• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Infeed unit (1) of a forage harvester, with a first pair of draw rollers from an upper and a lower feed roller, and with a seen in Gutflussrichtung behind the first pair of feed rollers second set of feed rollers of an upper and a lower feed roller, wherein in the region of at least one pair of feed rollers (2) upper feed roller (3) via at least one double-acting differential cylinder (8, 9) against the lower feed roller (4) can be pressed to provide a pre-pressing force. On two opposite sides of the respective upper feed roller (3) in each case acts on a differential cylinder. The differential cylinders are connected to form a master-slave circuit such that a piston rod side (12) of a first, on a first side of the upper feed roller (3) acting differential cylinder (9) is coupled to a return line (14) of a pressure medium supply that a piston side (13) of a second, on a second side of the upper feed roller (3) acting differential cylinder (8) is coupled to a flow (15) of the pressure medium supply, and that a piston side (13) of the first differential cylinder (9) with a piston rod side the second differential cylinder (8) is coupled, wherein an effective area of the piston rod side (12) of the second differential cylinder (8) corresponds approximately to an effective area of the piston side (13) of the first differential cylinder (9).
    公开号:BE1025992B1
    申请号:E2018/5595
    申请日:2018-08-27
    公开日:2019-09-10
    发明作者:Martin Lehmann；Stefan Look；Michael Kühn
    申请人:Claas Saulgau Gmbh；
    IPC主号:
    专利说明:

    Infeed unit of a forage harvester and method for operating the same
    The invention relates to a feed mechanism of a forage harvester. Furthermore, the invention relates to a method for operating a feed mechanism.
    DE 196 51 694 A1 discloses the basic structure of a forage harvester in a forage harvester. When viewed in the direction of crop flow, the feed unit is positioned in front of a chopper, the feed unit comprising a first pair of feed rollers consisting of two feed rollers arranged one above the other and a second pair of feed rollers comprising two further feed rollers arranged one above the other. The second pair of feed rollers is referred to as the pair of pre-press rollers and the feed rollers of the same are referred to as pre-press rollers. The feed rollers of the second pair of feed rollers are arranged behind the feed rollers of the first pair of feed rollers, viewed in the direction of crop flow.
    Another feed mechanism of a forage harvester is known from EP 2 123 146 B1. There, too, two pairs of feed rollers are shown, each consisting of two feed rollers arranged one above the other. From EP 2 123 146 B1 it is also known to press the upper feed rollers of the feed roller pairs against the lower feed rollers of the feed roller pairs using double-acting differential cylinders. According to EP 2 123 146 B1, depending on the switching position of switching valves, the respective differential cylinder can also be used to move the upper feed rollers of the feed roller pairs away from the lower feed rollers of the feed roller pairs.
    DE 10 2013 4 274 B1 and US 6 584 755 B2 each disclose infeed units of forage harvesters in which a single-acting differential cylinder interacts with an upper infeed roller of a pair of infeed rollers. A restoring force provided by a spring element acts counter to the force provided by the single-acting differential cylinder.
    BE2018 / 5595
    In the case of infeed units known from the prior art, there is a risk that the upper infeed roller of a pair of infeed rollers will skew during operation. This reduces the functionality of the feed mechanism. In particular, an achievable pre-pressing force is reduced when the upper feed roller is misaligned. In particular, in the case of misalignments, there is a risk that a roll that is tilted collides on its end face with a side wall of the feed mechanism.
    There is a need to reduce the risk of misalignment with simple construction of a feed mechanism while maintaining high functionality and to eliminate the same in the event of an oblique position.
    Proceeding from this, the present invention is based on the object of creating a novel intake mechanism for a forage harvester and a method for operating the same. This object is achieved by a feed mechanism according to claim 1.
    According to the invention, a differential cylinder acts on two opposite sides of the respective upper feed roller, the differential cylinders acting on the opposite sides of the respective upper feed roller being interconnected to form a MasterSlave circuit, i.e. are connected in series or in series, the output of one differential cylinder being connected to the input of the other differential cylinder.
    To form the master-slave circuit, a piston rod side of a first differential cylinder acting on a first side of the upper feed roller is coupled to a return of a pressure medium supply. The first differential cylinder can be referred to as a slave cylinder.
    To form the master-slave circuit, a piston side of a second differential cylinder acting on a second side of the upper feed roller is also coupled to a supply of the pressure medium supply. The second differential cylinder can be referred to as a master cylinder.
    BE2018 / 5595
    To form the master-slave circuit, a piston side of the first differential cylinder is also coupled to a piston rod side of the second differential cylinder, an effective area of the piston rod side of the second differential cylinder corresponding to an effective area of the piston side of the first differential cylinder.
    The inventive master-slave circuit of the two differential cylinders acting on different sides of the upper feed roller can reduce the risk of misalignment of the upper feed roller relative to the lower feed roller of the pair of feed rollers. The lifting movement of the upper roller thus advantageously runs parallel to the lower roller.
    According to an advantageous development, the first differential cylinder and the second differential cylinder each have an overflow element, via which, when the respective differential cylinder is fully extended, oil can flow over from the piston side of the respective differential cylinder to the piston rod side of the respective differential cylinder. With the aid of the overflow element, it is possible to easily and reliably resolve the same in the event of an inclination.
    According to an advantageous development, a pressure medium reservoir and / or a pressure control valve interacts with the flow of the pressure medium supply. A pressure medium reservoir can also interact with the return of the pressure medium supply. The pressure control valve is used to provide a constant pressure in the flow. An oversupply or undersupply of pressure medium can be compensated for via the or each pressure medium reservoir.
    The method for operating the feed mechanism is defined in claim 8.
    Preferred developments of the invention result from the subclaims and the following description. Exemplary embodiments of the invention are explained in more detail with reference to the drawing, without being restricted to this. It shows:
    BE2018 / 5595
    Figure 1 shows a schematic section of a feeder of a forage harvester.
    FIG. 2 shows the feed mechanism of FIG. 1 in a first state;
    Fig. 3 shows the feed mechanism of Fig. 1 in a second state.
    The present invention relates to a feed mechanism of a forage harvester.
    1 shows a schematic section of a feed mechanism 1 of a self-propelled forage harvester in the area of a pair of feed rollers 2, which comprises an upper feed roller 3 and a lower feed roller 4. An axis 5, about which the lower feed roller 4 of the feed roller pair 2 is rotatable, is stationary. The upper feed roller 3 is also rotatably mounted about an axis 6, but the upper feed roller 3, in contrast to the lower feed roller 4, is not designed to be stationary, but rather can be displaced relative to the lower feed roller 4. The axis 6 of the upper feed roller 3 is displaceable via links 7 which engage at one end on a respective axle bearing and at an opposite end on a housing.
    Double-acting differential cylinders 8, 9 cooperate with the upper feed roller 3 of the pair of feed rollers 2 in order to displace the upper feed roller 3 relative to the lower feed roller 4. A first differential cylinder 9 acts on a first side and a second differential cylinder 8 on a second side of the upper feed roller 3.
    Each differential cylinder 8, 9 has a piston 10 and a piston rod 11. The piston 10 delimits a piston side 13 from a piston rod side 12 of the respective differential cylinder 8, 9.
    The differential cylinders 8, 9 acting on the opposite sides of the upper feed roller 3 are interconnected or coupled to form a master-slave circuit. Thus, a piston rod side 12 of the first differential cylinder 9 acting on the first side of the upper feed roller 3 is coupled to a return 14 of a pressure medium supply to the differential cylinders 8, 9. The first
    BE2018 / 5595
    Differential cylinders can be called slave cylinders. A piston side 13 of the second differential cylinder 8, which acts on the second side of the upper feed roller 3, is coupled to a feed line 15 of the pressure medium supply. The second differential cylinder can be referred to as a master cylinder. A piston side 13 of the first differential cylinder 9 is coupled to a piston rod side 12 of the second differential cylinder 8.
    1 illustrates that the first differential cylinder 9 has an effective area AK1 in the area of its piston side 13. In the region of the piston rod side 12, the first differential cylinder 9 has an effective area AR1. The second differential cylinder 8 has an effective area AK2 in the area of the piston side 13 and an effective area AR2 in the area of the piston rod side 12.
    The differential cylinders 8, 9 connected in the master-slave circuit are designed such that the effective area AR2 on the piston rod side 12 of the second differential cylinder 8 corresponds to the effective area AK1 on the piston side 13 of the first differential cylinder 9. For an ideal parallel guidance of the upper roller:
    A R2 = A K1
    By the above master-slave circuit of the differential cylinders 8, 9, which act on different sides on the upper feed roller 3 of the feed roller pair 2, and by the above design of the effective area AR2 of the piston rod side 12 of the second differential cylinder 8 and the effective area AK1 Piston side 13 of the first differential cylinder 9 can be ensured that both differential cylinders 8, 9, namely the piston rods 11 thereof, extend uniformly and thus shift the axis 6 of the upper feed roller 3 parallel to the axis 5 of the lower feed roller 4, thereby causing the upper feed roller 3 to be skewed can be avoided relative to the lower feed roller 4.
    BE2018 / 5595
    For this mode of operation according to the invention, the effective area AR2 and the effective area AK1 need not be exactly identical, but it is sufficient if the area AR2 and area AK1 are approximately the same. Thus, when selecting the differential cylinders 8, 9, more economical standard parts can be used. For a given quality of parallel guidance, the person skilled in the art can determine via the surface difference and the stroke path to be carried out with which pairing of differential cylinders from a standard parts catalog this quality is achieved. 1, a pressure medium reservoir 19 interacts with the return 14. A pressure medium reservoir 18 and a pressure control valve 17 cooperate with the flow 15. It is possible for a pressure medium reservoir 18 or 19 to cooperate either only with the feed 15 or only with the return 14.
    The pressure control valve 17 is used to provide a constant pressure pDRV in the flow 15 of the pressure medium supply.
    The pressure control valve 17 operates in a manner familiar to the person skilled in the art here. Thus, the pressure control valve 17 can automatically switch back and forth between its two switching positions in order to keep the pressure pDRV constant in the supply line 15.
    A pressure pZW prevails in a coupling line 16, via which the piston rod side 12 of the second differential cylinder 8 is coupled to the piston side 13 of the first differential cylinder 9. A pressure pR prevails in the return 14.
    As an alternative to a pressure regulating valve 17, a pressure accumulator can be pretensioned to a desired pressure by means of two suitable valves when the rollers are moved together by feeding in or out. Such a system works passively with enclosed oil volume. Of course, the system can also be filled using manually operated valves with a pressure gauge as a pressure indicator.
    2 and 3 each show states of the feed mechanism 1, in which one between the feed rollers 3 and 4 of the pair of feed rollers 2
    BE2018 / 5595
    2, the gap between the feed rollers 3, 4 is smaller on the first side in the area of the first differential cylinder 9 than in the area of the second side or the second differential cylinder 8. In FIG. 3, on the other hand, the gap between the feed rollers 3 and 4 in the region of the second side or the second differential cylinder 8 are smaller than in the region of the first side or the first differential cylinder 9.
    In order to be able to eliminate such an inclination of the upper feed roller 3 relative to the lower feed roller 4, each differential cylinder 8, 9 has an overflow element 21.
    Via such an overflow element 21, when the respective differential cylinder 8, 9 or its piston rod 11 is fully extended, oil can flow over from the piston side 13 to the piston rod side 12 of the respective differential cylinder 8, 9. The overflow element 21 can be designed as an overflow notch or throttle check valve or an unlockable check valve.
    Then, when the upper feed roller 3 assumes the misalignment according to FIG. 2 relative to the lower feed roller 4, both differential cylinders 8, 9 are first extended as shown in FIG. 2 until one of the two differential cylinders, here the first differential cylinder 9, is fully extended.
    The pressure on the piston side of the second differential cylinder 8, the so-called master cylinder, is then increased in order to also fully extend the piston rod 11 thereof.
    The following relationship applies to the pressures in lines 15, 16 and 14:
    pZW = pDRV * AK2 / AR2> pR
    Then, when the first differential cylinder 9 assumes its end position according to FIG. 2, the piston side 13 is short-circuited with the piston rod side 12 thereof via the overflow element 21, so that from the piston rod side 12 of the first differential cylinder 9
    BE2018 / 5595 oil can flow over to the piston rod side 12 of the same despite the maximum extended position. It is then possible to extend the second differential cylinder 8, which has not yet been fully extended, namely by oil from its piston rod side 12 via the coupling line 16 into the piston side 13 of the first differential cylinder 9 and from there overflow element 21 into the piston rod side 12 of the first Differential cylinder 9 and from there flows into the return 14. As a result, the second differential cylinder 8, which has not yet been fully extended, can then be fully extended and the misalignment of the upper feed roller 3 can be released.
    Fig. 3 shows a variant in which the upper feed roller 3 is inclined relative to the lower feed roller 4 in the other direction, so that when the two differential cylinders 8, 9 are extended, the second differential cylinder 8 first reaches its end position, that is to say fully extends first, whereas first differential cylinder 9 is not yet fully extended. In this case, the overflow element 21 of the second differential cylinder 8 then takes over the connection of the piston side 13 of the same to the piston rod side 12. In this case, the following relationship applies to the pressure:
    p ZW = p DRV
    The piston of the first differential cylinder 9 extends further since AK1> AR1.
    When the second differential cylinder 8 is already fully extended, oil can flow from its piston side 13 into its piston rod side 12 and from there via the coupling line 16 into the piston side 13 of the second differential cylinder 8 in order to also fully extend the second differential cylinder 8.
    In the feed mechanism 2 according to the invention, the risk of misalignment between the feed rollers 3, 4 of the pair of feed rollers 2 can be reduced. In the event of misalignment, it can be removed easily and reliably.
    BE2018 / 5595
    Due to the parallel movement of the upper feed rollers, the feed mechanism 1 is exposed to a lower mechanical load, and a mechanical collision of the upper feed roller with the side walls is avoided.
    By acting on both sides of the differential cylinders 8, 9 on the piston side 13 and piston rod side 12, the movement of the upper feed roller 3 can be damped, thereby reducing the risk of vibrations in the feed mechanism 1. By applying the differential cylinders 8, 9 on both sides, a pressure difference between mi10 minimum and maximum load is smaller. The or each pressure accumulator 18, 19 can be designed better.
    BE2018 / 5595
    LIST OF REFERENCE NUMBERS
    infeed
    Feed roller pair upper feed roller lower feed roller
    axis
    axis
    handlebars
    differential cylinder
    differential cylinder
    piston
    piston rod
    Piston rod side
    piston side
    returns
    leader
    coupling line
    Pressure control valve
    accumulator
    accumulator
    control device
    overflow element
    权利要求:
    Claims (9)
    [1]
    1. Infeed unit (1) of a forage harvester, with a first pair of infeed rollers consisting of an upper infeed roller and a lower infeed roller, and with a second pair of infeed rollers consisting of an upper infeed roller and a lower infeed roller positioned behind the first infeed roller pair, viewed in the flow direction, with at least one pair of infeed rollers in the area (2) the respective upper feed roller (3) can be pressed against the respective lower feed roller (4) via at least one double-acting differential cylinder (8, 9) in order to provide a pre-pressing force between them, characterized in that on two opposite sides of the respective upper one Feed roller (3) each acts on a differential cylinder (8, 9), the differential cylinders (8, 9) acting on the opposite sides of the respective upper feed roller (3) being interconnected to form a master-slave circuit in such a way that a piston rod side ( 12) a first, on a first side of the upper feed roller (3) acting differential cylinder (9) is coupled to a return (14) of a pressure medium supply, a piston side (13) of a second, on a second side of the upper feed roller (3) acting differential cylinder (8) a feed line (15) of the pressure medium supply is coupled, a piston side (13) of the first differential cylinder (9) is coupled to a piston rod side (12) of the second differential cylinder (8), an effective area (AR2) of the piston rod side (12) of the second Differential cylinder (8) corresponds approximately to an effective area (AK1) of the piston side (13) of the first differential cylinder (9).
    [2]
    2. Feed mechanism according to claim 1, characterized in that a pressure medium reservoir (19) interacts with the return (14) of the pressure medium supply.
    BE2018 / 5595
    [3]
    3. Feeding mechanism according to claim 1 or 2, characterized in that a pressure medium reservoir (18) interacts with the flow (15) of the pressure medium supply.
    [4]
    4. Infeed mechanism according to one of claims 1 to 3, characterized in that a pressure control valve (17) or a pressure accumulator biased to a desired pressure cooperates with the flow (15) of the pressure medium supply.
    [5]
    5. Infeed mechanism according to claim 3 and 4, characterized in that the pressure medium reservoir (18) which interacts with the flow (15) of the pressure medium supply is connected between the pressure control valve (17) and the second differential cylinder (8).
    [6]
    6. Infeed mechanism according to one of claims 1 to 5, characterized in that the first differential cylinder (9) and the second differential cylinder (8) each have an overflow element (21), via which when the respective differential cylinder (8, 9) is full is extended, oil can flow over from the piston side (13) of the respective differential cylinder to the piston rod side (12) of the respective differential cylinder.
    [7]
    7. Infeed mechanism according to claim 6, characterized in that the overflow element (21) of the respective differential cylinder (8, 9) is an overflow notch or a throttle check valve or an unlockable check valve.
    [8]
    8. A method of operating a feed mechanism (1) according to claim 6 or 7, namely to compensate for an inclination of the respective upper feed roller (3), wherein. First both differential cylinders (8, 9) are extended until one of the two differential cylinders (8, 9) is fully extended, then the not yet fully extended differential cylinder (9, 8) is extended further by using the overflow element (21) already fully extended differential cylinder BE2018 / 5595 Linders (8,
    [9]
    9) Oil flows from the piston side (13) of the same to the piston rod side (12) of the same.
    类似技术:
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    同族专利:
    公开号 | 公开日
    DE102017121400A1|2019-03-14|
    BE1025992A1|2019-09-03|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4655031A|1985-07-24|1987-04-07|J. I. Case Company|Phasing circuit for serially|
    US20020007621A1|2000-06-23|2002-01-24|Van Der Plas Nicolaas|Silage cutter|
    EP2123146A1|2008-05-20|2009-11-25|CNH Belgium N.V.|Feed roll control system for a forage harvester|
    US20140166790A1|2012-12-13|2014-06-19|Vermeer Manufacturing Company|Method and Apparatus for Maintaining a Feed Roller Parallel to an Infeed Floor Through its Range of Motion|
    DE19651694A1|1996-12-12|1998-06-25|Claas Ohg|Cutter for agricultural crop chopper with drum and counter-blade|
    US6584755B2|2001-08-14|2003-07-01|Deere & Company|Apparatus for adjusting the spacing and/or the contact pressure between two rollers of a kernel processor|
    DE202009005719U1|2009-04-16|2010-09-02|Alois Pöttinger Maschinenfabrik Gmbh|Tillage device|
    DE102009026071A1|2009-06-30|2011-01-05|Amazonen-Werke H. Dreyer Gmbh & Co. Kg|Hydraulic actuator|
    DE102013004274B4|2013-03-13|2015-08-20|Claas Saulgau Gmbh|Feed device for a chopper of a forage harvester|
    DE102014118435B4|2014-12-11|2017-03-16|Claas Saulgau Gmbh|spring means|
    法律状态:
    2019-10-17| FG| Patent granted|Effective date: 20190910 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102017121400.3A|DE102017121400A1|2017-09-14|2017-09-14|Feed-in of a forage harvester and method of operating the same|
    DE102017121400.3|2017-09-14|
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