Self-propelled soil cultivation machine with combined heat exchanger cooling and engine compartment ventilation

Abstract

Self-propelled soil cultivation machine (10), such as road milling machine (10), surface miner or stabilizer, comprising: - a chassis (24) by means of which the soil cultivation machine (10) can roll onto a surface (U), and - a machine frame (30) supported by the chassis (24), - a power source (32) mounted on the machine frame (30) to provide power which can be used for driving and / or soil cultivation operation of the soil cultivation machine (10), - a working device (12) for soil cultivation mounted on the machine frame (30), - a cooling device (34) for cooling at least one functional device (25, 32) of the soil cultivation machine (10), wherein the cooling device (34) comprises: - at least one heat exchanger arrangement (46), comprising at least one heat exchanger (46a, 46b) designed for transferring heat from a cooling medium to air, and - a fan arrangement (48) which is designed and arranged, on the one hand, to generate a cooling airflow (KL) passing through the heat exchanger arrangement (46) and, on the other hand, to generate a ventilation airflow (LL) flowing away from the power source (32) in the region of the power source (32), characterized in that the heat exchanger arrangement (46) and a ventilation volume (32a), in which the ventilation airflow (LL) flows away from the power source (32), are arranged on the suction side of the fan arrangement (48), wherein the ventilation volume (32a) is arranged downstream of the heat exchanger arrangement (46) with respect to the cooling airflow (KL), so that the ventilation airflow (LL) generated by the fan arrangement (48) meets the cooling airflow (KL) downstream of the heat exchanger arrangement (46) and upstream of the fan arrangement (48).

Description

[0001] The present invention relates to a self-propelled soil tillage machine, such as a road milling machine, in particular a cold road milling machine, a surface miner, or a stabilizer. The soil tillage machine comprises: - a chassis by means of which the soil tillage machine can roll onto a surface, and - a machine frame supported by the chassis, - a power source mounted on the machine frame to provide power which can be used for driving and / or soil tillage operations of the soil tillage machine, - a working device for soil cultivation mounted on the machine frame, - a cooling device for cooling a functional device of the soil tillage machine, the cooling device comprising: - at least one heat exchanger arrangement comprising at least one heat exchanger which is designed to transfer heat from a cooling medium to air, and - a fan arrangement which, on the one hand, is designed and arranged to generate a cooling air flow passing through the heat exchanger arrangement and which, on the other hand, is designed and arranged to generate a ventilation air flow flowing away from the power source in the region of the power source.

[0002] Such a soil tillage machine in the form of a road milling machine is known from DE 10 2014 008 749 A1. This document discloses, in particular, the arrangement of both an internal combustion engine as the power source and the cooling device mentioned above between a driver's cab and the rear of a cold road milling machine. The known heat exchanger arrangement comprises two heat exchangers belonging to different cooling circuits. In a first cooling circuit, a cooling medium circulates between a heat exchanger and the internal combustion engine and releases heat at the heat exchanger that the cooling medium previously absorbed from the internal combustion engine. In a second cooling circuit, a hydraulic oil, which serves to operate hydraulic motors of the travel drive, circulates as the cooling medium that releases heat in the heat exchanger.The cooling air streams passing through the individual heat exchangers are strictly separated from one another by partition walls. This is because, due to the operating characteristics of the conventional cold milling machine, there is a certain degree of complementary thermal stress on the cooling medium of the internal combustion engine on the one hand and on the hydraulic oil on the other. In driving mode without soil cultivation, the internal combustion engine and its cooling medium are subjected to only a low thermal stress, whereas the hydraulic oil of the hydraulic motors providing the drive system is subjected to a high thermal stress. In soil cultivation mode with, compared to the previously mentioned driving mode, low driving speeds but with a high drive power of the milling drum of the cold milling machine, the hydraulic oil is subjected to only a low thermal stress, whereas the internal combustion engine and its cooling medium are subjected to a high thermal stress. Operation with a high drive power of the milling drum and simultaneous high driving speed practically never occurs in reality.This also applies to embodiments of the soil tillage machine of the present application, which preferably have a hydraulic motor drive and a milling drum as a working device.

[0003] DE 10 2014 008 749 A1 teaches the use of the fan arrangement both to supply cooling air to the heat exchangers and to extract air from an engine compartment. The engine compartment houses the internal combustion engine.

[0004] Specifically, DE 10 2014 008 749 A1 teaches, in one embodiment, arranging the heat exchangers and the internal combustion engine on the intake side of the fan assembly, and moving air extracted from the area of ​​the internal combustion engine, mixed with fresh air also drawn in, through the heat exchangers in a suction-like manner. Likewise, DE 10 2014 008 749 A1 teaches, in other embodiments, arranging the heat exchangers and the internal combustion engine on the pressure side of the fan assembly, and moving air drawn in by the fan assembly through the heat exchangers and past the internal combustion engine in a forced-action manner.

[0005] The first-mentioned technical teaching has the disadvantage that the air moving through the heat exchanger has a higher temperature than the pure fresh air sucked in due to the admixed heated air that was sucked in from the area of ​​the internal combustion engine, which reduces the heat transfer from the cooling medium to the air at the heat exchanger and thus its efficiency.

[0006] The second technical teaching has the disadvantage that fans operated with a push action are less efficient than fans operated with a suction action of the same power, and has the further disadvantage that on the pressure side, in particular the air moved with a push action towards the combustion engine flows along almost uncontrollable and unpredictable flow paths and escapes into the outside environment at arbitrary, often disadvantageous, locations on the soil tillage machine.

[0007] EP 3 081 421 B1 discloses another soil tillage machine designed as a drilling rig, in which an internal combustion engine as a heat source and a heat exchanger arrangement are arranged one behind the other on the suction side of the fan arrangement, specifically in the air flow generated by the fan arrangement. As a result, the fan arrangement conveys air heated by the internal combustion engine through the heat exchanger arrangement, which leads to the disadvantages described above. Due to the series arrangement, the internal combustion engine is in an environment with a significant negative pressure compared to the atmosphere throughout the entire fan operation. As a result, an above-average amount of dirt from the dust-laden construction site environment of the known soil tillage machine is conveyed almost continuously to the internal combustion engine.The fan arrangement known from EP 3 081 421 B1 is arranged obliquely with respect to a longitudinal axis of the fan duct carrying it in order to achieve the largest possible fan surface for a given duct cross-section.

[0008] DE 74 38 494 U discloses a cooling device with a box-shaped housing in which a flat heat exchanger is arranged in a vertical plane. A liquid heat exchange medium flows through the heat exchanger and has openings running transversely to its heat exchanger plane through which a gaseous medium can be passed. An axial fan is arranged in the housing, at a distance from the outlet side of the heat exchanger, the impeller of which is arranged in a plane inclined with respect to the vertical plane. This axial fan sucks in the gaseous medium flowing through the openings in the heat exchanger from the environment and directs it through the openings into the housing. The gaseous medium is released upwards into the environment through outlet openings in an upper housing shell running at right angles to the heat exchanger plane.The lower casing shell, which also runs approximately at right angles to the vertical heat exchanger plane, has a maintenance opening between the vertical heat exchanger plane and the inclined plane of the impeller of the axial fan, which is closed by a cover plate that can be removed downwards to remove the heat exchanger.

[0009] DE 10 2019 205 431 A1 discloses a cooling device for cooling an electrically powered motor vehicle. This cooling device comprises a first and a second heat exchanger, which are connected by an air duct. The air duct has two diametrically opposed, reversibly closable through-openings between the two heat exchangers. A cooling fan is arranged downstream of the second heat exchanger.

[0010] DE 10 2005 024 444 A1 discloses a cooling system for a motor vehicle with at least one radiator through which a coolant flows. An air flow can flow through the heat exchanger. When mounted on a vehicle, the radiator can be subjected to airflow at sufficient vehicle speed, or it can be forced through by a fan in suction mode. The fan is offset relative to the radiator, parallel to the air passage surface of the radiator, so that the fan projects laterally beyond the radiator when viewed from a direction orthogonal to its air passage surface.

[0011] DE 10 2005 031 474 A1 discloses another cooling system for a motor vehicle, which, like the aforementioned system, comprises a radiator through which a coolant flows. A fan is provided at a distance from the heat exchanger to direct air through the heat exchanger. The space between the heat exchanger and the fan is defined by a housing. The housing has at least one air passage area in the area between the heat exchanger and the fan that can be closed by a closing device.

[0012] It is therefore an object of the present invention to improve the soil tillage machine mentioned at the outset while eliminating the disadvantages mentioned above.

[0013] The present invention achieves this object on a soil tillage machine mentioned at the outset in that the heat exchanger arrangement and a ventilation volume, in which the ventilation air flow flows away from the power source, are arranged on the suction side of the fan arrangement, wherein the ventilation volume is arranged downstream of the heat exchanger arrangement with respect to the cooling air flow, so that the ventilation air flow generated by the fan arrangement strikes the cooling air flow downstream of the heat exchanger arrangement and upstream of the fan arrangement.

[0014] Using the arrangement of heat exchanger arrangement, fan arrangement and ventilation volume according to the invention, the fan arrangement is operated in a suction mode, which is not only the most effective operating mode of a fan arrangement, but which also ensures the possibility of determining where the air heated by the heat exchanger arrangement and / or by the power source can be blown away from the soil tillage machine.

[0015] Secondly, the ventilation airflow extracted from the ventilation volume of the power source and heated by the power source, whose temperature inevitably increases during operation, only encounters the cooling airflow after it has passed through the heat exchanger assembly. This ensures that the heat exchanger assembly is passed by the coolest possible airflow, which, due to the resulting higher temperature difference between the cooling medium flowing through the heat exchanger assembly and the passing airflow, ensures greater convective heat removal from the heat exchanger assembly than would be the case with the admixture of a heated ventilation airflow.

[0016] Likewise, the power source is efficiently ventilated, since the area around the power source, i.e. the ventilation volume which at least borders on the power source and preferably at least partially surrounds the power source, is not surrounded by air which was previously heated by heat transfer from the heat exchanger arrangement to the air.

[0017] Consequently, the heat exchanger arrangement can be operated effectively and the power source, which constantly heats up during operation, can be effectively ventilated.

[0018] A further advantage of the invention is that only a part of the total air volume conveyed by the fan arrangement is sucked in from the ventilation volume near the power source, whereby the negative pressure in the environment of the power source and thus the entry of dirt into this environment is reduced compared to the prior art according to EP 3 081 421 B1.

[0019] Preferably, the starting point of both the cooling air flow and the ventilation air flow is the outside environment and thus the ambient atmosphere of the soil tillage machine, without either air flow convectively absorbing heat from another functional device before reaching the heat exchanger arrangement or the power source. At most, air drawn in by the fan arrangement flows through a cover of the heat exchanger arrangement and / or a cover of the power source from the outside environment to the heat exchanger arrangement or the power source.

[0020] The power source is preferably an internal combustion engine, with a diesel engine being preferred as the internal combustion engine. Diesel internal combustion engines can be operated in a stationary mode with good efficiency and low emissions. However, it should not be ruled out that a gasoline engine or another type of thermal or electric engine is used as the power source, or that the power source comprises one or more fuel cells. The power source can, in particular, be an internal combustion engine with a turbocharger. The power source is, as it were, a power plant carried by the soil tillage machine, which provides the power required for its operation.In the case of a thermal engine as the power source, the soil tillage machine can comprise, in a manner known per se, one or more power converters which convert the power provided by the power source in one form into power provided in another form. For example, the working device for soil tillage can be mechanically driven by a mechanical output element of the power source, such as a crankshaft, with the interposition of gears. Likewise, a hydraulic pump can be operated, for example via a power take-off shaft of such a transmission, in particular a pump distribution gearbox, which converts the power provided by the power source into potential energy in the form of an increased pressure level of a hydraulic oil. Furthermore, power from the power source can be converted from mechanical power into electrical power via a generator.

[0021] According to a more generalized teaching of the present invention, instead of the power source, a heat source can be arranged separately from the heat exchanger arrangement, and preferably at a distance from it, from which the fan arrangement generates a ventilation airflow during operation to ventilate the heat source. The statements regarding the power source in the present application apply to the heat source, which can be, for example, an electrical energy storage arrangement or a transmission.

[0022] The working device for soil cultivation is preferably a soil-removing working device. This preferably involves a rotating working device with geometrically defined cutting edges, such as a milling drum, and / or with geometrically undefined cutting edges, such as a so-called "grinding drum" for the targeted texturing of soil surfaces.

[0023] In this case, a "passing" of the cooling air flow through the heat exchanger arrangement refers to any type of flow of the cooling air flow past the heat exchanger arrangement with convective dissipation of heat from the heat exchanger arrangement by the cooling air flow. When passing through the heat exchanger arrangement, the cooling air flow can flow in cocurrent or countercurrent along a heat transfer surface of the heat exchanger arrangement, in the same direction or opposite to the flow direction of a cooling medium flowing on the other side of the heat transfer surface. The heat exchanger arrangement is preferably a cross-flow heat exchanger arrangement, in which the cooling air flow flows transversely to the flow direction of the cooling medium flowing through the heat exchanger arrangement. The heat exchanger arrangement can have cooling channels carrying the cooling air flow for the cooling air flow to flow through.

[0024] In principle, it can be envisaged that the cooling air flow, on the one hand, and the ventilation air flow, on the other, are drawn in separately by the fan arrangement and, after passing through the fan arrangement, are discharged into the outside environment. However, a consistent separation of the two air flows requires the installation of corresponding flow channels, which represents increased effort and leads to complicated flow routing if the entire heat exchanger arrangement must always be accessible for the cooling air flow. Increased effort and complexity increase the susceptibility to failure. It is therefore preferable to provide a mixing volume between the heat exchanger arrangement and the fan arrangement in which the cooling air flow and the ventilation air flow mix.At the point at which the cooling air flow and the ventilation air flow mix, they have already fulfilled their task of heat dissipation as convective air flows and can be conveyed together and mixed as exhaust air through the fan arrangement on its pressure side and preferably blown out into the outside environment without having to fear any impairment of efficiency.

[0025] Consider filtering the exhaust air upstream or downstream of the fan assembly, i.e., placing an air filter through which the exhaust air flows in the exhaust air flow path. Since typically only air from the outside is drawn in and conveyed through the heat exchanger as a cooling air stream, or only air from the power source area is extracted, which usually receives air from the outside, the degree of contamination of both air streams is kept within limits, so that filtering of the air streams is not necessary either to protect the already robust fan assembly or to clean the exhaust air.

[0026] To facilitate assembly of the soil tillage machine, the soil tillage machine, in particular its cooling device, can have a pre-assembled airflow assembly, wherein the airflow assembly comprises the fan assembly, the heat exchanger assembly, and a frame supporting the fan assembly and the heat exchanger assembly. The airflow assembly can thus be easily pre-assembled at a separate assembly location and attached as a pre-assembled assembly to the soil tillage machine, in particular to its machine frame.

[0027] The frame can be a lattice frame with a plurality of bars to which the fan assembly and the heat exchanger assembly are mounted. A skeletal lattice frame is relatively lightweight. To enforce defined flow conditions, the frame can have a housing section that at least partially encloses the mixing volume. For this purpose, the frame can have a frame skin and, for this purpose, can be constructed and / or formed, for example, at least in sections, from sheet metal and / or plastic surfaces. This ensures that the fan assembly actually only or predominantly sucks in the cooling air flow passing through the heat exchanger assembly and the ventilation air flow drawn from the power source, but no false air from other areas of the soil tillage machine.This prevents the fan assembly from sucking in air from areas of the tillage machine that do not require convective cooling and / or ventilation.

[0028] To ensure that the cooling air flow and the ventilation air flow meet and can preferentially mix upstream of the fan arrangement but downstream of the heat exchanger arrangement, it is advantageous if the fan arrangement is arranged at a distance from the heat exchanger arrangement. Particularly good space utilization is achieved if the fan arrangement and the heat exchanger arrangement are rotationally displaced relative to one another about a pivot axis. Different areas of the fan arrangement, on the one hand, and the heat exchanger arrangement, on the other, are then at different distances from one another. For this reason, the flow paths from the heat exchanger arrangement to the fan arrangement are short. Additionally or alternatively, the fan arrangement and the heat exchanger arrangement can be arranged translationally displaced along a displacement axis.However, the translational displacement of the heat exchanger arrangement and fan arrangement generally requires more installation space than a rotational displacement.

[0029] To advantageously reduce the installation space required, the fan arrangement is preferably a substantially planar fan arrangement. “Planar” is not to be understood in a strictly mathematical sense, but rather such that the fan arrangement has considerably larger dimensions in two mutually orthogonal spatial directions than in a third spatial direction orthogonal to the aforementioned spatial directions, which third spatial direction is particularly preferably the flow direction of the fan arrangement, along which the exhaust air flows through the fan arrangement. A rotational axis of at least one fan of the fan arrangement preferably runs along the third spatial direction; preferably, if the fan arrangement comprises a plurality of fans, all rotational axes of the plurality of fans run along this third spatial direction. Alternatively, or preferably additionally, the heat exchanger arrangement is also a substantially planar heat exchanger arrangement.This also means that the heat exchanger arrangement has a substantially larger dimension along two mutually orthogonal spatial directions than in a third spatial direction orthogonal to the two spatial directions, which is preferably a flow direction along which the cooling air flow flows through the heat exchanger arrangement, which is preferably designed as a cross-flow heat exchanger arrangement.

[0030] When both the heat exchanger arrangement and the fan arrangement are each designed as planar arrangements, the pivot axis, about which the two arrangements are rotationally displaced relative to one another, preferably runs parallel to each design plane of the two arrangements.

[0031] The permeable surface of the heat exchanger arrangement is preferably larger than the permeable surface of the fan arrangement, so that the heat exchanger arrangement can provide the largest possible heat transfer surface. The permeable surface of a fan of the fan arrangement is preferably circular or annular so that it can approach a rotating fan impeller as closely as possible. If the fan arrangement has multiple fans, each permeable surface of a fan is preferably circular or annular.

[0032] In order to make the best possible use of the installation space provided for the installation of the heat exchanger arrangement, the flow-through surface of the heat exchanger arrangement is preferably rectangular.

[0033] When the fan arrangement and the heat exchanger arrangement are rotationally displaced relative to one another about the pivot axis, the rotational displacement angle is preferably between 65° and 115°, particularly preferably between 80° and 100°. By angling the two arrangements relative to one another by a displacement angle in an angular range around a right angle, a heat exchanger arrangement and a fan arrangement, each with relatively large flow-through areas, can nevertheless be arranged over a relatively small footprint. The above-mentioned air flow assembly can then have a roughly prismatic shape, for example with a mixing volume with a substantially triangular basic shape, wherein the mixing volume can be formed along one side by the fan arrangement, along a second side by the heat exchanger arrangement, and along a third side by a wall of the frame forming the housing section.

[0034] The fan assembly and the heat exchanger assembly can then be arranged spatially very compactly, in particular as a very compact airflow assembly, on the soil tillage machine if the ventilation airflow flows transversely to the flow direction of the cooling airflow passing through the heat exchanger assembly and / or transversely to an exhaust airflow flowing through the fan assembly toward the mixing volume. In the case of the coarsely prismatic airflow assembly mentioned above as an example, two airflows, preferably the cooling airflow and the exhaust airflow, can flow through the lateral surface of the coarsely prismatic airflow assembly, and one airflow, preferably the ventilation airflow, can flow through an end face of the coarsely prismatic airflow assembly.

[0035] For example, the housing section of the frame that at least partially encloses the mixing volume can have a through-opening spaced apart from both the heat exchanger assembly and the fan assembly, through which the ventilation air flow can flow. As previously explained, the housing section having the through-opening is preferably part of an end wall of a prismatic air flow assembly.

[0036] In principle, this through-opening can have a fixed cross-section, the shape and / or size and / or position of which can be optimized through appropriate testing. However, it is also conceivable to design a variable cross-sectional area of ​​the through-opening through which the ventilation air flow can flow in order to adapt the ventilation of the power source, for example depending on its operating state, in order to change the amount of ventilation air flowing in the ventilation air flow per unit time under given operating conditions. For this purpose, for example, the through-opening can have a diaphragm device with which the coverage of the through-opening by the diaphragm component can be varied by means of an actuator by displacing a diaphragm component relative to a component forming the through-opening.If the through-opening is formed on a housing section of the frame of the air flow assembly, the diaphragm device, in particular the diaphragm component movable relative to the through-opening, is preferably also received on the frame, in particular on the housing section of the frame, of the air flow assembly.

[0037] During operation of the soil tillage machine, the amount of cooling air required per unit of time is generally greater, often significantly greater, than the amount of ventilation air required in the same unit of time. A large portion of the air volume conveyed by the fan arrangement therefore flows through the heat exchanger arrangement. The ventilation air flow usually serves only to ventilate the power source to prevent heat buildup in its surroundings. The cooling air flow, on the other hand, generally serves to specifically dissipate a certain amount of heat in order to maintain thermal equilibrium in the at least one functional device cooled by the heat exchanger arrangement during operation of the soil tillage machine.

[0038] The heat exchanger arrangement can have a plurality of heat exchangers, which are preferably components of different cooling circuits and / or cooling passages for cooling functional devices on the soil tillage machine. The respective cooling medium of different cooling circuits and / or cooling passages can then advantageously be convectively cooled at one and the same location. For example, a cooling circuit can run between a heat exchanger and the power source, a cooling circuit can run between a heat exchanger and a hydraulic oil tank, or a heat exchanger can act as an oil cooler through which hydraulic oil flows as the heat-emitting cooling medium. In a cooling passage, a heat exchanger can serve as a gas-to-gas intercooler of a turbocharger. In a cooling circuit, a heat exchanger can be part of a gas-to-liquid intercooler of a turbocharger. Likewise, a heat exchanger in a cooling circuit can be a transmission oil cooler.Different heat exchangers can therefore be flowed through by different cooling media. Two or more heat exchangers can also be flowed through by the same cooling medium, but circulating in separate cooling circuits and / or passing through separate cooling passages.

[0039] Likewise, the fan arrangement can comprise a plurality of fans to generate airflows of varying intensity in different areas of the fan arrangement, and in particular in the mixing volume. This can be advantageous if one heat exchanger from a plurality of heat exchangers requires a higher convective cooling capacity than other heat exchangers in the heat exchanger arrangement. Preferably, the fans of the fan arrangement can be controlled separately from one another, so that different airflow quantities can be generated simultaneously by the individual fans.

[0040] The soil tillage machine preferably has a control station from which the operation of the soil tillage machine can be controlled, regardless of whether it is predominantly driving without soil tillage or predominantly working with only a low driving performance. The heat exchanger arrangement and the fan arrangement can then be arranged between the control station and the front longitudinal end of the soil tillage machine, so that the advantageous cooling device described above can also be used on compact milling machines whose working device, designed as a milling drum, is arranged in the area of ​​the rear of the soil tillage machine, in particular below and / or behind the control station.

[0041] In principle, it is possible to install a ventilation duct carrying the ventilation airflow from the power source to the cooling device. Such a ventilation duct would then define part of the ventilation volume. However, this generally means an increase in the flow resistance for the ventilation airflow and additional assembly effort. Therefore, the heat exchanger arrangement and the fan arrangement of the power source are preferably arranged directly adjacent to each other. Particularly preferably, there is no further functional device between the power source and the cooling device, in particular the airflow assembly, so that the fan arrangement can draw air directly into the ventilation volume as a ventilation airflow.According to this preferred embodiment, the ventilation volume can, on the one hand, be adjacent to the power source and even at least partially surround it without forming a channel-shaped line, and, on the other hand, the ventilation volume can be adjacent to the passage opening to the mixing volume.

[0042] To avoid any interference with the machine operator on a control station lagging behind the power source in the forward direction of travel, it is preferable for the heat exchanger arrangement to be located closer to one side of the soil tillage machine in the transverse direction of the machine, and for the fan arrangement to be located closer to the other side opposite in the transverse direction of the machine. This allows, in particular, an exhaust air flow with a flow component in the transverse direction of the machine to be blown off laterally from the soil tillage machine. The control station then does not pass through the exhaust air flow when traveling forward.

[0043] To facilitate observation of the soil cultivation process, the operator's station is preferably offset laterally, i.e., in the transverse direction of the machine, relative to the central longitudinal axis of the machine. To avoid exposure of the operator's station to the exhaust air flow, its discharge point is preferably located closer to, particularly preferably on, that side of the soil cultivation machine from which the operator's station is offset. In other words, the discharge point is preferably located closer to, particularly on, that side of the soil cultivation machine from which the operator's station is further away.

[0044] The arrangements, which are preferably displaced relative to one another in a rotational manner: fan arrangement and heat exchanger arrangement, can form a ridge, whereby the ridge line also preferably runs parallel to the longitudinal axis of the machine.

[0045] In other words, a load on the operator's platform caused by the operation of the cooling device can be avoided if the cooling air flow passing through the heat exchanger arrangement has a flow component in the cross-machine direction and a flow component in the machine height direction and / or if an exhaust air flow flowing through the fan arrangement has a flow component in the cross-machine direction and a flow component in the machine height direction. Due to the above-described preferred ridge-forming arrangement of the heat exchanger arrangement and fan arrangement, which can be achieved in particular by the above-described roughly prismatic shape of the air flow assembly, the flow components of the cooling air flow on the one hand and the exhaust air flow on the other hand running in the machine height direction are preferably directed in opposite directions. The flow components in the cross-machine direction, in contrast, are preferably directed in the same direction.The ventilation air flow then flows preferentially along the machine's longitudinal axis into the mixing volume of the cooling device.

[0046] To protect against external influences, the heat exchanger assembly and / or the fan assembly and / or the power source can be covered by a cover. The cover preferably has openings to ensure accessibility of the cooling device and / or the power source to ambient air.

[0047] When the soil tillage machine is in the operational state, a separating device can be arranged on a side of the heat exchanger assembly facing the cover of the heat exchanger assembly, said separating device separating a flow path from flow-through openings in the cover to the heat exchanger assembly from the surroundings of the flow path in at least one direction transverse to the flow path. The separating device preferably extends from the cover to the heat exchanger assembly. The separating device is preferably a shaft wall that runs continuously around the flow path and separates a shaft surrounded by it as a flow path or flow channel from the surroundings located outside the shaft wall. This essentially ensures that upstream of the heat exchanger assembly, only ambient air from the outside environment of the soil tillage machine is drawn in as a cooling air stream.

[0048] The separating device is preferably connected to the cover for joint movement, so that the separating device is also removed from the cooling device along with the cover and the cooling device, in particular the heat exchanger arrangement which is shielded against ingress of air by the separating device during operation, can be made accessible in a few simple steps.

[0049] The separator can be positioned against the side of the heat exchanger assembly facing the cover, with a sealing arrangement, such as an elastomeric seal surrounding the flow path, interposed. The sealing arrangement can be foamed, open- or closed-cell, or solid.

[0050] The side of the heat exchanger assembly facing the cover can have a contact surface, preferably a contact frame surrounding a surface through which the cooling air flow can flow. The separating device can then rest against the contact surface when the soil tillage machine is in the operational state, preferably with the sealing arrangement interposed.

[0051] The sealing arrangement may be permanently connected to the heat exchanger arrangement or to the separator. The sealing arrangement may comprise partial sealing assemblies, each of which is permanently connected to a different structure comprising the heat exchanger arrangement and the separator.

[0052] To ensure good mixing of the cooling air flow and the ventilation air flow, thus ensuring that the fan assembly is thermally homogeneously loaded by the exhaust air flowing through it, the mixing volume is preferably larger than the volume occupied by the heat exchanger assembly. Due to the often complex structure of a heat exchanger assembly, the volume defined by an envelope surface that closely encloses the heat exchanger assembly should be sufficient to determine its volume.

[0053] In relation to the volume of the heat exchanger arrangement through which the cooling air flow can actually flow, the mixing volume is preferably at least twice, particularly preferably at least three times, the volume through which the heat exchanger arrangement can flow, so that the cooling air flow can mix sufficiently with the ventilation air flow after passing through the heat exchanger arrangement.

[0054] To clean the cooling device, the fan arrangement can be designed to temporarily reverse the direction of rotation of at least one fan, preferably all fans, for an interim cleaning operation compared to the conventional cooling operation. During the cleaning operation, the fan arrangement conveys air through the fan arrangement into the mixing volume. Thus, during the cleaning operation, the fan arrangement can free the heat exchanger arrangement and / or a cover of the heat exchanger arrangement of dust and other contaminants, which can accumulate primarily on the side of the heat exchanger arrangement facing the outside environment of the soil tillage machine.

[0055] A cleaning airflow generated during cleaning operation, which flows through the fan assembly in the opposite direction to the exhaust airflow, can be utilized particularly efficiently if, as shown above, a closable passage opening is provided between the mixing volume and the ventilation volume. With the passage opening closed, the entire cleaning airflow can then be directed through the heat exchanger assembly and clean it.

[0056] The above applies to the intended cooling operation of the cooling device during soil cultivation or driving operation: the fan assembly generates a cooling air flow and a ventilation air flow, which flow towards the fan assembly, and blows the cooling air flow and the ventilation air flow out as exhaust air flow through the fan assembly.

[0057] Although the heat exchanger arrangement is preferably the only heat transfer device passed through by the cooling air flow, and the power source, possibly with additional units arranged thereon, such as a turbocharger, is the only heat source of the ventilation air flow extracted from its surroundings, it should not be ruled out in principle that the cooling air flow, after having passed through the heat exchanger arrangement, and / or the ventilation air flow, after having moved sufficiently away from the line source, passes through another heat transfer device and absorbs heat from it. It is crucial that the additional heat transfer device does not heat any air that still has to pass through the heat exchanger arrangement and / or that flows into the surroundings of the power source and there transfers heat to the power source, or that hinders heat transfer from the power source to the air surrounding the power source.The aim of the present invention is namely that the heat exchanger arrangement can be passed by ambient air that has not been additionally heated and that the power source can be ventilated by ambient air that has not been additionally heated. Inevitable heat sources, such as the passage of ambient air through a heated cover or casing of the soil tillage machine, are not taken into account. Thus, for example, with respect to the cooling air flow, a further heat transfer device can be arranged downstream of the heat exchanger arrangement, through which the cooling air flow and / or the ventilation air flow passes, for example in the mixing volume. Additionally or alternatively, with respect to the ventilation air flow, a further heat transfer device can be arranged downstream of the power source, through which the cooling air flow and / or the ventilation air flow passes, for example in the mixing volume, in the passage opening, or immediately in front of or behind the passage opening.The through-opening can be an inlet or outlet aperture for the additional heat transfer device. The arrangement of an additional heat transfer device in the ventilation airflow does not change the fact that, as stated, the ventilation airflow meets the cooling airflow downstream of the heat exchanger arrangement and upstream of the fan arrangement. The additional heat transfer device can be an active heat transfer device through which a heat-emitting medium flows, or it can be a heat-conducting heat sink that is thermally connected to a component to be cooled.

[0058] The present invention will be explained in more detail below with reference to the accompanying drawings. It shows: Fig. 1 a perspective view of a compact milling machine from the rear, Fig. 2 the perspective view of the compact milling machine from Fig. 1 without cover, Fig. 3 a perspective view of the air flow assembly of the cooling device of the compact milling machine of the Fig. 1 and Fig. 2, and Fig. 4 a side view of the airflow assembly of Fig. 3.

[0059] In the Fig. 1 and Fig. 2 shows a cold road milling machine in a purely exemplary form of a compact milling machine, viewed obliquely from the rear and generally designated 10. In the specifically illustrated compact milling machine, the working device 12 is located in a milling drum housing 14 in the rear area of ​​the cold road milling machine 10, approximately below an operator's platform 16 arranged asymmetrically offset from the right side of the machine in the forward direction of travel. This operator's platform is accessible via a ladder 17 at the rear of the machine and from which the operation of the cold road milling machine 10 can be controlled by a machine operator. Visible at the rear of the cold road milling machine 10 is a scraper blade 14a, which can be raised and lowered via a piston-cylinder actuator 15 and forms the rear wall of the milling drum housing 14.

[0060] The machine operator can sit on a driver's seat 20 to operate a control panel 18 and is protected from precipitation and solar radiation by a protective roof 22 that can be moved along the machine height axis H of the cold road milling machine 10.

[0061] The road cold milling machine 10 is mounted on a chassis 24, which in the example shown comprises four track drives 26, on a support structure which is only symbolically shown for the sake of clarity. Fig. 1. The subsoil U can be processed by the working device 12 in an abrasive manner. Instead of tracked drives 26, wheeled drives can also be provided. In any case, a rotating axis around which the rotating component of the respective drive rotates, be it chain or wheel, runs parallel to the surface of the subsoil U, so that the drives, here: tracked drives 26, can roll on the subsoil U when the road cold milling machine 10 is in operation.

[0062] With the milling drum mounted in the milling drum housing 14 in the illustrated application example as the working device 12, which rotates about a rotation axis parallel to the machine's transverse direction Q, material can be removed from the soil to be worked. The chassis 14, with the steerable track drives 26, each individually driven by hydraulic motors 25 in the illustrated embodiment, provides the propulsion of the cold road milling machine 10 and thus the advance of the working device 12, particularly during soil removal.

[0063] The chassis 24 carries a machine frame 30 (see Fig. 2), which carries functional devices of the cold road milling machine 10. The functional devices include the already mentioned working device 12 together with the milling drum box 14, the control panel 18, the hydraulic motors 25, a diesel engine 32 (see Fig. 2) as a power source within the meaning of the introduction to the description, a cooling device 34 (see Fig. 2), a cover 36, to name just a few examples of functional devices.

[0064] The internal combustion engine 32 is surrounded by an air-filled ventilation volume 32a, the air of which is heated by the internal combustion engine 32 during its operation due to convection and radiation.

[0065] In Fig. 1, an intake opening area 38 and a blow-out opening area 40 are formed on the cover 36, in which the cover 36 is perforated by openings to allow the passage of air between an outer side of the cover 36 and an opposite inner side. The cooling device 34 can suck in air from the outside environment of the cold road milling machine 10 through the openings of the intake opening area 38, which air is fed back into the outside environment of the cold road milling machine 10 after passing through the cooling device 34 through the openings of the blow-out opening area 40. The intake takes place, or the intake opening area 38 is located predominantly on the top side of the cover 36 and on the right-hand side of the machine in the forward direction of travel V. The blow-out takes place, orthe blow-out opening area 40 is located predominantly or even completely on the opposite side of the machine in the cross-machine direction Q and on the left side of the machine in the forward direction V.

[0066] For the sake of completeness, it should be noted that on the front side of the cold road milling machine 10 opposite the rear of the machine in the machine longitudinal direction L, there is a bearing formation 42 carried by the machine frame 30 for supporting a material transport device, not shown, but present during soil cultivation, for loading the milled material, in particular a conveyor belt.

[0067] As in Fig. 2 with the cover 36 removed, the cooling device 34, designed as a pre-assembled airflow assembly 44, comprises a heat exchanger arrangement 46 and a fan arrangement 48 with two fans 48a and 48b arranged side by side, for example. Unlike the example shown, the fan arrangement 48 may have only one fan or more than two fans, and the plurality of fans may be arranged in other spatial relationships to one another, for example, one above the other or diagonally offset from one another.

[0068] Likewise, the heat exchanger arrangement 46 has a first heat exchanger 46a, through which a cooling medium of the internal combustion engine 32 flows, in order to transfer heat, which it has previously absorbed in the internal combustion engine 32, to the air passing through the heat exchanger 46a. Furthermore, the heat exchanger arrangement 46 has a second heat exchanger 46b, which serves as a charge air cooler for a turbocharger 50 cooperating with the internal combustion engine 32. Thus, while the cooling medium flowing through the heat exchanger 46a is liquid, the cooling medium flowing through the heat exchanger 46b is gaseous. The heat exchanger arrangement 46 can have more or fewer heat exchangers than the two shown, 46a and 46b. For example, a further heat exchanger in the heat exchanger arrangement 46 can serve as a hydraulic oil cooler and be flowed through as a cooling medium by the hydraulic oil flowing through the hydraulic motors 25.The hydraulic oil can also be used to cool the hydraulic motors 25.

[0069] The two heat exchangers 46a and 46b may be arranged in a spatial relationship to one another other than that shown, for example, side by side along the longitudinal axis L of the engine, instead of one behind the other as shown. Instead of a gas-to-gas charge air cooler, the heat exchanger assembly 46 may comprise a gas-to-liquid heat exchanger as part of a charge air cooling system, with the charge air then transferring heat to a liquid cooling medium, which transfers the heat to the air passing through the heat exchanger assembly 46.

[0070] It can be seen in Fig. 2 the first cooling medium line 52a conveying the liquid cooling medium of the internal combustion engine 32 to the heat exchanger 46a and the second cooling medium line 52b conveying the gaseous cooling medium to the heat exchanger 46b.

[0071] The air flow assembly 44 is mounted directly on the machine frame 30 via a plurality of bearing formations 54 fixed to the machine frame, a total of four in the example shown.

[0072] The following is based on reference to Fig. 3 the airflow assembly 44 will be explained in more detail.

[0073] The air flow assembly 44 is connected via a total of four counter bearing formations 56, of which Fig. 3, only three are visible, are fixed to the bearing formations 54 of the machine frame 30. The counter-bearing formations 56 are fixed, for example, by welding, to a frame 58 made of a flat material, such as sheet metal. The frame 58 supports the heat exchanger assembly 46 and also the fan assembly 48.

[0074] It can be seen in Fig. 3 also the inlet connection 47a of the cooling medium into the heat exchanger 46a. The return connection 47b after the cooling medium has passed through the heat exchanger 46a is located on the opposite side of the heat exchanger 46a and is not in Fig. 3, but in Fig. 4 can be recognized.

[0075] Likewise, in Fig. 3 the inlet connection 53a of the charge air into the heat exchanger 46b and the return connection 53b of the charge air after passing through the heat exchanger 46b can be seen.

[0076] The housing-like frame 58 encloses, with a housing section 59, a mixing volume 60 between the heat exchanger arrangement 46 and the fan arrangement 48. The pre-assembled air flow assembly 44 has a roughly prismatic shape with a substantially triangular base. Two lateral surfaces of the triangular prism are formed by the heat exchanger arrangement 46 on the one hand and by the fan arrangement 48 on the other. A third lateral surface forms a bottom side of the housing section 59 and thus a boundary wall of the mixing volume 60. In the view directed at the viewer of Fig. 3 and Fig. 4 facing end face of the housing section 59 of the frame 58, a through-opening 62 is formed through which the mixing volume 60 can be fed from the outside, namely, as Fig. 2 shows, is accessible from the environment of the internal combustion engine 32, more precisely from the ventilation volume 32a.

[0077] The through-opening 62 is formed in a plate 64 mounted on the remaining end face of the housing section 59, which plate covers a passage that penetrates the end face of the housing section 59 supporting the plate 64. In this way, a passage can be provided as a kind of original through-opening with a maximum passage cross-section, which can be adapted to the respective application of the specific soil tillage machine by arranging the plate 64 with the through-opening 62 optimized for the respective application in terms of shape, position, and passage cross-section.

[0078] In the illustrated embodiment, the through-opening 62 is formed by a plurality of smaller elementary openings, for example, designed as bores penetrating the plate 64, which together form the through-opening 62. Furthermore, the through-opening 62 is formed in the plate 64 closer to one corner than to the other three corners in order to draw a ventilation air flow from the most optimal area of ​​the ventilation volume 32a around the internal combustion engine 32. Deviating from the illustration, the through-opening 62 can be formed by a single opening or by a smaller number of openings. It can also be formed at a different location in the plate 64.

[0079] As in Fig. As also shown in Figure 3, the two fans 48a and 48b are essentially identical and arranged with mutually parallel rotation axes Ra and Rb. The fan wheels of the fans 48a and 48b are preferably driven hydraulically or by an electric motor, with each fan 48a and 48b preferably being controllable or regulated separately from the other.

[0080] In the plan view of the end face of the housing section 59 of the frame 58, which is Fig. 4, it can be clearly seen that the heat exchanger arrangement 46 is a planar heat exchanger arrangement essentially in a plane relative to the plane of the drawing of the Fig. 4 orthogonal heat exchanger plane WE and that the fan arrangement 48 as a planar fan arrangement essentially in a plane to the drawing plane of the Fig. 4 is also arranged orthogonally to the fan plane LE. In the example shown, the heat exchanger plane WE and the fan plane LE form an angle of between 100° and 110°. They are arranged with respect to a plane orthogonal to the drawing plane of the Fig. 4 pivot axis SA and form a ridge F with a ridge line parallel to the pivot axis SA and the machine's longitudinal axis L. In the present case, the ridge F is formed by the uppermost edge of a support frame 74 in the machine height direction H. The support frame 74 surrounds a surface of the heat exchanger arrangement 46 through which the cooling air flow KL can flow for heat transfer. In the example shown, the support frame 74 runs completely closed around the surface of the heat exchanger arrangement 46 through which the cooling air flow KL can flow.

[0081] The heat exchanger plane WE and the fan plane LE are not infinitely thin planes in the mathematical sense, but are component planes which have a significantly smaller dimension in their respective thickness direction than in their two extension directions which are orthogonal to both the thickness direction and to each other.

[0082] In contrast to Fig. 3, the through hole 62' formed in the plate 64 is shown in Fig. 4 is formed as a single, continuous through-opening 62', which is, however, covered by a diaphragm 68 which is movable along two rails 66. The diaphragm 68 itself has a diaphragm opening 70 which passes through it and which can be brought into overlap with the through-opening 62' by moving the diaphragm 68 along the rails 66. This allows the flow-through cross-section of the through-opening 62' to be changed. The diaphragm 68 is movable by an actuator 72 between the Fig. 4, in which the aperture 68 completely closes the through-opening 62', and an open position in which the aperture 70 and the through-opening 62' completely overlap. Moving to intermediate positions is preferably possible. However, it can also be provided that the through-opening 62' is only either completely opened or completely closed by moving the aperture 68.

[0083] The fan arrangement 48 is provided on the cooling device 34 or on the air flow assembly 44 in such a way that the heat exchanger arrangement 46 and the through-opening 62 or 62' are located on the suction side of the fan arrangement 48. By operating the fan arrangement 48, a negative pressure with respect to the ambient atmosphere is generated on the suction side of the fan arrangement 48, which generates a cooling air flow KL from the outside through the heat exchanger arrangement 46 into the mixing volume 60. Likewise, when the through-opening 62 or 62' is open, the negative pressure generates a Fig. 4 orthogonal ventilation air flow LL from the outside through the through-opening 62 or 62' into the mixing volume 60, where the cooling air flow KL and the ventilation air flow LL coming from the area of ​​the internal combustion engine 32 can mix. The pressure difference generated by the fan arrangement 48 between its suction side and its pressure side also causes an exhaust air flow AL out of the mixing volume 60 through the fan arrangement 48.

[0084] The flow directions of the cooling air flow KL and the exhaust air flow AL, indicated by the associated arrows, which correspond to the respective thickness direction of the flow-through arrangement, preferably lie in one plane. This plane, in turn, is preferably inclined between 75° and 105° to the machine longitudinal direction L, in particular orthogonal to it. The flow direction of the ventilation air flow LL through the passage opening 62 or 62' runs transversely to the plane spanned by the flow directions of the cooling air flow KL and the exhaust air flow AL, in particular orthogonal to it.

[0085] This ensures that no air previously heated by the absorption of heat at the heat exchanger assembly 46 enters the area of ​​the internal combustion engine 32 and further heats the environment around the internal combustion engine 32 or prevents its cooling. Likewise, it ensures that no air heated by the internal combustion engine 32 flows through the heat exchanger assembly 46 and reduces the efficiency of the convective cooling of the cooling medium flowing through the heat exchanger assembly 46.

[0086] In the Fig. 3 and Fig. 4, a shaft wall 76 is shown in dashed lines as a separating device, which extends in the operational state of the soil tillage machine 10 from the cover 36 to the heat exchanger arrangement 46. The arrow KL in Fig.4 also symbolizes a flow path along which the cooling air flow KL flows from the openings 38 in the cover 36 to the heat exchanger assembly 46 and further through it. This flow path is located within the shaft wall 76 in a flow channel defined by the shaft wall 76 and separated from its external environment.

[0087] At its longitudinal end facing the heat exchanger assembly 46, the shaft wall 76 preferably has a counter-support frame 78, which, in the operational state of the soil tillage machine 10, lies opposite the support frame 74 with a seal 80 arranged therebetween. The preferably elastomeric seal 80 can be firmly connected to the support frame 76 or to the shaft wall 76, in particular to the counter-support frame 78.

Claims

[1] Self-propelled soil tillage machine (10), such as a road milling machine (10), surface miner or stabilizer, comprising: - a chassis (24) by means of which the soil tillage machine (10) rolls onto a base (U), and - a machine frame (30) carried by the chassis (24), - a power source (32) mounted on the machine frame (30) for providing power which can be used for driving operation and / or for soil cultivation operation of the soil cultivation machine (10), - a working device (12) for soil cultivation mounted on the machine frame (30), - a cooling device (34) for cooling at least one functional device (25, 32) of the soil tillage machine (10), wherein the cooling device (34) comprises: - at least one heat exchanger arrangement (46), comprising at least one heat exchanger (46a, 46b) which is designed to transfer heat from a cooling medium to air, and - a fan arrangement (48) which, on the one hand, is designed and arranged to generate a cooling air flow (KL) passing through the heat exchanger arrangement (46) and, on the other hand, is designed and arranged to generate a ventilation air flow (LL) flowing away from the power source (32) in the region of the power source (32), characterized byin that the heat exchanger arrangement (46) and a ventilation volume (32a), in which the ventilation air flow (LL) flows away from the power source (32), are arranged on the suction side of the fan arrangement (48), wherein the ventilation volume (32a) is arranged downstream of the heat exchanger arrangement (46) with respect to the cooling air flow (KL), so that the ventilation air flow (LL) generated by the fan arrangement (48) strikes the cooling air flow (KL) downstream of the heat exchanger arrangement (46) and upstream of the fan arrangement (48). [2] Self-propelled soil tillage machine (10) according to claim 1, characterized by that a mixing volume (60) is provided between the heat exchanger arrangement (46) and the fan arrangement (48), in which the cooling air flow (KL) and the ventilation air flow (LL) mix. [3] Self-propelled soil tillage machine (10) according to claim 1 or 2, characterized byin that the soil tillage machine (10) has a pre-assembled air flow assembly (44), wherein the air flow assembly (44) has at least the fan assembly (48), the heat exchanger assembly (46) and a frame (58) carrying the at least one fan (48a, 48b) and the heat exchanger assembly (46). [4] Self-propelled soil tillage machine (10) according to claims 2 and 3, characterized by that the frame (58) has a housing section (59) which at least partially encloses the mixing volume (60). [5] Self-propelled soil tillage machine (10) according to one of claims 3 or 4, characterized by that the fan arrangement (48) and the heat exchanger arrangement (46) are arranged so as to be rotationally displaced relative to one another about a pivot axis (SA) and / or translationally displaced along a displacement axis. [6] Self-propelled soil tillage machine (10) according to one of claims 3 to 5, characterized bythat the fan arrangement (48) is a substantially planar fan arrangement (48) and / or that the heat exchanger arrangement (46) is a substantially planar heat exchanger arrangement (46). [7] Self-propelled soil tillage machine (10) according to one of the preceding claims, including claim 2, characterized by that the ventilation air flow (LL) flows transversely to the flow direction of the cooling air flow (KL) passing through the heat exchanger arrangement (46) and / or transversely to an exhaust air flow (AL) flowing through the fan arrangement (48) towards the mixing volume (60). [8] Self-propelled soil cultivating machine (10) according to one of claims 4 to 7, including claim 4, characterized bythat the housing section (59) of the frame (58) which at least partially encloses the mixing volume (60) has a through opening (62; 62') which is located at a distance from both the heat exchanger arrangement (46) and the fan arrangement (48) and through which the ventilation air flow (LL) can flow. [9] Self-propelled soil tillage machine (10) according to claim 8, characterized by that a cross-sectional area of the passage opening (62; 62') through which the ventilation air flow (LL) can flow is variable in order to change the ventilation air quantity flowing in the ventilation air flow (LL) per unit of time under given operating conditions. [10] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized bythat the heat exchanger arrangement (46) has a plurality of heat exchangers (46a, 46b) which are components of different cooling circuits (52a) and / or cooling passages (52b), and / or that the fan arrangement (48) has a plurality of fans (48a, 48b). [11] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized by in that the soil tillage machine (10) has a control station (16), wherein the heat exchanger arrangement (46) and the fan arrangement (48) are arranged between the control station (16) and the front longitudinal end of the soil tillage machine (10). [12] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized by that the heat exchanger arrangement (46) and the fan arrangement (48) are arranged directly adjacent to the power source (32). [13] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized by that the heat exchanger arrangement (46) is located closer to one side of the machine and the fan arrangement (48) is located closer to the other side of the machine opposite in the cross-machine direction (Q). [14] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized by that the cooling air flow (KL) passing through the heat exchanger arrangement (46) has a flow component in the cross-machine direction (Q) and a flow component in the machine height direction (H) and / or that an exhaust air flow (AL) flowing through the fan arrangement (48) has a flow component in the cross-machine direction (Q) and a flow component in the machine height direction (H). [15] Self-propelled soil tillage machine (10) according to one of the preceding claims, characterized bythat the heat exchanger arrangement (46) and / or the fan arrangement (48) and / or the power source (32) are covered by a cover (36).

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