Self-propelled ground working machine with double engine and working transmission

Abstract

A self-propelled ground processing machine has a machine frame, which accommodates a work device for ground processing, at least one functional device different from the work device on the machine frame, a drive assembly, which provides work drive power for the work device and functional drive power for the at least one functional device, a work transmission mechanism between the drive assembly and the work device, and a functional transmission mechanism between the drive assembly and the at least one functional device. The drive assembly includes first and second engines, each of which is connected to the work device via the work transmission mechanism such that the work device can be driven to perform a prescribed ground processing only by the first engine or only by the second engine. The work transmission mechanism connects the first engine to the work device at a first transmission ratio and the second engine to the work device at a second transmission ratio different from the first transmission ratio.

Description

Self-propelled ground processing machine with dual engines and working transmission mechanism Technical Field

[0001] The present invention relates to a self-propelled ground processing machine having a mechanical frame supported by a traveling mechanism, wherein the traveling mechanism is erected on the ground and has multiple traveling mechanisms capable of rolling on the ground. Background Technology

[0002] The mechanical frame houses a working device, which serves as a first power receiver for ground processing, and is capable of driving the working device to perform working movements relative to the mechanical frame.

[0003] The mechanical frame houses at least one functional device, distinct from the working device, serving as a second power receiver.

[0004] A drive assembly is housed on a mechanical frame, the drive assembly providing the working drive power of the ground processing machine's working device and the functional drive power of at least one functional device.

[0005] A working transmission mechanism is provided between the drive assembly and the working device to transmit torque between the drive assembly and the working device. A functional transmission mechanism is provided between the drive assembly and at least one functional device to transmit torque between the drive assembly and at least one functional device.

[0006] The drive assembly includes a first engine and a second engine, wherein each engine is connected to the work device via a work transmission mechanism to transmit torque, such that the work device is driven by the first engine alone, or by the second engine alone, or by both the first and second engines to perform work movements to carry out the prescribed ground processing.

[0007] Such a ground processing machine designed as a road milling machine is known from EP 1 983 105 B1.

[0008] This document proposes that the first and second engines can be constructed identically or differently. Using different engines typically increases maintenance workload for the drive components because each of the two engines may be subject to different maintenance specifications, thus requiring corresponding training for maintenance personnel and the provision of separate spare parts for each engine, which are not interchangeable. While using identically constructed engines reduces maintenance workload, it limits the availability of the drive components because, for example, the first and second engines have identical speed-torque characteristic curves within essentially the same usable speed range, except for small to negligible differences caused by manufacturing and installation tolerances.

[0009] A ground machining machine, in the form of a road milling machine, is known from DE 10 2012 006 189 A1. The drive assembly of the ground machining machine has a higher-power main drive and a lower-power auxiliary drive, whose torque paths are guided to the working device via a planetary transmission mechanism as the main transmission mechanism. Therefore, the working device can be rotated at a low speed during maintenance operation and at a higher speed, especially with higher power, during ground machining operation via the auxiliary drive. Similarly, the milling roller can be accelerated first by the auxiliary drive to a speed at which the main drive can be engaged to continue accelerating the milling roller. However, during the specified ground machining operation, the milling roller is always driven only by the main drive. The auxiliary drive is not designed or constructed to drive the milling roller during the specified ground machining operation.

[0010] Another ground machining center with milling rollers is known from DE 10 2015 002 743 A1. The known ground machining center has a control device configured to match the rotational speed of the milling rollers to the operating conditions of the ground machining center based on at least one measured variable characterizing the critical operating state of the milling rollers, such as the load torque as a function of time during operation, so that the milling rollers operate in a non-critical operating state. This adaptive control of the milling roller rotational speed allows the ground machining center to operate at an optimal working point in terms of the milling roller rotational speed. The characterized measured variable is detected by a signal recording unit configured for its detection and transmitted to the control device.

[0011] According to DE 10 2015 111 249 A1, a milling machine as a ground processing machine is known, whose control device is configured to set the mechanical parameters of the ground processing machine operation in consideration of the material properties of the ground to be processed, so that there are favorable wear performance of the ground processing tools used. Summary of the Invention

[0012] Based on EP 1 983 105 B1 above, the object of the present invention is to improve a known ground processing machine so that it can have a wider range of operating parameters within which it can operate during ground processing. This allows for targeted setting of ground processing operating parameters, saving resources and extending maintenance cycles.

[0013] The present invention achieves this objective based on the ground processing machine described at the beginning by means of a working transmission mechanism that connects a first engine to the working device at a first transmission ratio and connects a second engine to the working device at a second transmission ratio different from the first transmission ratio.

[0014] The contribution of the first and second engines to the total drive power of the drive assembly can be extended by using different gear ratios when transmitting the engine power of the first and second engines to the working device. This extension occurs because the different gear ratios themselves occur when the same or structurally identical engines are used as the first and second engines.

[0015] A particularly large expansion of the engine power transmitted to the working device can be achieved by using different engines, each with different engine power and preferably different usable speed ranges. The working device can operate within a particularly comprehensive speed range during the specified ground machining. The engines can be different, but can be based on the same physical principle. For example, two engines can be internal combustion engines. However, it should not be excluded that the engines output drive power based on different physical principles.

[0016] The first and second engines preferably have rated power in the range of 150 to 800 kW, more preferably in the range of 300 to 750 kW, and particularly preferably in the range of 550 to 650 kW.

[0017] However, because providing different gear ratios for the first and second engines extends the range of speeds available on the working device, and because using engines with identical structures as the first and second engines provides the advantage of significantly reduced maintenance costs, the first and second engines are preferably engines with identical structures. Engines supplied and sold by the same engine manufacturer under the same model name are particularly considered to be structurally identical, even if individual components that do not significantly affect their rated power and rated operating performance may differ. It is not uncommon in engine manufacturing to provide two supply sources for a single component for supply security, with both supply sources providing components that function substantially the same, but are nominally not entirely identical, for the same engine model.

[0018] Preferably, the first and second engines are internal combustion engines, and particularly preferably diesel engines. They can operate at their optimal operating points according to preset boundary conditions during the specified ground processing operation, such as particularly low emissions or particularly low consumption.

[0019] In principle, it should not be excluded that one or both engines use different physical principles and, for example, can be constructed as electric motors. However, heat engines generally have a narrower speed range for the same rated power, within which they can operate and because the combustion process required for their operation is less freely adjustable than that of electric motors. Therefore, the working transmission mechanism proposed herein, with different gear ratios for the two said engines, is particularly advantageous for heat engines.

[0020] Ground processing machines can be, for example, road milling machines, recycling machines, stabilizing machines, or open-pit mining machines. All of these ground processing machines have the working device described at the beginning, which moves to perform ground processing. More precisely, all of these ground processing machines have a working device for stripping ground processing, such as milling rollers that can rotate about a milling axis. Therefore, the working motion is preferably a rotary working motion, and thus, in principle, different working motions, such as reciprocating translational and / or rotary working motions possible through the use of eccentric wheel transmission mechanisms, should not be excluded.

[0021] In principle, different transmission ratios can be provided in any structural manner within the working transmission mechanism. A preferred and robust structural design for a working transmission mechanism with different transmission ratios for the first and second engines can be achieved by having rotatable transmission members with different operating diameters interact with the first and second engines to induce different transmission ratios. The rotatable transmission members can be, for example, at least one of gears, friction wheels, and pulleys.

[0022] Because the ground machining machine discussed here transmits the drive power of the first and second engines to the working device via a working transmission mechanism when particularly high milling power is required, in the initial operating state where two engines output power to the working device, the transmission components of each torque transmission of the working transmission mechanism are indirectly connected to each engine to move together. Here, the connection used to enable the two components to move together refers to a physical connection where one component rotates continuously as the other component rotates.

[0023] More precisely, a first rotary transmission member having a first operating diameter is preferably connected to the first engine for joint rotation, and a second rotary transmission member having a second operating diameter different from the first operating diameter is connected to the second engine for joint rotation. Here, the first rotary transmission member is located between the first engine and the second rotary transmission member in the torque path from the first engine to the second rotary transmission member, and the second rotary transmission member is located between the second engine and the first rotary transmission member in the torque path from the second engine to the first rotary transmission member. In this way, although all torque transmission transmission members of the working transmission mechanism are at least indirectly connected simultaneously in the first and second engines, desired different transmission ratios are achieved, on the one hand, between the first engine and the working device, and on the other hand, between the second engine and the working device.

[0024] Preferably, the working transmission mechanism includes or is a traction transmission mechanism. In principle, the traction transmission mechanism can be a form-locking traction transmission mechanism. The traction element of the working transmission mechanism can be, for example, a chain, such as a roller or a flat chain, or a toothed belt. Preferably, the traction transmission mechanism is a force-transmitting traction transmission mechanism, such that, in principle, there is a possibility of slippage between the traction element and at least one transmission component. Because slippage in the working transmission is undesirable, slippage at this point, precisely when both engines are simultaneously transmitting power to the working device via the working transmission mechanism, can smooth out the instantaneous power difference without excessively loading the transmission component driving the transmission mechanism or the output shaft of the power output of the first or second engine. Therefore, the peak load at the transmission component or the first or second engine can be temporarily reduced by slippage.

[0025] The ordinal numbers “first” and “second” used do not indicate order, but rather distinguish similar components and component sections in other respects and indicate their functional and / or structural correspondence with the first or second engine. A second component assigned to the second engine may generally exist where only the first or only the second component and component section may exist according to this specification, rather than being mandatory to have a first component of the same type. The same applies to component sections, but not components.

[0026] The first rotary transmission component can be advantageously simple and equally reliable in terms of structure by at least one of the following transmission components.

[0027] i) The first reversing roller that reverses the direction of the traction component of the traction transmission mechanism and

[0028] ii) A first gear or friction wheel arranged in the torque path from the first engine to the first reversing roller.

[0029] In option i), it is preferred that the reversing roller rotates at the same speed as the output shaft of the first engine without the need for an intermediate transmission stage. This achieves the minimum number of components required to implement the working transmission mechanism for introducing the torque of the first engine to the input side of the working transmission mechanism.

[0030] However, option ii) can be selected when, for example, boundary conditions based on available structural space require reaching the first reversing roller across a distance orthogonal to the rotation axis of the first engine's output shaft. Typically, this achieves a drive stage between the first engine and the first reversing roller that transmits power from the first engine to the first reversing roller under changes in speed and torque directly output by the first engine.

[0031] Options i) and ii) may also be applied in combination if necessary, for example by using a transmission stage between the first engine and the reversing roller to achieve radial offset of the torque path, wherein a portion of the transmission ratio of the working transmission mechanism for the first engine is caused by the transmission stage and another portion by the reversing roller.

[0032] The description of the first engine and the first rotary transmission member can also be applied additionally or alternatively to the second engine and the second rotary transmission member. Therefore, the second rotary transmission member can be at least one of the following transmission members.

[0033] iii) The second reversing roller that reverses the direction of the traction element of the traction transmission mechanism and

[0034] iv) A second gear or friction wheel arranged in the torque path from the second engine to the second reversing roller.

[0035] The above description of the first engine and the first rotary transmission component is applicable to the second engine and the second rotary transmission component with necessary modifications.

[0036] For example, the transmission ratio of the engine power of one of the first and second engines to the working device via the working transmission mechanism can be a transmission ratio in the range of 13.5:1 to 16.5:1, especially 14:1 to 16:1, where the speed decreases or the torque increases.

[0037] Similarly, the transmission ratio of the engine power of the corresponding other engine in the first engine and the second engine can be a transmission ratio in the range of 17.5:1 to 20.5:1, especially 18:1 to 20:1, where the speed decreases or the torque increases.

[0038] In addition to the traction drive mechanism, the working drive mechanism may include a planetary drive mechanism that operates in the torque path between the third reversing roller allocated to the working device and the working device. Preferably, the planetary drive mechanism serves to reduce speed and increase torque.

[0039] In principle, either the first or second engine can directly transmit power to the functional transmission mechanism. In a preferred embodiment, each engine directly transmits power to the functional transmission mechanism, which has a large transmission ratio that reduces rotational speed. If the first and second engines have identical structures in this application, the engines, with a larger transmission ratio in the working transmission mechanism that reduces rotational speed, induce a slower working motion at the working device.

[0040] As mentioned at the beginning, the working device can be driven by the first engine alone, the second engine alone, or both the first and second engines. Therefore, in a preferred embodiment of the invention, to achieve different operating modes, a switchable first clutch is arranged in the first torque path between the first engine and the working device, to open or close the first torque path depending on the switching state of the switchable first clutch. Thus, the second engine can provide only the torque needed to move the working device without towing the first engine.

[0041] Alternatively or preferably additionally, a switchable second clutch may be arranged in the second torque path between the second engine and the working device to open or close the second torque path depending on the switching state of the switchable second clutch. This allows the working device to be driven solely by the first engine without towing the second engine.

[0042] At least one functional device, driven by a functional transmission mechanism different from the working transmission mechanism, makes a significant contribution to the operation of the ground processing machine, independent of the ground processing by the working device. Thus, by driving a hydraulic pump as a functional device, hydraulic pressure can be provided to hydraulic devices, such as lifting mechanisms for raising and lowering the mechanical frame relative to the traveling mechanism, steering for the various traveling mechanisms, and as a drive for a hybrid power unit, and for providing propulsion in the various traveling mechanisms and thus on the working device. Similarly, a generator, which may be a functional device, can be driven to provide current to the power-consuming parts of the ground processing machine, such as for lighting and control. Similarly, a pneumatic pump can be driven to provide pneumatic pressure to pneumatic devices, such as pneumatic piston-cylinder assemblies.

[0043] To ensure the functional device can be driven independently of the operating device, preferably applicable to one of the first and second engines, a switchable clutch arranged in the torque path between the engine and the operating device interrupts torque transmission from the engine to the operating device in relation to its switching state, but does not interrupt torque transmission from the engine to the functional transmission mechanism. Because the first and second engines are motion-coupled via the operating transmission mechanism, each device that can be directly driven by one of the two engines can, in principle, be indirectly driven by the other engine. Preferably, the functional transmission mechanism is assigned to one of the two engines, such that, according to a preferred improvement of the invention, for the corresponding other engine, a switchable clutch arranged in the torque path between the other engine and the operating device interrupts torque transmission from that other engine to the operating device and to the functional transmission mechanism in relation to its switching state.

[0044] The functional drive mechanism is known to be a transfer case, where the number of output shafts is greater than the number of input shafts. Preferably, the functional drive mechanism has only one input shaft, to which one of the first and second engines directly introduces torque. Similarly, the functional drive mechanism preferably has more than one output shaft to drive more than one functional device. Because the aforementioned ground processing machine uses hydraulic pressure as the energy source for the functional drive mechanism in a significantly larger context, multiple hydraulic pumps and / or gas pumps, especially pneumatic pumps, are preferably arranged on the transfer case. Thus, the functional drive mechanism is commonly referred to in the field as a pump transfer case.

[0045] As described above, at least one functional device may include at least one liquid pump and / or at least one gas pump and / or at least one generator and / or at least one mechanical auxiliary drive.

[0046] Particularly preferably, the ground machining center has an auxiliary drive independent of the two engines for driving the milling rollers during maintenance operations. During maintenance operations, the milling rollers should rotate at a significantly reduced speed and torque relative to the working drive mechanism. Therefore, by using an additional auxiliary drive, preferably an electric or hydraulic engine, the milling rollers can be rotated during maintenance operations independently of the operation of the two mentioned internal combustion engines used for driving. The energy of the auxiliary drive is preferably provided by an accumulator, such as a battery, storage battery, or hydraulic reservoir.

[0047] In principle, the working device can be any device for surface processing. Preferably, the working device mentioned herein includes or is constructed and arranged to remove surface material by rotating about a milling axis. Milling chisels are arranged on the outer circumferential surface of the milling roller tube via a chisel holder or preferably a chisel replacement holder. The milling chisels are typically arranged in a helical shape to remove the surface material removed from the surface structure from the milling roller, and particularly preferably in a double helix shape from the axial intermediate region of the milling roller about the milling axis in opposite axial directions, wherein the helix on each side of the axial intermediate region of the milling roller extends away from it.

[0048] Because the engine typically has a higher rotational speed than the working device and simultaneously provides lower torque than is required for ground machining via the working device, the working transmission mechanism preferably transmits the power of the first and second engines to the working device while reducing the rotational speed and increasing the torque output at the corresponding rotational speed.

[0049] Driving the same working device with two engines coupled to their output side via a working transmission mechanism in a substantially automated manner can be challenging under certain operating conditions, thus coordinating the operating parameters of the two engines motion-coupled via the working transmission mechanism. The operation of outputting engine power from the first and second engines to the working device in parallel presents particular challenges to the control of the engine and working device operation. Therefore, the present invention also relates to a method for operating the self-propelled ground processing machine described above and its modifications via a ground processing machine control device, wherein the first and second engines simultaneously output power to the working device, the method comprising...

[0050] a) The step of adjusting one of the two engines, the first and second engines, to a target speed determined by user input and / or by at least one detected value from a sensor and / or by querying data relationships.

[0051] b) The step of adjusting the corresponding other engine of the first and second engines to a motion variable selected from speed and torque, wherein the ratio of the difference between the value of the motion variable of the corresponding other engine and the value of the same motion variable of the speed-adjustable engine is different from the ratio of the difference between the first and second transmission ratios of the working transmission mechanism.

[0052] Based on input from the mechanical operator and / or sensor detection, one of the two engines is adjusted to a predetermined speed, where sensor detection also includes detecting torque transmitted to the working device and / or torque output from one of the engines. This is the speed-adjustable engine among the two engines. The speed of the speed-adjustable engine is related to the desired or required theoretical working speed of the working device. The theoretical working speed of the working device is typically a preset variable for ground machining. In the preferred case where a milling roller is used as the working device, the working speed of the milling roller is its rotational speed. The theoretical working speed may, for example, be related to the desired milling depth, the desired feed rate, and the characteristics of the surface to be machined, such as hardness, when the milling roller is used as the working device.

[0053] Particularly preferably, the control device is configured to monitor operating parameters during the operation of the milling rollers, which are the preferred working device, for the prescribed surface machining process. These parameters include the current milling roller speed and / or the torque output by the engine and / or the depth of cut and / or the feed rate. The characteristics of the surface to be machined can be determined by evaluating these mechanical parameters, for example, based on stored and predefined parameter relationships. By taking into account the determined characteristics of the surface to be machined, an optimized rotational speed for the current operating conditions can be determined and set to ensure particularly efficient and / or economical operation.

[0054] One of the two engines can have its speed or torque adjusted via a control device. To avoid undesirable mutual interference between the two engines in terms of their speeds, each engine is adjusted to a target speed, the difference between which is different from the difference in the transmission ratios of the two engines' working transmission mechanisms. Alternatively, the other engine is adjusted to a target torque, the difference between which is different from the torque output by the first engine at its target speed, and the difference in the transmission ratios of the two engines' working transmission mechanisms.

[0055] If determining the motion variables of one of the first or second engines or the working device requires including the transmission ratio of the working transmission mechanism, then the working transmission mechanism is always in slip-free operation.

[0056] The target speed of the always-adjustable engine is preferably derived based on the desired or required theoretical operating speed of the working device. The control device derives the intermediate target speed of the adjustable engine from the theoretical operating speed of the working device, using the known transmission ratio of the working gear for the adjustable engine.

[0057] If the other engine of the first and second engines is also speed-adjustable, the control device can also derive the intermediate target speed of the other speed-adjustable engine by using the known transmission ratio of the working transmission mechanism for the other speed-adjustable engine.

[0058] The two intermediate target speeds thus derived are necessarily related to the transmission ratios of the two engines' operating transmission mechanisms. As this invention has found, directly using the intermediate target speeds causes instability in the regulated operation of the two engines.

[0059] To avoid this instability, the control device preferably implements a final determination method, wherein at least one intermediate target speed of an engine is changed relative to a target speed, such that the numerical difference between the two finally determined target speeds increases. For this purpose, the control device may perform at least one of the following measures:

[0060] i) Increase the value of the higher of the two intermediate target rotational speeds.

[0061] ii) Reduce the lower of the two intermediate target speeds.

[0062] The increase in the numerical difference between these two intermediate target speeds does not need to be large. An increase of less than 3% in the higher intermediate target speed as a single measure is sufficient. Similarly, a decrease of less than 3% in the lower intermediate target speed as a single measure is also sufficient. If the higher and lower intermediate target speeds are changed within the above ranges when finally determined, each change can be numerically lower than that of only one intermediate target speed in a single measure, thereby achieving the same change in the numerical difference of the intermediate target speeds and the same regulatory effect.

[0063] Instead of increasing the percentage of the numerical difference in intermediate target speeds, the predetermined difference can be increased, for example, by 10 to 20 revolutions per minute, preferably 15 revolutions per minute. The predetermined difference can be applied only to one intermediate target speed or can be distributed across two intermediate target speeds. This generates a kind of "kinetic tension" between the two engines via a working transmission mechanism that couples their motion, which, for example, prevents the two engines, operating through a common control device, from manipulating each other into an undesirable speed increase operating state.

[0064] To simplify the adjustment method, it is preferable to change only the intermediate target speed of one of the two engines when finalizing the adjustment, while the intermediate target speed of the other engine is preferably kept at the target speed.

[0065] The control unit adjusts the first and second engines to the target speed, which is the intermediate target speed that is finally determined by the final determination method.

[0066] This also applies to cases where the other engine is torque-adjustable. Preferably, as described above, the target speed of the speed-adjustable engine is derived based on the theoretical operating speed of the working device. The resulting target speed is the target variable for the speed-adjustable engine.

[0067] In another engine with adjustable torque, the control device first determines what torque the speed-adjustable engine will output at its target speed. The torque value obtained from the torque-adjustable engine is altered, particularly reduced, to obtain the target torque of the other engine with adjustable torque. Based on this, the control device can operate the other engine with adjustable torque in a state where the target torque is output by the other engine, and this target torque is changed, particularly reduced, by a predetermined value relative to the torque of the torque-adjustable engine. The ratio of the difference between the output torque of the speed-adjustable engine and the theoretical torque of the other engine with adjustable torque differs from the ratio of the transmission ratios of the working transmission mechanisms of the first and second engines. This also causes the aforementioned "kinetic tension" between the two engines, which are kinematically coupled to each other via the working transmission mechanism. The predetermined value can be a value added or subtracted, or it can be a factor, for example, 95% of the torque induced by one engine on the working device.

[0068] Preferably, the engine with a larger gear ratio that reduces speed is an engine whose speed is always adjustable. The corresponding engine with a smaller gear ratio that reduces speed may have adjustable speed or torque, depending on the operating parameters of the engine whose speed is always adjustable.

[0069] The above method allows the use of a control device when both the first and second engines transmit engine power to the working device via the working transmission mechanism. However, this is not the only operating mode for the ground processing machine. In principle, the control device enables the self-propelled ground processing machine to operate in at least the following three operating modes:

[0070] 1) Only one of the first and second engines transmits torque to the working device via a working transmission mechanism, and the other of the first and second engines transmits torque to at least one functional device via a functional transmission mechanism.

[0071] 2) The two engines, the first and second, transmit torque to the working device via the working transmission mechanism.

[0072] 3) Only one of the first and second engines transmits torque to the working device via the working transmission mechanism and to at least one functional device via the functional transmission mechanism, while the corresponding other engine of the first and second engines is turned off.

[0073] Therefore, the above method involves the aforementioned operating mode 2).

[0074] Finally, the present invention relates to a self-propelled ground processing machine constructed according to the above description and having a control device, wherein the ground processing machine, and in particular its control device, is used to perform the method according to the foregoing. Attached Figure Description

[0075] The invention will now be described in detail with reference to the accompanying drawings. Wherein it is shown that:

[0076] Figure 1 shows a rough side view of a ground processing machine according to an embodiment of the present invention.

[0077] Figure 2 shows a rough side view of the drive assembly, working transmission mechanism, working device, and functional transmission mechanism of the ground processing machine of Figure 1.

[0078] Figure 3 shows a rough top view of the drive assembly, working transmission mechanism, working device, and functional transmission mechanism of the ground processing machine of Figure 1. Detailed Implementation

[0079] Figure 1 illustrates an embodiment of the invention of a ground processing machine, generally indicated by 10, in the form of a rotary tiller or milling machine. The ground processing machine includes a mechanical frame 12 that forms the base of a machine body 13. The machine body 13 includes the mechanical frame 12 and components connected to the mechanical frame 12 that are movable relative to the mechanical frame when necessary.

[0080] The main mechanical body 13 includes a front lifting column 14 and a rear lifting column 16. One end of the front lifting column and the rear lifting column are connected to the mechanical frame 12, and the other end is connected to the front traveling mechanism 18 or the rear traveling mechanism 20. The distance between the mechanical frame 12 and the traveling mechanism can be changed by the lifting columns.

[0081] The traveling mechanism is exemplarily shown as a chain-type traveling mechanism. A single or all of the traveling mechanisms may differ from this and be wheeled traveling mechanisms.

[0082] The observer in Figure 1 looks at the ground processing machine, or simply "machinery," along the machine's lateral direction Q, which is orthogonal to the drawing plane of Figure 1. The machine's longitudinal direction, denoted by L, is orthogonal to the lateral direction Q and extends parallel to the drawing plane of Figure 1. The machine's height direction H is also parallel to the drawing plane of Figure 1 and extends orthogonally to both the machine's longitudinal direction L and lateral direction Q. The arrowhead of the machine's longitudinal direction L in Figure 1 points in the forward direction. The machine's height direction H extends parallel to the machine's yaw axis Gi, the machine's longitudinal direction L extends parallel to the roll axis Ro, and the machine's lateral direction Q extends parallel to the pitch axis Ni.

[0083] The ground processing machine 10 has a cab 24 from which the machine operator can control the machine via a control console 26, which serves as the control device for the ground processing machine 10. The control console 26 has an operation display 27, such as a touch screen. The control device includes integrated circuits and data storage.

[0084] A working assembly is arranged beneath the mechanical frame 12, here for example as a milling assembly 28 having a milling roller 32 housed in a milling roller box 30. The milling roller is rotatable about a milling axis R extending in the transverse direction Q of the machine, so that ground material can be removed from the supporting surface AO of the ground U during ground machining at a milling depth determined by the relative height position of the mechanical frame 12. Thus, the milling roller 32 is the working device and the first power receiver in this application. Alternatively or additionally, the milling roller 32 can be accommodated on the mechanical frame with adjustable height relative to the mechanical frame 12.

[0085] The height adjustability of the machine frame 12 via the lifting column is also typically used to set the milling depth or general working depth when the machine is machining the ground. The exemplary ground machining machine 10 shown is a large milling machine in which the milling assembly 28 is typically arranged along the longitudinal direction L of the machine between the front travel mechanism 18 and the rear travel mechanism 20. Such large milling machines or ground-removing machines generally have a conveyor belt to transport the removed ground material from the machine. For clarity, the conveyor belt, which is present in principle in the machine, is not shown in Figure 1.

[0086] Not visible in the side view of Figure 1, the machine has two lifting columns not only in its front end region but also in its rear end region, each lifting column having a traveling mechanism connected thereto. Each front lifting column 14 is coupled to its corresponding front traveling mechanism 18 in a manner known per se via a traveling mechanism connection structure 34, for example, by a connecting fork that spans across the corresponding front traveling mechanism 18 in the transverse direction Q of the machine. Each rear lifting column 16 is connected to its corresponding rear traveling mechanism 20 via a traveling mechanism connection structure 36 constructed identically to the traveling mechanism connection structure 34. The traveling mechanisms are constructed substantially identically and form the traveling mechanism 22 of the machine. The traveling mechanisms are driven by an engine, typically a hydraulic engine (not shown).

[0087] The driving force source of the machine is formed by a drive assembly 39 housed on the machine frame 12, which is shown in more detail in Figures 2 and 3 and described therein. In the illustrated embodiment, the drive assembly 39 drives the milling roller 32 to rotate about the milling axis R. The power from the drive assembly 39 also provides a hydraulic pressure reservoir on the machine, through which the hydraulic motor and hydraulic actuators on the machine can be operated. Therefore, the drive assembly 39 is also the driving force source of the machine. The drive assembly 39 supplies power to all the functional receivers described in this embodiment, that is, to provide operational drive power to the milling roller 32 and to provide functional drive power to the functional devices described below.

[0088] In the example shown, each of the forward walking mechanisms 18, which has a radially inward receiving and guiding structure 38, has a walkable chain 40 arranged on it and guided to perform a circumferential movement.

[0089] The front rising column 14 and the front traveling mechanism 18 together can rotate about the steering axis S via a steering device (not shown in detail). Preferably, additionally, but also alternatively, the rear rising column 16 and the rear traveling mechanism 20 together can rotate about a steering axis parallel to the steering axis S via a steering device.

[0090] The cab 24 is shielded by a protective canopy structure 42, which includes a protective canopy 44 connected to the machine frame 12 or machine body 13 via a front panel assembly 46 and a rear wall assembly 48. The protective canopy 44 is vertically and flexibly mounted on the machine frame 12 by means of a motion guide 50. In Figure 1, the protective canopy 44 is shown in its raised operating position, in which the machine is ready for processing operations.

[0091] Figure 2 shows the drive assembly 39 and its associated unit in more detail. In Figure 2, the observer is looking at the drive assembly 39 in the same direction as in Figure 1, that is, parallel to the transverse mechanical direction Q.

[0092] The drive assembly 39 includes a first engine 52 and a second engine 54, which are arranged side by side on the mechanical frame 12 with their crankshafts or output shafts parallel to each other and extending along the mechanical transverse direction Q via a rotation axis 56 or 58.

[0093] A functional transmission mechanism 62, acting as a transfer case, is arranged between the observer in Figure 2 and the first engine 52. This transfer case is permanently coupled to the output shaft of the first engine 52 to transmit torque. A hydraulic pump is arranged on a driven mechanism on the functional transmission mechanism 62 as a functional device and another power receiver, such that the hydraulic pump can always be operated via the functional transmission mechanism 62 through the first engine 52.

[0094] A switchable first clutch 66 is arranged between the observer and the functional transmission mechanism 62 in Figure 2. This switchable first clutch can interrupt or establish the transmission of torque from the first engine 52. Based on the arrangement of the switchable first clutch 66 after the functional transmission mechanism 62 in the torque path of the first engine 52, the switching state of the switchable first clutch 66 has no effect on the torque transmission from the first engine 52 to the functional transmission mechanism 62.

[0095] A switchable second clutch 68 is arranged between the observer and the second engine 54 in Figure 2, by means of which the transmission of torque of the second engine 54 can be interrupted or established.

[0096] A work drive mechanism 70 is arranged between the observer in Figure 2 and a switchable clutch on one hand and a milling roller 32 on the other hand. The work drive mechanism includes a traction drive mechanism and, more precisely, a belt drive mechanism as a force transmission connection in the illustrated embodiment.

[0097] The working drive mechanism 70 includes three reversing rollers and a belt 78, which closes around the three reversing rollers. A belt tensioner 79 provides sufficient tension to the belt 78 and sufficient clamping force in the area surrounding the reversing rollers in a known manner. The first reversing roller 72 is connected to the first motor 52 via a switchable first clutch 66 and rotates together; the second reversing roller 74 is connected to the second motor 54 via a switchable second clutch 68 and rotates together; and the third reversing roller 76 is connected to the milling roller 32.

[0098] Here, the diameters of the three reversing rollers are chosen such that there is a different transmission ratio between the first reversing roller 72 and the third reversing roller 76 than between the second reversing roller 74 and the third reversing roller 76, which reduces the rotational speed and increases the torque.

[0099] Figures 1 through 3 are not shown to scale. They are for illustrative purposes only. For example, the second reversing roller 74 has a larger diameter than the first reversing roller 72, such that the speed reduction of the second engine 54 toward the milling roller 32 is less than the speed reduction of the first engine 52 toward the milling roller. Preferably, the speed of the first engine 52 is reduced to, for example, between one-eighteenth and one-twentieth of its value along the milling axis R and on the milling roller 32. The speed of the second engine 54 is reduced to, for example, between approximately one-fourteenth and one-sixteenth of its value along the milling axis R and on the milling roller 32.

[0100] The working drive mechanism 70 may have another planetary drive mechanism 80 with reduced rotational speed disposed between the third reversing roller 76 and the milling roller 32, which contributes to the aforementioned gear ratio. The different gear ratios for the first engine 52 and the second engine 54 are preferably achieved only through the reversing roller. The planetary drive mechanism 80 transmits torque from the third reversing roller 76 to the milling roller 32 at the same gear ratio, regardless of which engine is currently providing working drive power.

[0101] Figure 3 shows the components in Figure 2, excluding the belt tensioner 79, in a top view.

[0102] As generally schematically shown, the first engine 52 is connected to the functional transmission mechanism 62 or to the switchable second clutch 68 via a first flexible shaft connector 82 and the second engine 54 via a second flexible shaft connector 84. The flexible shaft connector can be any device suitable for compensating for radial misalignment between the end regions of the rotating shafts, such as a universal joint or an elastomeric clutch. Because the flexible shaft connector can compensate for certain radial misalignment in the torque paths of the first engine 52 and the second engine 54, such as radial misalignment caused by the elastic engine bearing 60, the switchable first clutch 66 and the switchable second clutch 68 can be non-rotatably connected to the first reversing roller 72 or the second reversing roller 74 via rigid drive shafts 86 or 88, respectively.

[0103] The second hydraulic pump, serving as both an additional functional device and an additional power receiver, can be directly housed within the housing 90 of the functional transmission mechanism 62. This is even a preferred option.

[0104] To maximize structural space while maintaining transport dimensions that allow movement without special permission, both engines are equipped with crankshafts extending parallel to the lateral mechanical direction Q. This preferred arrangement applies not only to this embodiment but is also a general principle.

[0105] Similarly, it is also preferred in principle that the crankshafts of the two engines are arranged parallel to the milling axis R. It is also preferred in principle that the axes of rotation of all other rotatable components of the working transmission mechanism 70, i.e., the reversing rollers, and all other rotatable components of the functional transmission mechanism 62 are parallel to each other and preferably parallel not only to the milling axis R but also to the crankshaft arrangement of the first engine 52.

[0106] The control console 26, serving as a control device, allows the milling roller 32 to operate in three different operating modes: for example, when the speed requirement of the milling roller 32 is low, the milling roller 32 is driven only by the first engine 52, wherein the exemplary functional devices 64 and 89 are also operated via the functional transmission mechanism 62 at this time; when the speed requirement of the milling roller 32 is high, the milling roller 32 is driven only by the second engine 54, wherein the first engine 52 operates the exemplary functional devices 64 and 89 via the functional transmission mechanism 62 as before; and when the power requirement of the milling roller 32 is particularly high, the milling roller 32 is driven by both engines.

[0107] The control unit can autonomously select the operating mode via input from the operator through the operation display 27, depending on how the operator determines the characteristics of the surface U to be machined, especially its hardness, and the desired milling depth and feed rate. Alternatively, the control unit can derive the characteristics of the surface to be machined from the detected operating parameter values ​​themselves and incorporate these characteristics into the control of the milling rollers 32 and / or both engines. For this purpose, a corresponding database can be stored in the control unit, which associates the parameters characterizing the surface to be machined, as well as the desired milling parameters—feed rate and depth of cut—with the operating parameters of the first engine 52 and the second engine 54. The control unit selects the operating mode, in particular, by correspondingly switching a switchable clutch.

[0108] For example, when the milling roller 32 needs to be driven by both generators, the control device can first determine the target speed of the first engine 52 for the corresponding milling task. Because the control device has access to a database that stores the engine power of the first engine 52 and the transmission ratio of the milling roller 32, the control device can calculate the required speed of the first engine 52 for this purpose from the desired speed of the milling roller 32.

[0109] If the second engine 54 is torque-adjustable, the control unit adjusts the first engine 52 to the target speed, wherein the control unit detects the speed of the first engine 52 by means of a speed sensor 92.

[0110] At or near the target speed, the control device detects the torque output by the first engine 52 via, for example, a torque sensor 96 that may be arranged in a switchable first clutch 66.

[0111] The control unit then begins to adjust the torque of the second engine 54. For this purpose, the control unit uses the detected torque output from the first engine 52 as a basis and reduces its value by a predetermined amount. This reduction in torque can be achieved additively by subtracting a predetermined torque difference, i.e., by adding a negative difference, or multiplicatively by multiplying by a factor less than 1.

[0112] Therefore, the control unit determines the torque value that the second engine 54 needs to output. Using the torque sensor 98 in the switchable second clutch 68, the control unit then adjusts the second engine 54 to output the theoretical torque.

[0113] Alternatively, the second engine 54 can also be speed-adjustable, just like the first engine 52.

[0114] The adjustment begins with a target rotational speed for the first engine 52, derived from the theoretical milling roller speed. Based on this theoretical milling roller speed, the control device also determines a target rotational speed for the second engine 54 according to the transmission ratio of the working transmission mechanism 70 for the second engine 54. In the illustrated embodiment, the first engine 52 is always faster than the second engine 54 when the milling roller speeds are the same.

[0115] The two target speeds are finalized by the control device before application to achieve the most stable regulated operation. Here, the numerical difference between the target speeds derived from the theoretical milling roller speed is increased. This can be achieved, for example, by increasing the target speed of the first engine 52 by 15U / min or decreasing the target speed of the second engine 54 by 15U / min, or by increasing the target speed of the first engine 52 and decreasing the target speed of the second engine 54, for example, by increasing the overall target speed difference by 15U / min. The control device then adjusts the first engine 52 and the second engine 54 to their finalized target speeds while simultaneously operating speed sensors 92 and 94.

[0116] In the described embodiment, the first engine 52 is an engine with an always adjustable speed, and the adjustment of the second engine 54 assists the operation of the first engine. It is also possible that, with the same working transmission mechanism 70, the second engine 54 is an engine with an always adjustable speed, and the first engine 52 is adjusted according to any of the methods described above while maintaining the indicated adjustment basis.

[0117] In the illustrated embodiment, the functional transmission mechanism 62 is continuously distributed to the first engine 52 at a larger speed reduction ratio. In contrast, the functional transmission mechanism 62 can be continuously distributed to the second engine 54 at a smaller speed reduction ratio.

[0118] It should be added that the belt tensioner 79 may have a motor-driven roller 79a and can therefore be used as a secondary drive during maintenance work on the milling roller 32. This allows the milling roller to rotate at a low speed, enabling visual inspection of the outer side of the milling roller and repair or replacement of components requiring repair or replacement, such as milling chisels, chisel holders, or chisel replacement holders. However, milling operations using the belt tensioner 79 as a secondary drive are not possible due to the excessively low drive torque of the belt tensioner 79.

Claims

1. A self-propelled ground processing machine (10), the self-propelled ground processing machine comprising a mechanical frame (12), the mechanical frame being supported by a traveling mechanism (22), wherein, The traveling mechanism (22) is erected on the ground (U) and has multiple traveling mechanisms that can roll on the ground (U). A working device, configured for ground processing as a first power receiver, is housed on the mechanical frame (12). The working device is driven to perform working movements relative to the mechanical frame (12). At least one functional device (64, 89), different from the working device, is housed on the mechanical frame (12) as another power receiver. A drive assembly (39) is housed on the mechanical frame (12) providing working drive power for the working device of the ground processing machine (10) and functional drive power for at least one functional device (64, 89). A working transmission mechanism (70) is provided between the drive assembly (39) and the working device to transmit torque between the drive assembly (39) and the working device. A functional transmission mechanism (62) is provided between the drive assembly (39) and the at least one functional device (64, 89) to transmit torque between the drive assembly (39) and the at least one functional device (64, 89), wherein the drive assembly (39) includes a first engine (52) and a second engine (54), wherein each engine is connected to the working device via the working transmission mechanism (70) to transmit torque, such that the working device is driven to perform working motions by the first engine (52) alone, or by the second engine (54) alone, or by both the first engine (52) and the second engine (54) together to perform a prescribed ground processing, characterized in that the working transmission mechanism (70) connects the first engine (52) to the working device at a first transmission ratio and connects the second engine (54) to the working device at a second transmission ratio different from the first transmission ratio.

2. The self-propelled ground processing machine (10) according to claim 1, characterized in that, Different transmission ratios of the working transmission mechanism (70) are caused by the interaction of rotary transmission members with different working diameters with the first engine (52) and the second engine (54), wherein the first rotary transmission member with a first working diameter is connected to the first engine (52) to rotate together, and wherein the second rotary transmission member with a second working diameter different from the first working diameter is connected to the second engine (54) to rotate together, wherein the first rotary transmission member is located between the first engine (52) and the second rotary transmission member in the torque path from the first engine (52) to the second rotary transmission member, and wherein the second rotary transmission member is located between the second engine (54) and the first rotary transmission member in the torque path from the second engine (54) to the first rotary transmission member.

3. The self-propelled ground processing machine (10) according to any one of claims 1 or 2, characterized in that, The working transmission mechanism (70) includes or may include a traction transmission mechanism.

4. The self-propelled ground processing machine (10) according to claim 2, characterized in that, The working transmission mechanism (70) includes or is a traction transmission mechanism, wherein the first rotary transmission member is at least one of the following transmission members i) a first reversing roller (72) that reverses the traction member of the traction transmission mechanism and ii) a first gear or friction wheel arranged in the torque path from the first engine (52) to the first reversing roller (72), or / and the second rotary transmission member is at least one of the following transmission members iii) a second reversing roller (74) that reverses the traction member of the traction transmission mechanism and iv) a second gear or friction wheel arranged in the torque path from the second engine (54) to the second reversing roller (74).

5. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, A switchable first clutch (66) is arranged in a first torque path between the first engine (52) and the working device to open or close the first torque path according to the switching state of the switchable first clutch (66), and / or a switchable second clutch (68) is arranged in a second torque path between the second engine (54) and the working device to open or close the second torque path according to the switching state of the switchable second clutch (68).

6. The self-propelled ground processing machine (10) according to claim 5, characterized in that, For one of the first engine (52) and the second engine (54), a switchable clutch arranged in the torque path between the engine and the working device interrupts the torque transmission from the engine to the working device in relation to its switching state, but does not interrupt the torque transmission from the engine to the functional transmission mechanism (62). For the other engine of the first engine (52) and the second engine (54), a switchable clutch arranged in the torque path between the other engine and the working device interrupts the torque transmission from the other engine to the working device and to the functional transmission mechanism (62) in relation to its switching state.

7. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, The functional transmission mechanism (62) is a transfer case, and the number of output shafts of the transfer case is greater than the number of input shafts of the transfer case.

8. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, The at least one functional device (64, 89) includes at least one liquid pump and / or at least one gas pump and / or at least one generator and / or at least one mechanical auxiliary drive.

9. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, The working device includes milling rollers (32) configured and arranged for removing the surface by rotating about the milling axis (R).

10. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, The working transmission mechanism (70) transmits the power of the first engine (52) and the second engine (54) to the working device while reducing the rotational speed and increasing the torque output at the corresponding rotational speed.

11. A method for operating a self-propelled ground processing machine (10) according to any one of claims 1 to 10 via a control device (26) of the ground processing machine (10), wherein, The first engine (52) and the second engine (54) simultaneously output power to the working device, the method comprising a) adjusting one of the two engines (52 and 54) to a target speed determined by taking into account user input and / or at least one detection value of sensors (92, 94, 96, 98) and / or query data relationships, b) adjusting the other engine of the two engines (52 and 54) to a motion variable selected from speed and torque, wherein the difference ratio between the value of the motion variable of the other engine and the value of the same motion variable of the speed-adjustable engine is different from the difference ratio between the first transmission ratio and the second transmission ratio of the working transmission mechanism (70).

12. The method according to claim 11, characterized in that, The corresponding other engine is also speed-adjustable via a control device (26), wherein the control device determines a first intermediate target speed of the first engine (52) based on the theoretical operating speed of the working device determined by user input and / or by at least one detection value of sensors (92, 94, 96, 98) and / or by querying data relationships, taking into account the transmission ratio of the working transmission mechanism (70) of the first engine (52), and a second intermediate target speed of the second engine (54) determined by taking into account the transmission ratio of the working transmission mechanism (70) of the second engine (54), wherein, in the final determination method, the control device changes the values ​​of the first and / or second intermediate target speeds to the first and second target speeds, such that the numerical difference between the final determined first target speed and the final determined second target speed according to the final determination method is greater than the numerical difference between the first and second intermediate target speeds calculated solely by the theoretical operating speed of the working device and the transmission ratio of the working transmission mechanism (70).

13. The method according to claim 11, characterized in that, The other engine is torque adjustable via a control device (26), wherein the control device (26) determines the torque output by the speed-adjustable engine, and wherein the theoretical torque of the torque-adjustable engine is selected by the control device (26) to be lower than the torque of the speed-adjustable engine, wherein the difference between the output torque of the speed-adjustable engine and the theoretical torque of the other torque-adjustable engine is different from the difference between the transmission ratios of the working transmission mechanisms (70) of the first engine (52) and the second engine (54).

14. The method according to any one of claims 11 to 13, characterized in that, The control device (26) enables the self-propelled ground processing machine (10) to operate in at least the following three operating modes: 1) only one of the first engine (52) and the second engine (54) transmits torque to the working device via the working transmission mechanism (70) and the other engine of the first engine (52) and the second engine (54) transmits torque to at least one functional device (64, 89) via the functional transmission mechanism (62); 2) both engines of the first engine (52) and the second engine (54) transmit torque to the working device via the working transmission mechanism (70); 3) only one of the first engine (52) and the second engine (54) transmits torque to the working device via the working transmission mechanism (70) and to at least one functional device (64, 89) via the functional transmission mechanism (62), while the corresponding other engine of the first engine (52) and the second engine (54) is turned off.

15. The self-propelled ground processing machine (10) according to any one of claims 1, 2 or 4, characterized in that, The self-propelled ground processing machine has a control device (26) and is used to perform the method according to any one of claims 11 to 14.

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