GB2169551A

GB2169551A - Balers

Info

Publication number: GB2169551A
Application number: GB08504637A
Authority: GB
Inventors: Francis Poley
Original assignee: C Van der Lely NV
Current assignee: C Van der Lely NV
Priority date: 1984-11-30
Filing date: 1985-02-22
Publication date: 1986-07-16
Also published as: GB8504637D0

Abstract

A baler comprises a bale forming chamber (8) having an inlet opening (28). In use, crop is picked up by a device (33) and is fed by a pressing member (39) into the chamber (8) through the opening (28). The length of the pressing member (39), in the direction of crop passage, is substantially equal to or greater than the vertical dimension (64) of the inlet opening (28) and it is movable at an effective speed exceeding the peripheral speed of a bale rotating in the chamber (8). The effect of the pressing member (39) is to force crop into the chamber (8) to achieve a densely packed bale. The chamber (8) is defined by transport members (66,67,68), one of which (66) is pivotable about an axis (79) disposed between the horizontal boundaries of an operative bale engaging surface of the transport member and is provided with elastic tensioning means for circumferentially tensioning the said surface. <IMAGE>

Description

SPECIFICATION Balers This invention relates to balers for forming cylindrical bales of crop (so called "big bales"). Such balers comprise a bale forming chamber, having an inlet opening and a pick-up device for picking up the crop from the ground.

In such devices some slip often occurs between transport members bounding the bale forming chamber and the bale being formed, as the crop is being wound. This is particularly evident when the bale has almost reached its final diameter, when the outer layer of the bale being formed in the bale forming chamber has consolidated to a hard layer, but with some forms of transport members this may occur even when the bale still has a relatively small diameter.

It is usually desirable for the bale to have a relatively hard outer layer of relatively large thickness, to give protection against the influence of weather conditions when the ready bale is left on the field.

It is desirable to enhance the hardness of this outer layer.

According to one aspect of the present invention there is provided a baler for forming cylindrical bales of crop, comprising a bale forming chamber having an inlet opening and a pick-up device for picking up crop from the ground, a pressing member being provided between the pick-up device and the inlet opening for pressing crop into the bale forming chamber, the effective dimension of said member, measured in the transport direction of the crop into the bale forming chamber, being not less than substantially equal to the upwardly measured dimension of the inlet opening.

According to a second aspect of the present invention, there is provided a baler for forming cylindrical bales of crop, comprising a bale forming chamber having an inlet opening and a pick-up device for picking up crop from the ground, pressing means being provided which, in operation, pushes the crop into the inlet opening, the pressing means being movable, in operation, towards the inlet opening, at an effective speed exceeding the peripheral speed of a bale rotating in the bale forming chamber.

The pressing member introduces the crop into the inlet opening at a relatively high pressure and forces it into the approximately wedge-shaped space between the surface of the forming bale disposed behind the inlet opening and the transport members locally supporting the bale. In this way the crop exerts a tangential force on the periphery of the bale so that the effect of the transport members is enhanced and the slip is at least reduced.

The crop is furthermore vigorously pressed against and between the outer stalks of the bale so that the hardness of the outer layer is increased.

According to a third aspect of the present invention, there is provided a baler for forming cylindrical bales of crop, comprising a bale forming chamber having a crop inlet opening, at least one transport member being provided which has an operative surface which, in operation, engages a bale lying in the bale forming chamber, the transport member being pivotable about a pivotal axis which, as viewed from the bale forming chamber, is spaced from the horizontal boundaries of the operative surface.

According to a fourth aspect of the present invention, there is provided a baler for forming cylindrical bales of crop, comprising a bale forming chamber which is partly bounded by a transport member which has drivable transport means for turning a bale lying in the bale forming chamber, the transport member having elastic tensioning means for circumferentially tensioning the transport means in operation.

For a better understanding of the present invention and to show how it may be carried into effect, reference will now be made, by way of example, to the accompanying drawings, in which: Figure 1 is a side view of a baler; Figure 2 is a view taken on the lines ll-ll in Figure 1; Figure 3 is a sectional view taken on the lines Ill- 111 in Figure 2; Figure 4 is a side view of another baler; Figure 5 is a sectional view taken on the line V-V in Figure 4; and Figure 6 is a sectional view taken on the line VI VI in Figure 5.

The baler shown in Figure 1 forms cylindrical bales of crop. It comprises a frame 1, which carries a front part 2 of the baler, and is supported by ground wheels 3. Behind the front part 2 there is a rear part 4 of the baler, which occupies the position shown in Figure 1 during bale formation but which, when the bale is fully formed, can be tilted up, as indicated by an arrow B, with respect to the front part 2 about a pivotal shaft 5 extending transversely of the intended direction of operative travel A. This tilting is effected by hydraulic rams 6 situated one on each side of the baler and its purpose is to allow the formed bale to be discharged from the baler so that it drops on the ground behind the baler.

The front part 2 is provided with a drawbar 7, by means of which the baler can be coupled with coupling means of a tractor to draw the baler in the direction A.

A bale-forming chamber 8 is situated partly in the front part 2 and partly in the rear part 4. As viewed transversely of the direction A, the bale forming chamber 8 is bounded on both sides by mutually parallel side plates 9 and 10. The distance between the plates 9 and 10 defines the axial length of the bale to be formed (Figure 2). Each of the side plates 9 and 10, as is shown in Figure 1, is divided so that a front part of each side plate is associated with the front part 2 of the baler and a rear part of each side plate is associated with the rear part 4 of the baler. The two parts of each side plate 9 and 10 are coplanar and meet each other at the interface between the parts 2 and 4.

The circumferential periphery of the bale forming chamber 8 is defined by drivable bottom rollers 11 (Figure 1) arranged one behind the other. These rollers 11 support, in operation, at least part of the weight of the growing or complete bale. The bottom rollers 11 are journalled in the side plates 9 and 10 of the front part 2 and extend horizontally and transversely of the direction A. To the rear of the bottom 11 there are drivable rollers 12 which continue the row of rollers 11 and extend parallel to them. The rollers 12 are journalled in the parts of the side plates 9 and 10 of the rear part 4 of the baler. The rollers 11 and 12 extend over the whole width between the side plates 9 and 10. The rollers 12 provide a surface for guiding crop, this surface adjoining a similar surface provided by the rollers 11 and curving upwards towards the rear.The rollers 11 and 12 serve as transport members for the crop introduced into the bale forming chamber 8 and for the bale to be formed.

At a position obliquely behind and above the uppermost roller 12, as shown in the side view of Figure 1, there is a pivotal shaft 13 which is journalled in the side plates 9 and 10 and extends parallel to the axes of the rollers 11 and 12. A transport member 14, having a length substantially equal to half the diameter of a fully formed bale, is pivotable about the shaft 13. The outer circumference of a fully formed bale in the bale forming chamber 8 is designated by reference numeral 15.

The transport member 14 comprises two spaced rollers 16 and 17 interconnected at both ends by carrier rods (not shown) which are journalled around the axes of the two rollers 16 and 17. A row of flexible, endless conveyor belts or a plurality of chains 18 pass around the rollers 16 and 17 and extend over the entire width between the side plates 9 and 10. These belts or chains 18 are interconnected in a direction at right angles to the direction A by transport rods 19 which extend over substantially the whole distance between the side plates 9 and 10. The whole transport member 14 is freely pivotable about the pivotal shaft 13 extending transversely of the direction A. In the position indicated by chain-dotted lines the shaft of the roller 17 bears on stops provided in the side plates 9 and 10 so that this position represents the most inwardly pivoted position.The transport member 14 is pivotable in the direction of the arrow 10 into an outermost position indicated by dashed lines, which is also established by stops in the side plates 9 and 10.

When the transport member 14 is in the dashed line position, the roller 17 lies near to a roller 21 which is journalled in the side plates 9 and 10 and is part of an upper transport member 22 having the same construction, and approximately the same length, as the transport member 14, as indicated in Figure 1. In the upwardly directed position indicated by chain-dotted lines the transport member 22 extends forwardly and slightly downwards away from the roller 21. This position is also defined by stops in the side plates 9 and 10. The transport member 22 can pivot upwards from this position in the direction indicated by an arrow 23 into an outermost position indicated by dashed lines, which is also defined by stops.

In a similar manner the front part 2 of the baler has in its front region, and approximately at the level of the centre of a fully formed bale 15, a roller 24 which is journalled in the side plates 9 and 10 and is part of a transport member 25, which is constructed in the same way as the transport members 14 and 22 and has approximately the same length as indicated in Figure 1. The transport member 25 is pivotable about the shaft of the roller 24 in the direction indicated by an arrow 26 from an inwardly directed position indicated by chain-dotted lines and defined by stops into an outermost position indicated by dashed lines and also defined by stops.

When in the most inwardly directed position shown in Figure 1, the transport member 25 extends to the rear and slightly upwards from the roller 24, with respect to the direction A.

Below the roller 24, there is a drivable roller 27 which is journalled in the side plates 9 and 10.

There is a gap between the points of closest approach of the rollers 11 and 27, this gap defining an inlet opening 28.

The rollers 11 and 12 mounted in the side plates 9 and 10, the transport member 14, 22, 25 when in their outermost positions indicated by dashed lines and the roller 27 define a substantially cylindrical space which is closed at both ends by the side plates 9 and 10 and, as indicated in Figure 1, is filled by a fully formed bale 15.

The rollers 11 and 12, the transport members 14, 22 25 and the roller 27 are all driven in the directions indicated by arrows 30. This drive is performed in known manner by means of sprockets arranged on the driving shafts of the rollers 11, 12 and 27 and on the rollers 16, 21 and 24 of the transport members, these sprockets being situated outside the side plates 9 and/or 10. The sprockets can be driven from a gear wheel transmission 31 mounted on the drawbar 7. The gear wheel transmission 31 is drivable from the power take-off shaft of the tractor by means of an auxiliary shaft 32 provided with universal joints, extending forwardly away from the gear wheel transmission 31.

Ahead of the inlet opening 28, there is a pick-up device 33 which comprises tines 34 mounted on a reel 35. The reel 35 is drivable in the direction indicated by an arrow 36 (Figure 3) from the gear wheel transmission 31. The pick-up device 33 is enclosed at both lateral ends by plates 37. The rear ends of the plates 37 are in contact with the inner faces of the side plates 9 and 10. The tines 34 of the pick-up device 33 are arranged in groups. The tines in each group lie in a common vertical plane, the groups being disposed side by side so that they are regularly distributed across the width between the side plates 37. The reel 35 is surrounded by scraping strips 38 situated in the intervals between the groups of tines. The function of the scraping strips 38 is to scrape picked up crop from the tines 34 at the rear of the pick-up device 33, where the tines 34 are moving downwards.

Between the pick-up device 33 and the inlet opening 28 there is a pressing member 39 which extends over the whole active width of the baler.

The purpose of the pressing member is to press the crop supplied by the pick-up device 33 forcibly through the inlet opening 28 into the wedgeshaped space bounded on the underside by the upper parts of the rollers 11 and on the upper side by the periphery of the bale being formed. This wedge-shaped space is schematically indicated in the side elevation of Figure 3 by means of the angle 40.

The pressing member is situated between the pick-up device 33 and the foremost roller 11 and is thus disposed outside the bale forming chamber 8.

It comprises two pairs of stub shafts 41 and 42 (Figures 2 and 3). The stub shafts of each pair are aligned and extend horizontally and transversely of the direction A. The common axes of the pairs of stub shafts 41 and 42 are disposed one behind the other (Figure 3) at approximately the level of a horizontal plane containing the axis of the leading roller 11. The stub shafts of each pair 41 and 42 are interconnected by a crank shaft 43. The inner ends of each pair of stub shafts 41 and 42 respectively are rigidly secured to crank webs 44 which extend at right angles to the stub shafts. One end of each crank web 44 carries a crank pin 45 which extends parallel to the stub shafts and is rigidly secured to the crank web. The length of each crankpin 45 is about one third of the distance between the side plates 9 and 10 (Figure 2).The inner ends of the crankpins 45 are rigidly secured to crank webs 46 extending parallel to the crank webs 44.

The mutually parallel crank webs 46 carry, at their ends opposite the crankpins 45, a crankpin 47A interconnecting the crank webs 46 and extending parallel to the crankpins 45. The crankpin 47A is rigidly secured to the crank webs 46. The length of the crankpin 47A is about one third of the distance between the side plates 9 and 10 and the crankpin 47A constitutes the central part of each crank shaft 43. The crankpin 47A, which is parallel to the crankpins 45, is situated on the other side of the axis of the respective stub shaft 41 and 42 from the crankpins 45.

The crankpins 45 and 47A carried by the stub shafts 41 are connected with corresponding crankpins 45 and 47A respectively carried by the stub shafts 42 in a direction parallel to the direction A by groups or assemblies of pressing means or tines 47 and 48 respectively mounted on the tops of the respective crankpins 45 and 47A. Each of these identical assemblies comprises a continuous bottom plate 49, which is upwardly bent over at its edge regions extending parallel to the direction A to form rows of tines 50. A further row of tines 51 extends parallel to the rows of plate-shaped tines 50 midway across the width of the bottom plate 49. The tines 51 are identical to the tines 50.The groups or sets of tines 47 and 48 have, as is shown in the side view of Figure 3, a length which is at least equal to the distance between the outwardly facing surfaces of the crank webs 44 in the position shown in Figure 1. In the embodiment shown (see the side view of Figure 3) each row of tines 50 and 51 has a tine 52 which is situated nearest the crankpins 45 and 47A respectively carried by the rear stub shafts 42, a tine 53 situated nearest the crankpins 45 and 47A respectively carried by the front stub shafts 41, and a tine 54 located approximately midway between the tines 52 and 53. The tines 52 to 54 of each group are directed upwardly, preferably vertically, from the associated bottom plate 49.The height of the middle tine 54 of each group 47 and 48 is larger than that of the tine 52 nearest the inlet opening 28, and the height of the front tine 53 is larger than that of the middle tine 54. The active edges of the tines 52 and 54 of each group, i.e. the edges facing the inlet opening 28, are approximately vertical, as shown in the side view of Figure 3. The edges of the tines 52 and 54 facing away from the inlet openings 28 are inclined upwardly and to the rear with respect to the direction of movement A. The edges of the front tines 53 facing towards the inlet opening 28 are inclined upwardly and to the front, and the edges of these tines 53 facing away from the inlet opening 28 are vertical.

The groups of tines 52 to 54 constitute pressing means for forcing crop into the winding space.

The bottom plates 49 of all of the assemblies 47 and 48 are fastened to bearings 55, which allow the assemblies 47 and 48 to pivot relatively to the associated crankpins 45 and 47A respectively. The axes of the stub shafts 41 and 42 and those of the crankpins 45 and 47A constitute the corners of parallelograms. Consequently, when the two crank shafts 43 are driven by means of sprockets 43A in the direction indicated by arrows 56 (Figure 3), the assemblies of tines 47 and 48 will invariably remain parallel to themselves while moving through a closed path. The assemblies 47 and 48 will alternately be in upper and lower positions as the assemblies 47 move in regions adjoining the side plates 9 and 10 and the assembly 48 passes through an intermediate region.

Scraping strips 57 are situated between the rows of tines 50 and 51, between the assemblies 47 and 48 and also between the assemblies 47 and the adjacent side plates 9 or 10. These scraping strips 57 are disposed just above the positions of the bottom plates 49, as shown in the sectional view of Figure 2, in the upper positions of the moving assemblies. As shown in the side view of Figure 3, the scraping strips 57 are bent downwards in front of and behind the pressing member 39 to terminate at carriers 58 which support the scraping strips 57 and which extend horizontally and transversely of the direction A. The carriers 58 are fixed with respect to the frame 1.

Near the front edges of the lateral boundary plates 37 of the pick-up device 33, there is a pivotal shaft 59 which is journalled in the plates and which extends horizontally and transversely of the direction A. A plurality of rearwardly extending, elastic rods 60 are fastened to the rear of this pivotal shaft 59. These rods 60 extend over the pick-up device 33 and also over the pressing member 39. The rear free ends of the rods 60 terminate near the inlet opening 28 and preferably in the wedge-shaped space indicated by the angle 40. The rods 60 extend between adjacent groups of tines 34 of the pick-up device 33, between adjacent rows of tubes 50, 51 of each group 47, 48 of the pressing member 39, between adjacent groups 47 and 48 and also between the groups 47 and the side plates 9, 10 (when the groups 47 and 48 are in their upper positions).When the baler is idle, the rods 60 preferably bear on the scraping strips 57 near their rear ends. As shown in Figure 3, the rear end portions of the rods 60 are slightly curved downwards and directed towards a corner of the wedgeshaped space represented by the angle 40. The rods 60 may be freely pivotable with respect to the plates 37, but alternatively tension springs 61 may be provided near the pivotal shaft 59 to bias the rods 60 downwardly. The groups of rods 60 may be pivotable independently about the pivotal shaft, and each rod may be loaded by its own tension spring 51, if desired. In an alternative embodiment the elastic rods 60 may be secured rigidly with respect to the plates 37 near the front edges of the plates.

During operation, the baler is moved by a tractor in the direction A across a field, from which crop is to be picked up. The pick-up device 33 picks up the crop from the ground by means of the tines 34 which are driven in the direction 36. The tines 34 deposit the crop on the scraping strips 38, from which the crop is fed to the pressing member 39.

The crop is introduced by the pressing member 39 into the wedge-shaped space, defined by the angle 40 (when a new bale is started) or pressed into it (at a later stage of bale formation). This process will be discussed in more detail later. The crop is then passed at the beginning of a bale forming process by the rollers 11 and 12 provided with extensions generally horizontally to the rear and then upwards in an inclined direction until the upwardly carried crop comes into contact with the transport member 14, which is then in its inwardly pivoted position. The crop is then downwardly coiled to initiate the formation of the bale core.As stated above the rollers 11, 12 and 27 as well as the transport member 14, 22 and 25 are driven in the directions indicated by the arrows 30 so that the core of the bale initially grows below the transport member 14 as indicated by the chain-dotted outline 62. When the bale has the size indicated by the outline 62, the top of the bale rotating in the bale forming chamber 8 comes into contact with the underside of the driven transport member 14, which rests on its stops under its own weight. The growing bale is thus shifted slightly towards the front, as indicated by the chain-dotted outline 63 in Figures 1 and 3. When the size indicated by the outline 63 is achieved, the top of the bale touches both the underside of the transport member 14 and the underside of the transport member 25.As the diameter of the bale increases further, it will thus lift the transport members 14 and 25, which turn about their pivotal shafts 13 and 14 respectively against their own weight, in the directions indicated by the arrows 20 and 26 respectively.

Since the weight of the transport members bears on the outer periphery of the growing bale, a relatively hard outer layer of the bale is formed from the time when it has reached a diameter which is, at least in this embodiment, approximately half of the final diameter. During the continued growth of the bale and the upward turning of the transport members 14 and 25, the top part of the cylindrical circumference of the growing bale contacts the inner end of the still inwardly directed transport member 22 so that as the diameter of the bale increases further, the bale also has to lift the transport member 22 against its own weight. As a result of this the outer layers of the bale are yet further uniformly hardened.The increase in diameter of the bale continues until the transport members 14, 22 and 25 reach their outermost positions, defined by stops and indicated in Figure 1 by dashed lines.

In this position, the transport members exert a further increasing pressure on the outer periphery of the bale until the tractor driver interrupts the drive to the rollers and to the transport members. Before doing so, the driver actuates a binding device (not shown) for wrapping twine or wire around the bale as it turns in the baler. Subsequently the rear part 4 of the baler is tilted upwards about the pivotal shaft 5 in the direction of the arrow B with respect to the front part 2 by means of two hydraulic rams 6 after which the fully formed bale is discharged from the device.

It should be noted that the transport members 14, 22 and 25 can be pressed downwards not only by their weight but also by additional means such as springs (not shown).

As the bale increases in diameter, the rollers 11 and 12 as well as the transport members 14 and 25, and, at a later stage, the transport member 25 and the roler 27, form a boundary of the bale, which, although generally cylindrical, is, in fact, polygonal (side elevation of Figure 1). The transport effect on the bale in a tangential direction by the rollers and the transport members is not uniformly distributed around the whole periphery of the bale despite the fact that the rollers are provided with small extensions and the transport members with slightly protruding transport rods 19. This non-uniform effect is more pronounced with bales having relatively hard outer layers as in the embodiment described.

In order to remedy this effect, the pressing member 39 is provided, the pressing means of which is disposed approximately at the level of the lower edge of the inlet opening 28, when these pressing means are in their working position. During upward movement at the front of the pressing member, the upwardly and forwardly bevelled front tines 53 carry along crop deposited by the pick-up device 33 on the scraping strips 38 towards the inlet opening 28. Each revolution of the crank shafts 43 moves the crop further to the rear under the action of the tines 52 and 54. By suitable selection of the diameter of the sprockets 43A the speed of revolutions of the crank shafts 43 is at least 1.2-times, and prefereably at least 1.4-times that of the rollers 11, 12, and 27 and the rollers 16, 21 and 24 of the transport members 14, 22 and 25 rotating in the same direction. Therefore, in principle, the feed rate achieved by the pressing members 39 exceeds the tangential speed of the bale to be formed. The tines 52 and 54, whose rearwardly directed boundary lines always remain vertical, thus exert a pressure on the crop pushed into the above-mentioned wedge-shaped space represented by the angle 40.

This propelling force exerted tangentially with respect to the bale circumference (to which the rotation of the rollers 11 contributes) is to the full benefit of the torque exerted on the bale. At the level of the operating groups of tines 47 or 48 a high pressure can be built up in connection with the horizontal length (viewed parallel to the direction of movement A or the transport direction of the crop). This is possible as a result of the presence of the sequence of tines 52, 54, 53 of each group 47, 48, in which the tines increase in height in the direction A. Consequently, the pressure can be uniformly built up in the direction towards the inlet opening 28.The length of the assemblies 47, 48 of the tines of the pressing member 39, measured in the direction A, has, therefore, a value which is at least substantially equal to the vertical height 64 of the inlet opening 28 (Figure 3) and preferably at least equal to the width 65 of the inlet opening 28 measured directly between the roller 29 and the front roller 11.

The height of the tines 52, 54, 53, measured from the top face of the scraping strips 57, is in the illustrated embodiment at least approximately 15, 20 and 25% respectively of the height 64. Depending on the circumstances in which the baler is to be used (such as the nature of the crop: short, long, moist or dry) the tines of the assemblies 47 and 48 may have greater heights, for example heights of about 30 to about 60% of the height 64.

If appreciable assistance for the rotation of the bale or hardening of the layers of the bale is desired, the length of the assemblies 47 or 48, measured parallel to the direction A or to the transport direction of the crop, may be about twice the height 64 or 65.

The crop pressed by the tines of the pressing member 39 into the wedge-shaped space also contributes to a greater hardness of the layers of the bale to be formed.

The presence of the rods 60 between the assemblies 47, 48 ensures that the crop will be pressed in the desired direction into the wedge-shaped space.

Depending upon the dimensions, it is often desirable for the free rear ends of the crop guiding rods 60 to bend slightly downwards, away from the region where the pressure in the crop is built up, towards the angle 40 of the wedge-shaped space, so that the crop cannot readily bend in a direction differing from the desired direction. A large number of adjacent rods 60 ensures a straight guidance of the crop in the desired direction. The rods 60 can adapt themselves upwardly and downwardly to the stream of crop. The rods tend to maintain their lowermost position under their own weight and, if desired, by the action of the springs 61. Since the rods 60 bridge both the pressing member and the pick-up device 33, the total length of the rods, i.e.

the distance between the free rear ends of the rods and the pivotal shaft 59 is relatively large, so that deflection of the rods 60 caused by movements of the crop can have only little influence on the direction in which the rear ends of the rods extend. The length of the rods is preferably at least about twice the length of the pressing member measured in the direction A.

Owing to the parallelogram-like movement of the groups of tines 47, 48, the orientation of the edge of the flat tines facing the inlet opening 28 is maintained. Consequently, during downward movement of the tines, the pressure will not prematurely fall.

The rearmost edges of the tines 52 and 54, which are vertical in this embodiment, may, if desired, be inclined upwardly and to the rear with respect to the direction A in order to exert a slightly downwardly directed pressure towards the wedgeshaped space.

The crop is alternately pressed by the assemblies 47 in the regions near the side plates 9 and 10 and by the assembly 48 in the intermediate region into the wedge-shaped space so that a satisfactory distribution of the crop in a transverse direction and a satisfactory entanglement of the crop in that direction are ensured.

The number of tines distributed in the direction A of each assembly 47 and 48 can be greater than the three tines in the embodiment shown, when, as stated above, the effective length of each assembly is increased. This also depends on the conditions under which the baler is to be used. For example, in the case of short crop it may be desirable for the pressing member to be relatively long and to have a larger number of tines on each assembly 47,48 compared with the case in which mainly long stalked crop is to be harvested.

It should be noted that the pressing member 39 can be used not only in balers as described above, but also in balers having a bale forming chamber of constant shape and size, for example, balers having a large number of rollers and/or transport members arranged along a cylindrical plane which may be compared with the transport members 14, 22, 25 (provided with transport rods or endless belts), when the latter are fixed in a position which may be compared with the outermost position indicated by dashed lines in the embodiment of Figure 1.

The pressing member 39 is arranged outside the bale forming chamber 8. It is, however, conceivable to replace, for example, the rollers 11 and/or the rollers 12 by a pressing member of the same construction as the pressing member 39. The tines 52 to 54 of such a pressing member would have a relatively small height and the driving speed at the area of the tines would be substantially equal to that of the further transport members or rollers, or slightly higher. During formation of a bale, these tines would penetrate into the outer periphery of the bale and thus contribute appreciably to the torque exerted on the bale.The rotation of the bale is generally hindered not only where the shape of the bale forming chamber differs from a purely cylindrical shape, but also (and to a considerable extent) by the friction produced by the pressure of the end faces of the bale against the inner faces of the two side plates 9 and 10. It is furthermore noted that fully formed bales of different diameters can be formed by the baler described above if the above-mentioned stops defining the outermost positions of each of the tiltable transport members 14, 22 and 25 are supplemented by further stop in the side plates 9, 10, which stops define at least one further outermost position of each of these transport members. This further outermost position is between the innermost position and the originally mentioned outermost position (defining the maximum attainable diameter of the bale).

Each further stop can be fitted or removed as desired by the operator before starting the operation of the baler. The added, outermost stops are preferably arranged near the arc of a circle described by the shaft of the inner rollers of the transport members during their upward turn.

Figures 4 to 6 show an alternative embodiment of a baler which differs from the previous embodiment by having other types of pivotable driven transport members replacing the transport members 14, 22 and 25 of the preceding embodiment.

It is apparent from Figure 4 that, with respect to the direction A, the front transport member 25 is replaced by a transport member 66, the rear transport member 14 is replaced by a transport member 67 and the upper transport member 22 is replaced by a transport member 68. It will be appreciated that only some of these replacements may be made.It should be noted that the pivotability of the transport members 66 to 68 from an extreme inner position determined by stops (assumed when the bale forming chamber 8 is empty or at the beginning of bale formation) to an outer position determined by stops (assumed when the bale forming space 8 contains a fully formed bale), the pressure applied by the transport members under their own weight and, as the case may be, by spring load, on the circumference of the bale, and the chain drive of the transport members are similar to those described for the transport members 14, 22 and 25, unless stated otherwise. The position of each transport member shown in Figure 4 is the outermost position determined by stops and corresponds to the largest bale diameter.

The rear transport member 67 is pivotable about a horizontal pivotal shaft 13 which extends transversely of the direction A and is situated, as shown in the side view of Figure 4, approximately at the level of tiZentre of a fully formed bale 81 in the bale forming chamber 8. In the outermost position shown, determined by stops, the transport member 67 extends upwardly away from the pivotal shaft 13. The transport member 67 has two pairs of sprockets 69 and 70, one pair being disposed adjacent each side plate 9 and 10. A chain 71 runs over the sprockets 69 and 70. Transport rods 72 are fastened to the chain 71 and extend parallel to the pivotal shaft 13 over substantially the whole distance between the side plates 9 and 10. The chain 70 also passes along a sprocket 73 situated on the side of the transport member 67 facing away from the winding space 8.

A frame beam 74 of the transport member extends adjacent each of the side plates 9 and 10.

Each frame beam 74 is pivotable at one end about the pivotal shaft 13 and carries at the other end a pivotal shaft 75, about which the sprocket 70 is rotatable. The two spaced frame beams 74 of the transport member 67 are rigidly interconnected by a transverse beam (not shown).

The sprockets 73 located near the side plates 9 and 10 are freely rotatable about a shaft 76, which extends over the whole width between the side plates 9 and 10, like the shafts 13 and 75. Near each end, the shaft 76 is journalled in the arm 77, which, at least in the illustrated position of the transport member 67, is upwardly and forwardly inclined towards the frame beam 74 and is pivotally connected by a pivotal shaft 78 to the frame beam 74 at a position between the shafts 13 and 75.

The arm 77 and the sprocket 73, which together form a tensioning device for the chain 71, are fixed relatively to the frame beam 74 during operation, since each arm is rigidly secured to the frame beam 74 by fixing means. These fixing means (not shown) may comprise flat arcuate strips centred on the pivotal shaft 78, one strip being rigidly connected with the arm 77 and the other with the frame beam 74. Each strip has a large number of locking holes by means of which the strips (and hence the arm 77 and the frame beam 74) can be locked in any one of a plurality of different relative positions by passing a locking pin (near each side plate 9,10) through aligned holes of the strips.

Thus, the arm 77 can be turned with respect to the frame beam 74 and fixed in any one of a plurality of positions. Displacement of the arm 77 relative to the beam 74 is, however, only carried out when the baler is not in use, in order to tension the chains 71 should they have become slightly too slack during operation. During operation, each arm 77 is fixed relative to its frame beam 74.

In operation, the operative part of the transport means 71, 72 facing the bale forming chamber 8, will come into contact, at least over part of its length, with the approximately cylindrical outer periphery of the growing bale. The contact force produced by the weight of the transport member 67 and any downwardly acting spring means contributes not only to the exertion of a torque on the outer circumference of the bale but also to an increase in hardness of the then outer layers of the bale.

As in the preceding embodiment, the transport means 71, 72, 67 is driven in the direction 30 by means of a sprocket on the outboard side of the side plate, which is drivable from the gear wheel transmission 31 and is drivably connected to the sprocket 69.

The transport rods 72 shown only schematically in the Figures may comprise tubes of circular or rectangular cross-section which are spaced apart by a distance corresponding to about once or twice the diameter of the pipes. As an alternative, they may comprise strips of sheet material, preferably U-shaped strips, the limbs of the U being directed towards the frame beam 74. These strips are preferably disposed side by side transversely of the di rection A in a manner such that there is a small gap between adjacent strips.

The transport member 68 is, at least in the illustrated embodiment, similar to the transport member 67. From its pivotal shaft 13 (Figure 4) the transport member 68 extends in the illustrated position (corresponding to the bale forming chamber 8 being completely filled) substantially horizontally to the front, and bears on the top of the bale filling the bale forming chamber 8.

The front transport member 66 has, at least in the illustrated embodiment, a construction differing from that of the transport members 67 and 68. As shown in the side view of Figure 4, the transport member 66, also intended for turning the growing or completed bale in the bale forming chamber 8, is pivotally connected to the side plates 9 and 10 by means of a pivotal shaft 79 situated between its ends rather than by means of a pivotal shaft situated near one end of the transport member. As is shown in Figure 4, the frame of the transport member 66, unlike that of the transport members 67 and 68, has a curved, banana-shaped form (see also Figure 6). The frame of the transport member 66 comprises parallel frame beams 80 disposed near the side plates 9 and 10.Each beam 80 comprises a U-section profile which is upwardly and rearwardly inclined away from the pivotal shafts 79 journalled in the side plates 9, 10 when the bale forming chamber contains a completed bale, and extending rearwardly and inwardly when the bale forming chamber 8 is empty. The disposition is such that, when the bale forming chamber 8 contains a completed bale 81, the top end of the frame beam 80 is nearest the periphery of the bale 81, whereas the lower end of the frame beam 80, bear the pivotal shaft 79, is spaced from the periphery of the bale 81 by a distance which is about 10 to 20%, preferably about 15% of the diameter of the bale 81 indicated in Figure 4.

Figure 6 shows that each frame beam 80 is provided, near the pivotal shaft 79, with a flat carrier plate 82. The carrier plate 82 is welded to the beam 80 on the side facing into the bale forming chamber 8, and is parallel to the adjacent side plate 9 or 10 respectively. At its end away from the frame beam 80, the carrier plate 82 supports a shaft 83, which extends over substantially the whole distance between the side plates 9 and 10. The ends of the shaft 83 project beyond the two carrier plates 82 and are provided with sprockets 84 (Figures 5 and 6).

The two ends of the pivotal shaft 79 projecting beyond the frame beams 80 are provided with drivable sprockets 85, which is in the same plane as with the sprocket 84, as shown in Figure 5. The pivotal shaft 79 extends through the side plate 9 beyond its bearing in that plate. This projecting end carries a sprocket 86 (Figure 5), which is rigidly secured to the shaft 79 and can be driven by means of chain transmissions from the gear wheel transmission 31. Thus the shaft 79 constitutes both a pivotal shaft for the freely pivotable frame 80, 82, and, through the driving connection between the sprockets 85 and 86, a drive shaft for a chain 87 passing around the sprockets 84 and 85. This chain 87 passes around the sprockets 84 and 85 disposed near the side plate 10.As in the other transport members 67 and 68, transport rods 19 are fastened to the links of the chain 87 and extend over substantially the whole distance between the side plates 9 and 10. The transport rods 19 are shown in Figures 5 and 6 with a circular cross-section, but they could be replaced by other rods as mentioned above.

The end of each of the two frame beams 80 further from the shaft 79 is provided with a sprocket 88, which is freely rotatable about a shaft 89 journalled in the respective frame beam 80 (Figure 4).

Each sprocket 88 guides the respective chain 87 provided with the transport rods 19.

At a distance from the shaft 79 which is about 20 to 30% of the overall length of each frame beam 80, the two frame beams 80, situated near the side plates 9 and 10 respectively, are rigidly interconnected by a hollow member or a tube 90, which extends horizontally at right angles to the direction A and hence parallel to all of the transport rods 19.

The connecting member 90 projects for a relatively short distance beyond each of the frame beams 80 to terminate near the adjacent side plate 9 or 10.

As shown in Figure 5, the member 90 projects beyond the outer boundary of the adjacent chain 87.

Thus the connecting member 90 and the two frame beams 80, 82 constitute a rigid unit.

The member 90 has a rectangular cross-section (square, as illustrated). The interior of the member 90 accommodates throughout its length a solid bar 91 having, as is shown in Figure 6, a rectangular cross-section (also square, as illustrated). The disposition of the bar 91 relative to the member 90 is such that, in the no-load state, an angle of the bar 91 (Figure 6) is disposed approximately in the middle of an inner boundary face of the member 90, the boundary faces of the bar 91 forming the angle being inclined at an angle of 45" to the inner boundary face of the beam 90. The dimensions of the section of the bar 91 are such that turning of the bar 91 relative to the member 90 surrounding it is not obstructed by the member.In the no-load position, the corners of the section of the bar 91 are situated as close as possible to the inner boundary faces of the member 90.

As shown in Figure 6, four spaces are defined between the boundary faces of the bar 91 and the inner boundary faces of the member 90. These spaces have the shape of right-angled triangles in cross-section. Each of these four triangular spaces contains a rod 92, which extends over the whole length of the member 90. Each of these rods 92 is made from elastic material such as rubber, preferably a hard rubber or an elastic synthetic resin, so that turning of the bar 91 with respect to the member 90 about their common centre line is elastically resisted. Each of the elastic rods 92 has a circular, solid cross-section when unloaded in the illustrated embodiment, but rods of other cross-section may be used.

The bar 91 projects at both ends from the member 90 for a short distance. An arm 93 is rigidly se cured to each projecting end of the bar 91. Each arm 93 is at right angles to the centre lines of the member 90 and the bar 91 is parallel to the adjacent side plate 9 and 10 respectively. As shown in Figures 4 and 6, the arm 93 extends to that side of the frame beam 80 which is further from the side of the transport member 66 which is loaded by the bale during operation. The longitudinal axis of each arm 93 approximately intersects the axis 83, the arm 83 being disposed on the opposite side of the bar 91 to the axis 83. The angle between the arm 93 and the frame beam 80, as viewed from the side, is about 45" when the transport member 66 is loaded by the bale. At the end of each of the two arms 93 away from the bar 91 there is a shaft 94.

The shaft 94 is journalled in the arms 93 and a sprocket 95 is fastened to it (Figure 4). The chains passing over the sprockets 84, 85 and 88 also run over the sprockets 95.

It is noted that, as viewed outwardly from the winding space 8, the frame of the transport member 66 has a concave shape since the carrier plate 82 carrying the sprocket 84 is at an angle to the frame beam 80. In this way the chain 87, which is in contact with the cylindrical periphery of the bale during operation and which is deflected by the pressure of the bale in the direction towards the frame of the transport member 66, is prevented from touching frame parts of the transport member 66. This design of frame can be used independently of the features of the described baler.

As shown in the side view of Figure 4, a drivable feed roller 96 is situated approximately perpendicularly below the pivotal shaft 79 of the transport member 66, some distance in front of the sprocket 84. The roller 96 can be driven about a horizontal shaft 97 extending transversely of the direction A from the gear wheel transmission 31. The roller 96 can be driven in the direction indicated by an arrow 98. The roller 96 thus cannot come into contact with the circumference of the bale and consequently the direction of rotation 98 can be chosen so that the roller 96 contributes to the supply of the crop in the direction towards the inlet opening 28 and thus co-operates with the pressure member 39. Preferably, the roller 96 is provided with small projections.The roller 27 of the first embodiment cannot fulfil this task because it engages the bale and so has to be driven in the opposite direction. Because the roller 96 is situated in front of and slightly below the lower part of the transport member 66 (i.e. the sprocket 84) (Figure 4), crop moved downwards by the transport member 66 in the direction of rotation 30 of the bale and tending to leave the surface of the bale in the region of the lower sprocket wheel 84 is returned by the roller 96, cooperating with the pressure member 39 and the incoming crop, in the direction towards the corner of the wedge-shaped space 40 (see Figure 3). Occasional occurrence of this phenomenon is thus avoided.

The pivotal shaft 79, about which the transport member 66 is pivotable as a whole, is at approximately the same level as the pivotal axis of the transport member 26 (i.e. the axis of the roller 24 of Figure 1), that is to say, approximately at the same level as the centre line of a fully formed bale of maximum permissible diameter, and is parallel to that centre line. Therefore, compared with the transport member 26 the transport member 66 is extended in the direction towards the inlet opening 28 by the carrier plates 82, the shaft 83, and the sprockets 84. Thus the transport member 66 can, so to say, balance about its pivotal shaft 79 under the influence of its weight.The centre of gravity of the transport member 66 is approximately in the region of the member 90 (i.e. between the pivotal shaft 79 and the shaft 89) and always on the same side of the pivotal shaft 79 as the bale forming chamber 8. The transport member 66 thus always tends to turn anti-clockwise, as indicated by an arrow 99 under its own weight and, as the case may be, the action of spring means (not shown), which are not required. Owing to the concave shape of the frame, the operative part of the transport means 19, 87 which is pressed against the periphery of the forming bale can engage the bale periphery over a length which is appreciably larger than in the case of the transport member 25 (Figure 1) so that the torque driving the bale and exerted by the drivable transport member 66 also exceeds that of the transport member 25.The transport member 66 can constantly remain in contact with the periphery of the bale over the full length between the sprockets, turning about the pivotal shaft 79 as the bale increases in diameter.

As viewed from the bale forming chamber 8, the pivotal shaft 79 is parallel to and between the lower and upper, horizontal boundaries of the operative part of the transport means 19, 87 engaging the bale.

The extra length of the transport member 66 compared to the transport member 25 means that the bale can be supported up to the inlet opening 28 so that the crop entering through the opening 28 can smoothly join a bale surface which has already been compressed by the transport member 66. This downward extension means that the crop is prevented from falling off the partly formed bale in the region of the inlet opening 28, which crop would disturb the flow of the entering crop.

Experience has shown that a strongly consolidated bale core, which is highly important for silage, is initially formed mainiy in the rear part of the bale forming chamber 8. During the first stage of the bale formation the downward extension of the transport member 66 urges the bale towards the rear of the chamber for a fairly long time so that bales having a relatively high core density can be formed (under the action of the transport member 67 then having turned downwards). This is highly important when forming relatively small bales (diameter of about 1.2 ms) of straw.

The transport member 66, balancing about the pivotal shaft 79 and extending up to the inlet opening 28, contributes to the formation of a substantially purely cylindrical shape of the bale both during the increase in the bale diameter and at the end of the bale formation also because at the area of the inlet opening 28 the bale is prevented from bulging downwardly, which would hinder rotation of the bale in the bale forming chamber 8 and disturb the application of entering crop to the surface of the bale.

As the diameter of the bale increases during operation, the bale periphery at a given stage of the bale formation will touch the part of the then downwardly turned transport member 66 at a position above the pivotal shaft 79, which part will thus be turned upwards in a direction opposite the arrow 99. The part of the transport member 66 below the pivotal shaft 79 is pressed in an early stage against the bale surface so that turning of the upper part in the direction opposite the arrow 99 is resisted. This means that even at an early stage in the bale formation, a considerable density of the bale can be obtained. Therefore, the balancing transport member 66 will contribute to the formation of bales having a relatively higher density throughout its diameter.

The resilient arm 93 and the sprocket 95 provide tensioning means for the driven transport means (chain 87 and transport bars 19). During operation, the resiliently mounted bar 91 produces an elastic force constantly tending to increase the angle between the arm 93 and the upper part of the frame beam 80 when the operative part of the transport means 19, 87 engaging the bale periphery is curved in the direction towards the frame beam 80.

The elastic connection between the tensioning means 93 to 95 and the frame beam 80 thus constantly tends to tauten the chain 87 during operation, contrary to the tensioning devices described above for the transport members 67 and 68, which are fixed during operation and which can be adjusted only during idle periods. Owing to the elastic tensioning device, the tensioning force of the chain 87 increases as the curvature of the bale increases, since the resilient force tending to urge the arms 93 forwardly increases as the operative part 19, 87 engaging the bale is further curved.

Therefore, the pressure exerted on the bale and hence the density of the bale are relatively great even when the bale diameter is small.

The bar 91 will itself operate also as a torsion bar. As an alternative the elastic rods 92 may be omitted and the bar 91 may be clamped rigidly with respect to the hollow member 90 in the middle of its length so that the bar 91 absorbs in both parts of its length an identical torsional moment.

The transport members 67 and 68 may also be provided with tensioning means for the circulating chain in the manner described with reference to the transport member 66, so that the tensioning means 90, 91, 92 used for the arms 77 then also act resiliently during operation.

It is furthermore possible to replace the transport members 67 and/or 68 described above by a transport member similar to the transport member 66, i.e. with a curved frame and a balancing suspension.

Whilst various features of the balers that have been described, and that are illustrated in the drawings, will be set forth in the following claims as inventive features, it is to be noted that the invention is not necessarily limited to these features and that it encompasses all of the features that have been described both individually and in var ious combinations.

Claims

1. A baler for forming cylindrical bales of crop, comprising a bale forming chamber having an inlet opening and a pick-up device for picking up crop from the ground, a pressing member being provided between the pick-up device and the inlet opening for pressing crop into the bale forming chamber, the effective dimension of said member, measured in the transport direction of the crop into the bale forming chamber, being not less than substantially equal to the upwardly measured dimension of the inlet opening.

2. A baler as claimed in claim 1, in which the effective dimension of the pressing member is about twice the upwardly measured dimension of the inlet opening.

3. A baler as claimed in claim 1 or 2, in which the operative part of the pressing member is disposed approximately at the level of the underside of the inlet opening.

4. A baler as claimed in any one of the preceding claims, in which the pressing member comprises pressing means distributed across the whole effective width of the baler.

5. A baler as claimed in any one of the preceding claims, in which the pressing member comprises means disposed one behind another, as viewed from the side.

6. A baler as claimed in claim 3, 4 or 5, in which the pressing means comprises tines which are movable in operation in the direction towards the inlet opening.

7. A baler as claimed in claim 6, in which tines of the pressing member disposed further from the inlet opening have a greater effective height than tines of the pressing member disposed nearer the inlet opening.

8. A baler as claimed in claim 7, in which the effective height of the tines is substantially 15 to 60% of the upwardly measured dimension of the inlet opening.

9. A baler as claimed in any one of claims 6 to 8, in which, during their movement towards the inlet opening, the orientation of the tines remains the same.

10. A baler as claimed in any one of claims 6 to 9, in which the effective sides of at least some of the tines are substantially vertical.

11. A baler as claimed in any one of claims 6 to 9, in which the effective sides of at least some of the tines are inclined upwardly and forwardly in the direction towards the inlet opening.

12. A baler as claimed in any one of claims 4 to 11, in which the pressing means is movable, in operation, towards the inlet opening at an effective speed exceeding the peripheral speed of a bale rotating in the bale forming chamber.

13. A baler for forming cylindrical bales of crop, comprising a bale forming chamber having an inlet opening and a pick-up device for picking up crop from the ground, pressing means being provided which, in operation, pushes the crop into the inlet opening, the pressing means being movable, in operation, towards the inlet opening at an effective speed exceeding the peripheral speed of a bale rotating in the bale forming chamber.

14. A baler as claimed in claim 12 or 13, in which the effective speed of the pressing means is at least 1.2 times, preferably 1.4 times, the peripheral speed of the bale.

15. A baler as claimed in any one of claims 4 to 14, in which the pressing means is connected to two drivable crank shafts which are coupled together by the pressing means.

16. A baler as claimed in claim 15, in which the crank shafts are drivable about horizontal axes which extend transversely of the intended direction of travel of the baler, and which lie in a substantially horizontal plane.

17. A baler as claimed in claim 15 or 16, in which the pressing means is pivotally connected with crankpins of the two crank shafts.

18. A baler as claimed in any one of claims 15 to 17, in which, across the width of the baler, the pressing means are alternately connected to crankpins on different sides of the shafts.

19. A baler as claimed in any one of claims 4 to 18, in which the pressing means are constructed in the form of flat tines, each of which is parallel to the intended direction of travel of the baler.

20. A baler as claimed in claim 6 or in any one of claims 7 to 19 when appendant to claim 6, in which the tine nearest the pick-up device has an effective side which is inclined upwardly and rearwardly, in the direction away from the inlet opening.

21. A baler as claimed in claim 6, or in any one of claims 7 to 20 when appendant to claim 6, in which the pressing member comprises nine rows of tines distributed transversely of the direction of travel of the baler.

22. A baler as claimed in any one of claims 4 to 21, in which substantially horizontal rods extend between the pressing means, the rods being supported in front of the pressing member, with respect to the intended direction of travel of the baler.

23. A baler as claimed in claim 22, in which the rods are elastic and rigidly supported.

24. A baler as claimed in claim 22, in which the rods are upwardly and downwardly pivotable about a pivotal axis extending substantially horizontally and transversely of the intended direction of travel of the baler.

25. A baler as claimed in claim 24, in which upwards pivoting of the rods is resiliently resisted.

26. A baler as claimed in any one of claims 22 to 25, in which the rods are supported at a position which is spaced in front of the inlet opening by a distance which is at least twice the effective length of the pressing member.

27. A baler as claimed in any one of claims 22 to 26, in which the rods have free ends situated near the inlet opening.

28. A baler as claimed in claim 27, in which the free ends extend into the inlet opening.

29. A baler as claimed in claim 27 or 28, in which the free ends are downwardly directed.

30. A baler as claimed in any one of the preceding claims, in which the bale forming chamber has dimensions which vary during formation of a bale.

31. A baler as claimed in any one of claims 1 to 29, in which the bale forming chamber of the device has dimensions which are fixed during formation of a bale.

32. A baler as claimed in any one of claims 1 to 30, in which the bale forming chamber is at least partially defined by first and second elongate, pivotable transport members, one end of the first transport member being pivotally mounted near the front of the bale forming chamber, and one end of the second transport member being pivotally mounted near the rear of the bale forming chamber.

33. A baler as claimed in claim 32, in which a third pivotable, elongate transport member is provided, one end of which is pivotally mounted near an upper part of the baler.

34. A baler as claimed in claim 32 or 33, in which the or each transport member is pivotable from an inner position defined by a stop into an outer position defined by a stop.

35. A baler as claimed in claim 34, in which the movement from the inner position to the outer position of at least one of the transport members takes place against an oppositely directed force.

36. A baler as claimed in claim 35, in which the oppositely directed force is produced by the weight of the transport member.

37. A baler as claimed in claim 35 or 36, in which the oppositely directed force is produced by a spring.

38. A baler as claimed in any one of claims 34 to 37, in which the movement from the inner position to the outer position of at least one of the transport members is produced by the bale increasing its diameter.

39. A baler as claimed in any one of claims 34 to 38, in which at least one further, optionally selectable outer stop is provided, which defines the diameter of a fully formed bale which is smaller than the maximum attainable bale diameter defined by the outermost stop.

40. A baler as claimed in claim 39, in which the further outer stop can be mounted and dismounted.

41. A baler as claimed in any one of claims 32 to 40, in which at least one of the transport members comprises two endless belts passing around two mutually parallel axes.

42. A baler as claimed in any one of claims 32 to 40, in which at least one of the transport members comprises two spaced chains which pass around two mutually parallel axes and are interconnected by transport rods.

43. A baler as claimed in claim 41 or 42, in which the transport member is driven by a drive shaft at only one of the axes.

44. A baler as claimed in any one of the preceding claims, in which at least one transport member has an operative surface which, in use, engages a bale lying in the bale forming chamber, the transport member being pivotable about a pivotal axis which, as viewed from the bale forming chamber, is spaced from the horizontal boundaries of the operative surface.

45. A baler for forming cylindrical bales of crop, comprising a bale forming chamber having a crop inlet opening, at least one transport member being provided which has an operative surface which, in operation, engages a bale lying in the bale forming chamber, the transport member being pivotable about a pivotal axis which, as viewed from the bale forming chamber, is spaced from the horizontal boundaries of the operative surface.

46. A baler as claimed in claim 44 or 45, in which the transport member is freely pivotable about the pivotal axis.

47. A baler as claimed in claim 44 or 45, in which the transport member is pivotable about the pivotal axis under spring action.

48. A baler as claimed in any one of claims 44 to 47, in which the pivotal axis is horizontal and extends transversely of the intended direction of operative travel of the baler.

49. A baler as claimed in any one of claims 44 to 48, in which the pivotal axis is substantially parallel to the centreline of a bale in the bale forming chamber.

50. A baler as claimed in any one of claims 44 to 49, in which the centre of gravity of the transport member is situated above the pivotal axis and on the side nearer the interior of the bale forming chamber.

51. A baler as claimed in any one of claims 44 to 50, in which the lower horizontal boundary of the operative surface defines approximately the upper boundary of the inlet opening.

52. A baler as claimed in any one of claims 44 to 51, in which the transport member bounds the inlet opening.

53. A baler as claimed in any one of claims 44 to 52, in which the pivotal axis is situated approximately at the same level as the centre line of a fully formed bale lying in the bale forming chamber.

54. A baler as claimed in any one of claims 44 to 53, in which the transport member comprises a frame which supports drivable transport means having the operative surface for turning a bale forming in the bale forming chamber, the frame, as viewed from the bale forming chamber, being concave and being disposed behind the operative surface.

55. A baler as claimed in any one of claims 32 to 54, in which the transport member comprises resilient tensioning means for circumferentially tensioning the transport means in operation.

56. A baler for forming cylindrical bales of crop, comprising a bale forming chamber which is partly bounded by a transport member which has drivable transport means for turning a bale lying in the bale forming chamber, the transport member having elastic tensioning means for circumferentially tensioning the transport means in operation.

57. A baler as claimed in claim 55 or 56, in which the tensioning means comprises a sprocket for tensioning and guiding the transport means, the sprocket being journalled on an arm which is resiliently pivotably connected to a frame part of the transport member.

58. A baler as claimed in claim 57, in which the arm is connected to a bar which is disposed at least partly within a tube which is rigidly secured to the frame part, the bar partly filling the tube.

59. A baler as claimed in claim 58, in which both the bar and the tube have a rectangular crosssection, the boundary faces of the bar and the tube being inclined to one another.

60. A baler as claimed in claim 58 or 59, in which the space defined between the bar and the tube is filled at least partly by at least one elastic member.

61. A baler as claimed in claim 60, in which the elastic member is a rod.

62. A baler as claimed in claim 60 or 61, in which the elastic member comprises an elastomeric material.

63. A baler as claimed in any one of claims 60 to 62, in which the elastic member comprises a synthetic resin.

64. A baler substantially as described herein with reference to, and as shown in, Figures 1 to 3 or Figures 4 to 6 of the accompanying drawings.