure rollers form a continuous, consistent linear contact and can be designed in any other type of rolling or contoured shape, as well as spherical or conical. The pressure path of the system camshaft can have a rolling path in an elliptical shape or in a closed spline shape.

[0015] The force bridges are connected to the piston rods via the tension rollers, on the one hand, and to the system camshaft, on the other. A hydrodynamic bearing is provided for the piston rod in the piston rod guide. The force bridges can be designed symmetrically or asymmetrically to suitably vary the piston speed.

[0016] All constructible size ratios of the design points for the spline calculation of the system camshaft or any other freely definable trajectory curve shape, in variable relationship with the size ratios of the force bridge design, can lead to the appropriate stroke movement and speed change of the pistons. The angular variables Y'° in the functional sequence are in constant adaptation change, and the dimensions X can be determined constructively for the functional task.

[0017] The compression center may be dependent on the force bridge size ratios or any other type of force bridge geometry design.

[0018] Another special feature of the invention is that each arranged pair of pistons performs work twice per total revolution and different temporal decoupling from the peripheral speed is possible at the outer reversal points.

[0019] The system camshaft is provided with teeth on its outer circumference. According to the invention, the axially acting piston force is diverted to the rotating system camshaft opposite the shaft, thereby converting it into a rotational movement acting in one plane, which can be detected via the teeth. The special design is a novel rotating spline profile, which can be designed in different sizes and thus defines the piston stroke and its velocity decoupling.

[0020] The associated circumferential bearing creates a constant counter-force, and work is performed twice per revolution. This makes it possible for the first time to achieve different piston speeds per revolution, as well as to utilize the centrifugal forces at the circumference to support the rotation without creating imbalance. In addition, the leverage for the torque is many times greater. can be designed because the force is used from the piston crown to the rotating center point.

[0021] The piston rod transfers the forces axially to a force bridge, which allows the force to be redirected to the shared system camshaft in both directions of movement, which in turn controls the pistons. This positive guidance keeps the pistons always in their trajectory. This innovative change in the direction of force eliminates transverse forces acting on the piston skirt or cylinder liner. This makes it possible to use innovative materials for long-term operation.

[0022] The innovative overall design requires fewer additional components, which, in keeping with the design, represents a significant advantage over all previous technologies. Power can be delivered simultaneously and distributed across the large peripheral gear ring at different circumferential pitches and offset pitches to a common drive shaft. Thanks to the freely selectable cam profile size, torque design is no longer limited at different angular positions of the system camshaft, as is the case with crankshaft technology. This provides a significant improvement in efficiency.

[0023] The inventive machine with a dynamic cam-shaft system (DKWS) is designed as a crankshaft-less machine. These can be designed as opposed-piston, cam-track, cam-disk, and reciprocating piston engines with internal combustion, or as drives in pump technology (for radial and axial piston machines), as compressors, or as hydraulic motors.

[0024] All this results in the working machine according to the invention having a torque amplification, start-up amplification, pulse smoothing, noise minimization, reversal point delay for appropriate slot control of the different piston speeds in order to optimize the direct current flushing.

[0025] A key advantage is the decoupling of piston speed from circumferential speed at the respective reversal points, which, through design coordination, ensures appropriate port control. This allows the expanded gases to flow into the exhaust port first. The delayed opening of the intake port creates a cocurrent purge. In addition, the exhaust port closes before the intake port closes. This reduces the loss of fresh gases and promotes pre-compression.

[0026] The decoupling of the pistons from the peripheral speed occurs due to the symmetrically closed cam track in conjunction with the pivoting of the power bridges at the respective reversal points.

[0027] This allows for control with different piston speeds per revolution for each speed range and with a constant counterpressure. This allows, for example, direct flow purging in combustion technology without fresh gas losses using overpressure fillings. This allows for improved combustion with high excess air or pulse smoothing in hydraulic systems through reversal point delay.

[0028] A continuous following functional movement can be carried out with any number of pistons that can be constructed; for example, with eight pistons, four pistons are always sucking in and four pistons are generating pressure, whereby the rotary slide valve is coupled to the rotating gear ring or system circular shaft in order to ensure the respective switching point.

[0029] At the respective reversal points, the pairwise symmetrical pivoting of force bridges of the same size results in an opposite, equal speed decoupling of the pistons in the pivoting connection to the peripheral speed, whereby the pressure change and the switching pulsing are improved when the webs of the rotary valve are passed over, with the associated slowing down of the volume flow.

[0030] A rotary slide valve is located in the center for switching between the pressure and pressureless sides, as well as for other applications and any geometric opening shapes for volume flow. During switching of the rotary slide valve, an opposing piston pressure pair and a piston suction pair are always in continuous operation. The shared cylinder liner has an inlet and outlet opening at each of the outer reversal points.

[0031] The system camshaft's traction path is responsible for suction if the working machine according to the invention is designed as a pump or compressor. In hydraulic motors, the suction chamber can be used as a return chamber.

[0032] The design of the working machine with a dynamic cam-shaft system (DKWS) can be symmetrical with paired row arrangements, row-staggered or star-shaped arrangements.

[0033] The features described above or in the claims can also be mirrored or combined with unequal piston pitches in order to be able to implement the advantages accordingly.

[0034] Essentially, it involves converting a translational motion across two rolling line contacts into a rotational motion using a force-transfer bridge. Translation and rotation can each be described by four physical quantities. For translation, these are mass, velocity, acceleration, and force. For rotation, these are the moment of inertia, angular velocity, angular acceleration, and torque.

[0035] The principle of the invention is applicable to combustion engines, hydraulic motors, pumps, compressed air motors and compressor technology.

[0036] The invention will be explained in more detail using an example.

[0037] They show: Fig. 1 - Schematic diagram of the working machine according to the invention Fig. 2 - Section through the working machine according to the invention - opening outlet - Fig. 3 - Section through the working machine according to the invention - piston in BDC position Fig. 4 - Section through the working machine according to the invention - outlet closed and Entrance open Fig. 5 - Section through the working machine according to the invention - inlet and outlet closed Fig. 6 - Section through the working machine according to the invention Fig. 7 - Section through the working machine according to the invention in working function Fig. 8 - Section through the working machine according to the invention with representation of the Pressure change function

[0038] Figure 1 shows a schematic diagram of the working machine according to the invention, designed as an internal combustion engine with opposing piston-cylinder units 14, with the pistons shown in the TDC position. The housing 1 with inlet and outlet ports and the direction of rotation are shown. In the sectional view The closed cam tracks of the system camshafts (pull track 2 and push track 3) can be seen, with pistons 11 and 13 at top dead center. The asymmetrical force bridge 4 and the symmetrical force bridge 5 distribute the forces to two pressure rollers 6 each and assume position control at the reversal points. To secure the position during the start-up phase, a pull roller 7 is attached to the force bridge pivot point to prevent the pressure rollers 6 from lifting via the pull track 2.

[0039] Figure 2 shows a section through the working machine according to the invention in the working position - opening the outlet -. The upper sectional view shows the central detail K, showing the piston rod 9 in conjunction with the piston rod guide 8 for transverse force dissipation. The different pivoting of the force bridges 4 and 5 is also visible. In detail K, the piston 13 first opens the outlet channel 12 to control the outlet, whereby the remaining excess pressure is the first to escape into the outlet channel 12. Subsequently, the piston 11 opens the inlet channel 10 to control the inlet. This determines the co-flow direction for gas exchange.

[0040] Figure 3 shows a section through the working machine according to the invention - piston in BDC position and a representation of the force bridge function. In detail J, pistons 10 and 13 are at bottom dead center, and channels 10 and 12 are opened with a time delay, since force bridges 4 and 5, by pivoting in at the reversal point, decouple the circumferential speed 15 of the thrust track 3 of the system camshaft. The ratios marked x and Y ° show the change variables for the interaction of the circumferential movement with the piston movement, which is created by force bridges 4 and 5 and by the closed curve profile of the traction track 2 and the thrust track 3 of the system camshaft, which can be freely constructed in terms of size.

[0041] Figure 4 shows a cross-section through the working machine according to the invention, the DKWV engine in the position - exhaust closed and intake still open. The curve transition with the different lever sizes of the power bridges 4 and 5 subsequently ensures a faster closing of the exhaust port 12 compared to the intake port 10. This prevents the fresh gases from escaping and creates an excess of air before the actual compression takes place.

[0042] Figure 5 shows a section through the working machine according to the invention in the position inlet and outlet closed in the closed position and the Start of the joint piston movement for the gas volume to be compressed.

[0043] Figure 6 shows a section through the working machine according to the invention, illustrating the symmetrical piston stroke in one plane. It can be seen that the force for pressure generation is introduced via the piston rods 9 symmetrically from the thrust track 3 of the system cam shaft, and the transverse force is absorbed by the piston rod guide 8. This prevents any transverse forces from being applied to the piston skirt.

[0044] Figure 7 shows a section through the inventive work machine in a star design with eight piston-cylinder units 14 in working function. It can be seen that all eight pistons perform a continuously successive function, with four pistons each operating in the intake stroke and four pistons each operating in the compression stroke. The rotary slide valve 17 is coupled to a rotating gear ring 19 to ensure the respective switching point. The gear ring 19 can be used to dissipate or introduce force. The large circumferential bearing 16 can dissipate large forces in a well-distributed manner on the housing 1. Also visible is the traction track 2 of the system camshaft, which is responsible for suction when the work machine is designed as a pump. When designed as a hydraulic motor, the suction chamber is a return chamber. The middle section shows the traction roller 7, which is located on the pivot bearing of the symmetrical power bridge with hydraulic piston 18.

[0045] Figure 8 shows a working machine according to the invention, illustrating the pressure change function. It can be seen that at the respective reversal points, the speed of the pistons 18 is decoupled from the peripheral speed by the pairwise symmetrical pivoting of the force bridges 18. Traveling over the webs of the rotary valve 17, with a slowing down of the volume movement, improves the pressure change and the associated switching pulses. Furthermore, a double, opposing symmetrical force dissipation or introduction is always present. Additionally, during switching, an opposing piston pressure pair and a piston suction pair are always in operation, which significantly improves efficiency because a respective working volume is always present. This means that there are virtually no interruptions in the respective flow area.

[0046] The combustion engine's operation can be supported with simple pre-cooled air injection if a fan wheel is integrated into the system with an opposing motor disk via a peripheral gear coupling. This results in significant savings in overall weight and eliminates the need for manufacturing. of additional components such as turbochargers, camshafts, etc., as well as a constant excess of air to ensure combustion even at low engine speeds with a combustion air ratio of X=2. This results in a nitrogen oxide content in the per mille range, creating one of the cleanest combustion options.

[0047] Due to the associated special cooling effect, hydrogen combustion can also be used for continuous peak performance. Because the combusted gases are purged by means of the direct current purge and the constant excess of fresh air, and the new mixture is formed without residual gases, a consistently optimal combustion process is ensured.

[0048] Fuel injection can occur in a wide variety of positions, as the arrangement of injection nozzles or ignition units can be freely selected at the compression center. The oil supply for the hydrodynamic bearing of the piston rod guide can also be extended to include a piston crown cooling nozzle. This solves the overheating problems in opposed-piston combustion applications.

[0049] Compared to a crank drive, the utilization process of the inventive machine can be viewed as a single-cycle process with each revolution, because force is introduced and utilized in the opposite direction every 180°. Based on the thermodynamic cycle, this represents a significant improvement in efficiency. Since the energy supplied is distributed over 360°, it can be utilized continuously.

[0050] All this is a completely new usage process that can be described in more detail through scientific potential studies.

[0051] The invention is not limited to one of the above-described embodiments, but can be modified in many ways. All features and advantages apparent from the claims and the description, including design details, spatial arrangements, and method steps, can be essential to the invention both individually and in a wide variety of combinations. Other structural variants and adaptations of the disclosure are possible, and they can be implemented or carried out in practice in various ways.

[0052] Reference symbol list 1 - Housing 2 - Trajectory of the system cam shaft 3 - Pressure path of the system cam shaft 4 - Asymmetrical power bridge 5 - Power bridge symmetrical 6 - Pressure roller 7 - Pulley 8 - Piston rod guide 9 - Piston rod 10 - Inlet channel 11 - Piston for controlling the intake 12 - Outlet channel 13 - Piston for controlling the exhaust 14 - Piston-cylinder unit 15 - Decoupling from the peripheral speed 16 - Circumferential bearing 17 - Rotary slide valve 18 - Symmetrical power bridge with hydraulic piston 19 - Gearing 20 - System camshaft

Claims

Patent claims 1. Working machine with a dynamic cam-shaft system (DKWS) for use as a power, heat or working machine comprising a housing with piston-cylinder units and a system cam shaft with a cam track on which the end regions of the piston rods are arranged to slide, characterized in that the rotating system cam shaft (20) has a traction track (2) and a pressure track (3) on which the force bridges (4, 5, 18) arranged at the end regions of the piston rods (9) with corresponding pressure rollers (6) are arranged, wherein the pistons (11, 13) are acted upon via the piston rods (9) onto the force bridges (4, 5, 18), which run in a plane on the pressure track (3) of the rotating system cam shaft (20) in a force-distributing manner according to the lever size and are acted upon by the axial piston forces twice per revolution, as well as oppositely with different Piston speed decoupling can be converted into a rotary movement, wherein the piston speed (15) is decoupled from the outer peripheral speed of the pressure track (3) of the system cam shaft (20) by pivoting in the power bridges (4, 5, 18).

2. Work machine with a dynamic cam-shaft system (DKWS) according to claim 1, characterized in that the pistons (11, 13) are connected to the tension rollers (7) on the power bridges (4, 5, 18) and the system cam shaft.

3. Work machine with a dynamic cam-shaft system (DKWS) according to claim 1 to 2, characterized in that for securing the position a tension roller (7) is attached to the pivot point of each of the power bridges (4, 5, 18) in order to prevent the pressure rollers 6 from lifting off the tension track 2 in the starting phase.

4. Working machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 3, characterized in that the design of the power bridges (4, 5, 18) can be symmetrical or asymmetrical for the appropriate piston speed change.

5. Working machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 4, characterized in that a hydrodynamic bearing is provided in the piston rod guide (8) for the piston rod (9).

6. Work machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 5, characterized in that the pressure rollers (6) form a continuous, consistent line contact and can be designed in any other type of rolling or contour shape as well as in spherical or conical shape.

7. Work machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 6, characterized in that the pressure track (3) of the system cam shaft (20) has a rolling track with an elliptical shape or with a closed spline shape.

8. Work machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 7, characterized in that the structure of the drive machine can be designed symmetrically with paired row arrangements, offset in rows, distributed in a star shape, wherein the number of pistons (11, 13) can be arbitrary. Work machine with a dynamic cam-shaft system (DKWS) according to claims 1 to 8, characterized in that the system cam shaft (20) is provided with a toothing (19) on its outer circumference.

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