Semi-mounted reversible plough with improved reversing mechanism

Abstract

Semi-mounted reversible plough (1) with a rotating mechanism (2) by means of which a plough frame (3) supporting two rows of plough bodies (4a, 4b) opposite one another can be rotated about a horizontal turning axis (W), wherein the rotating mechanism (2) has at least one first hydraulic cylinder (5a) and one second hydraulic cylinder (5b) for rotating the plough frame (3) about the turning axis (W) into the respective working position, wherein the hydraulic cylinders (5a, 5b) are arranged on the rotating mechanism (2) in such a single-acting manner that, in order to rotate the plough frame (3) from one working position into the opposite working position, the first hydraulic cylinder (5a) is initially operatively connected to the rotating mechanism (2) in order to rotate the plough frame (3) from the working position into an intermediate position in which the plough frame (3) is arranged at least approximately above the turning axis (W),to spend, wherein the second hydraulic cylinder (5b) is not operatively connected to the rotating mechanism (2) and then the second hydraulic cylinder (5b) is operatively connected to the rotating mechanism (2) in order to lower the plough frame (3) from the intermediate position into the opposite working position, wherein the first hydraulic cylinder (5a) is not operatively connected to the rotating mechanism (2), and in order to rotate the plough frame (3) from the opposite working position into the working position, conversely, first the second hydraulic cylinder (5b) and then the first hydraulic cylinder (5a) is operatively connected to the rotating mechanism (2), wherein the stroke (H1) of the hydraulic cylinders (5a, 5b) in order to lower the plough frame (3) from the intermediate position into the working position is hydraulically damped, characterized in that the semi-mounted reversible plough (1) comprises at least one bypass (10), wherein by means of the bypass (10) the stroke (H2) of the hydraulic cylinders (5a,5b) to move the plough frame (3) from the working position to the intermediate position is undamped.,

Description

The invention relates to a saddle-ridden reversible plough according to the preamble of claim 1.Such saddle-backed rotorcrafts having a slewing gear are well known in practice. By means of the slewing gear, a plough frame carrying two rows of plough bodies opposite one another is rotatable about a lying turning axis, so that optionally the one row of plough bodies operates or the opposite row of plough bodies can enter the ground. In order to rotate the plough frame about 180 degrees about the turning axis into the respective working position, the slewing gear comprises at least a first hydraulic cylinder and a second hydraulic cylinder. The hydraulic cylinders act in a simple manner during the rotation of the plough frame, although they can be designed to be double-acting. The hydraulic cylinders are thus arranged on the slewing gear in such a simple manner of action that, for the rotation of the plough frame from an operating position into the opposite operating position, the first hydraulic cylinder is firstly operatively connected to the slewing gear in order to move the plough frame from the operating position into an intermediate position in which the plough frame is arranged at least approximately above the turning axis, wherein the second hydraulic cylinder is not operatively connected to the slewing gear. The second hydraulic cylinder is then operatively connected to the slewing gear in order to lower the plough frame from the intermediate position into the opposite working position, wherein the first hydraulic cylinder is not operatively connected to the slewing gear. In order to move the plough frame from this opposite working position back into the first working position in the reverse sequence, the second hydraulic cylinder is firstly operatively connected to the slewing gear and then the first hydraulic cylinder is operatively connected to the slewing gear. In order to make the turning process jerk-free, it is regularly provided that the stroke of the hydraulic cylinders is hydraulically damped in order to lower the plough frame from the intermediate position into the working position. During the hydraulic damping of this stroke path, the volume flow, in particular the outflow, is throttled, so that the hydraulic cylinder moves at a reduced speed.In previous saddle-type rotorcrafts with such a slewing gear, the problem is that the damped lifting travel of the hydraulic cylinders to lower the plough frame from the intermediate position into the working position likewise corresponds to the lifting travel to move the plough frame from the working position into the intermediate position. The damping thus has hitherto been effective for the entire stroke path regardless of the direction in which it is executed. The change from one working position to the other, i.e. the turning process by means of the slewing gear, is thus extended due to the bidirectional damping.DE 29 19 362 A1 and DE 10 2019 129 988 A1 each disclose an attached reversible plough having a slewing gear, wherein the slewing gear has only a single cylinder in order to selectively bring the one row of plough bodies into the working position.The object of the present invention is to provide a saddle-riding reversible plough with an improved slewing gear which, in particular, overcomes the disadvantages known in the prior art. In particular, the turning process is to be accelerated by means of the slewing gear without additionally stressing the saddle reversible plough.This object is achieved according to the invention by a saddle-ridden reversible plough having the features of claim 1. It is provided that the saddle reversible plough comprises at least one bypass, wherein the lifting travel of the hydraulic cylinders around the plough frame is to be moved from the working position into the intermediate position by means of the bypass. By means of the bypass, the throttling of the volume flow can be bridged at least for the stroke of the hydraulic cylinders in the direction from the working position into the intermediate position, so that this stroke can be carried out at an increased speed. "Unattenuated", i.e. that the volume flow for this stroke or in this direction does not have to flow via the damping.The invention makes use of the finding that the respective hydraulic cylinder works against the dead weight of the plough frame in this first half of the turning process. This lifting path can thus be traversed at an increased speed without introducing impacts into the slewing gear and / or the plough frame. During the second half of the turning process, on the other hand, the travel distance is damped, since here the dead weight of the plough frame loads the hydraulic cylinder. The turning process is consequently accelerated during the first half without additional material loading.The saddle-ridden reversible plough according to the invention is advantageously further developed in that the first hydraulic cylinder and the second hydraulic cylinder each comprise an end position damping for damping the stroke path around the plough frame from the intermediate position into the working position, wherein the bypass is configured to conduct hydraulic fluid under pressure parallel to the respective end position damping into at least one chamber of the hydraulic cylinders. By introducing the hydraulic fluid into the chamber of a hydraulic cylinder parallel to the end position damping, the damping can consequently be bridged in at least one direction, namely in the inflow direction, while outflowing hydraulic fluid is throttled by means of the end position damping. When the hydraulic cylinders are designed with end position damping, the damping can thus be canceled in one direction by means of the bypass, namely for the stroke path from the working position into the intermediate position.In a further particularly advantageous development of the saddle-riding reversible plough according to the invention, it is provided that the first hydraulic cylinder and the second hydraulic cylinder each comprise a bypass which is connected in parallel with the end position damping, wherein the bypass each has a nonreturn valve. By using a check valve, it can be ensured in a particularly expedient manner that the hydraulic fluid flows in one direction via the end position damping and can flow in the opposite direction parallel to the damping directly into the chamber of the hydraulic cylinder via the bypass.The above embodiment of the saddle-ridden reversible plough according to the invention is advantageously further developed in that the nonreturn valve is configured to block the bypass during the lifting travel in order to lower the plough frame from the intermediate position into the working position and to release the bypass during the lifting travel in order to move the plough frame from the working position into the intermediate position.In a further advantageous development of the saddle-riding reversible plough according to the invention, the end position damping is designed in multiple stages, in particular in three stages.Further details of the invention can be found in the exemplary description and the drawings. The drawings show FIG. 1 shows an exemplary embodiment of the saddle-ridden reversible plough according to the invention with a slewing gear in a perspective view obliquely from the rear, FIG. 2 shows the slewing gear with two hydraulic cylinders in a detailed view obliquely from the front, FIG. 3 shows a hydraulic cylinder of the slewing gear along a first stroke path in a first stroke position in sectional view, FIG. 4 shows the hydraulic cylinder in a second stroke position in sectional view, FIG. 5 shows the hydraulic cylinder in a third stroke position in sectional view, and FIG. 6 shows the hydraulic cylinder on a second stroke path in the third stroke position in a sectional view.A saddle reversible plough 1 with a slewing gear 2 at its front end can be seen in FIG. 1 in an operating position in a perspective view obliquely from the rear. The saddle-ridden reversible plough 1 comprises a plough frame 3 which carries two oppositely arranged plough body rows 4a, 4b. In the working position shown, the ground is worked by means of the row 4a of plough bodies. By means of the slewing gear 2, the plough frame 3 is rotatable about a lying turning axis W, which points at least approximately in the direction of travel, by at least approximately 180 degrees, so that the opposite working position, in which the row of plough bodies 4 bcarries out the soil working, is reached. For this purpose, the slewing gear 2 comprises two hydraulic cylinders 5 a, 5 b.The slewing gear 2 is shown in FIG. 2 in a detailed view obliquely from the front. The hydraulic cylinders 5 a, 5 bare of double-acting design but are arranged on the slewing gear 2 in a single-acting manner. A rocker 6 pivotable about the turning axis W in a limited angular range ensures that only one of the hydraulic cylinders 5 a, 5 bis always operatively connected to the slewing gear 2, as will be explained below. In order to rotate the plough frame 3 from the working position shown in FIG. 1 into the opposite working position, the hydraulic cylinder 5 ais firstly operatively connected to the slewing gear 2. The hydraulic cylinder 5 athus corresponds to the "first hydraulic cylinder" in the sense of the patent claims. The hydraulic cylinder 5 awhich is initially operatively connected to the slewing gear 2 is in a third stroke position, shown in FIGS. 5 and 6, in which it has its minimum length. In order to move the plough frame 3 from the working position into an intermediate position, in which the plough frame 3 is arranged at least approximately above the turning axis W, the hydraulic cylinder 5 ais extended along a second stroke H 2, indicated in FIG. 6. The hydraulic cylinder 5 bis hereby out of operative connection with the slewing gear 2. the hydraulic cylinder 5 bthus corresponds to the "second hydraulic cylinder" in the sense of the patent claims.Subsequently, the hydraulic cylinder 5 bis operatively connected to the slewing gear 2 in order to lower the plough frame 3 from the intermediate position into the opposite working position. The hydraulic cylinder 5b is in the intermediate position in a first stroke position, shown in Fig. 3, in which it has its maximum length. In order to lower the plough frame 3 from the intermediate position into the opposite working position, the hydraulic cylinder 5 bis moved in a first stroke H 1, indicated in FIGS. 3 to 5. On this stroke H 1, the weight of the plough frame 3 with the plough body rows 4 a, 4 bloads at least partially on the hydraulic cylinder 5 b, while the hydraulic cylinder 5 ais not operatively connected to the slewing gear 2.For rotating the plough frame 3 in the opposite direction from the working position of the plough body row 4 bto the working position of the plough body row 4 a, the hydraulic cylinder 5 bis accordingly firstly operatively connected to the slewing gear 2 and is moved from its third stroke position of minimum length along the second stroke path H 2 into the first stroke position of maximum length. Subsequently, the hydraulic cylinder 5 ais operatively connected to the slewing gear 2 and is moved from the first lifting position on the first lifting path H 1 into the third lifting position of minimum length in order to lower the plough frame 3.In order to avoid a sudden load on the components involved in the rotation, it is provided that the stroke H 1 of the hydraulic cylinders 5 a, 5 bis hydraulically damped in order to lower the plough frame 3 from the intermediate position into the working position. The hydraulic cylinders 5a, 5b have a three-stage end position damping 7, as will be explained in more detail with reference to FIGS. 3 to 6.In the first stroke position of the hydraulic cylinders 5 a, 5 bshown in FIG. 3, the annular chamber side is acted upon by pressurized hydraulic fluid, so that the piston is set in motion along the first stroke path H 1. The hydraulic fluid located in the piston chamber is displaced by a mandrel 8 of the end position damping 7. the mandrel 8 has a bore through which the displaced hydraulic fluid is throttled, so that the stroke H 1 is damped.With increasing stroke H 1, shown for the second stroke position in FIG. 4, the mandrel 8 begins to enter a piston bore 9, whereby the free cross section for the displaced hydraulic fluid is further reduced. The mandrel 8 has a first diameter D 1 in this region. The end position damping 7 is thus provided with an additional damping stage.As the stroke distance H 1 increases further, a region of the mandrel 8 dips into the piston bore 9 one of the second diameters D 2, wherein the second diameter D 2 is greater than the first diameter D 1. The volume flow for the hydraulic fluid displaced from the piston chamber is thus further throttled, so that the end position damping 7 is created with a third damping stage.In order that the hydraulic fluid under pressure does not have to flow in a damped manner over the end position damping 7 for the second stroke H 2 from the third stroke position, shown in FIG. 6, back into the first stroke position according to FIG. 3, a bypass 10 is provided. The bypass 10 ensures that the stroke H 2 of the hydraulic cylinders 5 a, 5 bto move the plough frame 3 from the working position into the intermediate position is unattenuated.The bypass 10 is connected to its mandrel 8 parallel to the end position damping 7, so that it is configured to conduct hydraulic fluid under pressure into the piston chamber of the hydraulic cylinders 5 a, 5 bin parallel to the respective end position damping 7. Each of the hydraulic cylinders 5 a, 5 bhas a check valve 11 on its bypass 10 for this purpose.The check valve 11 is configured to block the bypass 10 during the stroke H 1 in order to lower the plough frame 3 from the intermediate position into the working position, so that the displaced hydraulic fluid flows via the end position damping 7, and to release the bypass 10 during the stroke H 2 in order to bring the plough frame 3 from the working position into the intermediate position, so that the end position damping 7 is bridged and the hydraulic fluid under pressure can flow directly into the piston chamber. The stroke H 2 is thus unattenuated because the incoming hydraulic fluid can bypass the throttling end position damping 7 via the bypass 10.List of reference characters1 Saddle reversible plough 2 slewing gear 3 plough frame 4 a, 4 b Plough body row W Turning axis 5 a, 5 b Hydraulic cylinder 6 Rocker 7 End position damping 8 Pin 9 Piston bore D 1, D 2 Diameter 10 Bypass 11 Nonreturn valve

Claims

Saddle reversible plough (1) having a slewing gear (2) by means of which a plough frame (3) carrying two rows of plough bodies (4a, 4b) opposite one another can be rotated about a lying turning axis (W), wherein the slewing gear (2) has at least one first hydraulic cylinder (5a) and one second hydraulic cylinder (5b) for rotating the plough frame (3) about the turning axis (W) into the respective working position, wherein the hydraulic cylinders (5a, 5b) are arranged on the slewing gear (2) in such a simple action that, for rotating the plough frame (3) from a working position into the opposite working position, the first hydraulic cylinder (5a) is firstly operatively connected to the slewing gear (2), about the plough frame (3) from the working position into an intermediate position, in which the plough frame (3) is arranged at least approximately above the turning axis (W), wherein the second hydraulic cylinder (5b) is operatively connected to the slewing mechanism (2) and then the second hydraulic cylinder (5b) is operatively connected to the slewing mechanism (2) in order to lower the plough frame (3) from the intermediate position into the opposite working position, wherein the first hydraulic cylinder (5a) is operatively connected to the slewing mechanism (2), and for rotating the plough frame (3) from the opposite working position into the working position, conversely, first the second hydraulic cylinder (5b) and then the first hydraulic cylinder (5a) are operatively connected to the slewing mechanism (2), wherein the stroke path (H1) of the hydraulic cylinders (5a, 5b) for lowering the plough frame (3) from the intermediate position into the working position, characterized in that the saddle reversible plough (1) comprises at least one bypass (10), wherein the lifting path (H2) of the hydraulic cylinders (5a, 5b) for moving the plough frame (3) from the working position into the intermediate position is unattenuated by means of the bypass (10).Saddle reversible plough (1) according to Claim 1, characterized in that the first hydraulic cylinder (5a) and the second hydraulic cylinder (5b) each comprise an end position damping (7) for damping the lifting travel (H1) in order to lower the plough frame (3) from the intermediate position into the working position, wherein the bypass (10) is configured to conduct hydraulic fluid under pressure parallel to the respective end position damping (7) into at least one chamber of the hydraulic cylinders (5a, 5b).Saddle reversible plough (1) according to Claim 2, characterized in that the first hydraulic cylinder (5a) and the second hydraulic cylinder (5b) each comprise a bypass (10) which is connected in parallel with the end position damping (7), the bypass (10) each having a nonreturn valve (11).Saddle reversible plough (1) according to Claim 3, characterized in that the nonreturn valve (11) is configured to block the bypass (10) during the lifting path (H1) in order to lower the plough frame (3) from the intermediate position into the working position, and to release the bypass (10) during the lifting path (H2) in order to bring the plough frame (3) from the working position into the intermediate position.Saddle reversible plough (1) according to Claim 2, 3 or 4, characterized in that the end position damping (7) is designed in multiple stages, in particular in three stages.

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