Patent Description:
Agricultural tools are known comprising a machine body equipped with a motor and a utensil configured to make the fruit fall, which is connected to the machine body motor by means of a mechanical transmission. In particular, agricultural tools of the harvester type are equipped with a utensil comprising a pair of combs that cause the fruit to fall by means of fast vibration (over <NUM> beats per minute).

For example, an olive shaking machine used in olive harvesting is known from <CIT>. This machine is a so-called "olive harvester" and provides high torque at low speeds by transmitting the rotational movement received from the engine's drive gears to a plurality of timing gears, and to the curved connecting rods by means of the timing gears.

At operational level, each comb is moved according to a tilting movement. The pair of combs is typically moved at the same frequency. Together, the combs define a plurality of mutual movement configurations depending on the timing of the tilting movement of the combs themselves. In the field covered by the present invention, depending on parameters such as the size and type of fruit tree as well as the size and state of ripeness of the fruit to be harvested, it is known to employ a specific comb operating configuration. In particular, two mutual comb movement configurations are known to be very efficient: a first configuration in which the combs are moved in phase and a second configuration in which the combs are moved in counterphase.

A strongly felt need is therefore to be able to convert the mutual movement configuration of the combs (in particular by switching from the phase configuration to the counterphase configuration and vice versa) so that the harvester can be adapted to operate optimally according to these parameters. One attempt to solve this need has been to sell harvesters with the head tool (i.e. the pair of combs) interchangeable. In particular, the machine body of the harvester is known to be sold in combination with two or more head tools, each configured to operate at a predetermined configuration of mutual comb movement.

The Applicant has noted that, even in their most modern implementations, the systems described above have certain disadvantages.

Firstly, such systems have an operational disadvantage. In fact, the operator is forced to repeatedly change the head utensil in order to adapt the harvester to the plant variety on which he is operating so as to optimise the harvesting process. However, this practice is cumbersome and inefficient in terms of operational timing.

Secondly, such systems are disadvantageous in economic terms since, in addition to the cost of the machine body, the operator must also take into account the economic outlay associated with the two or more head utensils.

Furthermore, the continuous replacement of head utensils together with strong operating vibrations can result in damage to the mutual coupling means of the head utensil of the machine body.

In this context, the technical task of the present invention is therefore to make available a portable agricultural tool, such as a harvester, that is free of the drawbacks complained of in the known technique.

The purpose of the present invention is therefore to make available a portable agricultural tool, such as a harvester, that is versatile and at the same time inexpensive and easy to use.

A further purpose of the present invention is to make available a portable agricultural tool, such as a harvester, with a simplified structure that is more resistant to damage.

The purposes are substantially achieved by a portable agricultural tool, such as a harvester, in accordance with the characteristics set forth respectively in the accompanying claim <NUM>. Preferred aspects are defined by the accompanying dependent claims.

Further features and advantages of the present invention will become more apparent from the approximate and thus non-limiting description of a preferred, but non-exclusive, embodiment of a portable agricultural tool, as illustrated in the accompanying drawings, wherein:.

With reference to the accompanying figures, the numerical reference "<NUM>" indicates a portable agricultural tool. Preferably, the tool <NUM> is of the "harvester" type. However, the present invention is extended to any portable agricultural tool presenting a utensil comprising two elements that are mutually movable according to a periodic movement, in accordance with the generality of the invention.

The tool <NUM> comprises a machine body, not illustrated, comprising a motor <NUM> configured to selectively operate in a first drive direction and a second drive direction opposite the first drive direction. In other words, functionally, the operator can selectively drive the motor <NUM> in the first drive direction or in the second drive direction. Preferably, the tool <NUM> comprises an operator-driven control connected to the motor <NUM> and configured to switch the tool <NUM> on and off and to switch the drive direction of the motor <NUM>.

The machine body has a rod that extends longitudinally along a longitudinal axis "Z".

The tool <NUM> comprises a utensil <NUM> operatively arranged on one end of the rod. The tool <NUM> is connected to the motor <NUM> by means of a mechanical transmission <NUM>. The tool <NUM> comprises a first comb <NUM> and a second comb <NUM> connected to the motor <NUM> by means of the aforementioned mechanical transmission <NUM>.

Preferably, the combs <NUM>, <NUM> have a mutually specular conformation with respect to the longitudinal axis "Z" of the tool <NUM>.

The mechanical transmission <NUM> comprises a first connecting rod-crank mechanism <NUM> configured to move the first comb <NUM> and a second connecting rod-crank mechanism <NUM> configured to move the second comb <NUM>.

Structurally, each connecting rod-crank mechanism <NUM>, <NUM> comprises a main body <NUM>, <NUM> fitted to rotate about a respective axis of rotation "X", "Y". In use, the main bodies <NUM>, <NUM> are mutually concordant in rotation. Each connecting rod-crank mechanism <NUM>, <NUM> further comprises a connecting rod <NUM>, <NUM> having a first end 102a, 202a hinged to the respective comb <NUM>, <NUM> and a second end 102b, 202b hinged to the main body <NUM>, <NUM>. In particular, the second end 102b, 202b of the connecting rod <NUM>, <NUM> is hinged to the main body <NUM>, <NUM> in a respective crank pin <NUM>, <NUM>.

Preferably, as can be seen in the accompanying figures, each main body <NUM>, <NUM> is at least partially circular in shape. Even more preferably, each main body <NUM>, <NUM> has a gear wheel shape.

Preferably, moreover, the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> have the same diameter and the two connecting rods <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> have the same length.

Advantageously, these technical features allow the two connecting rod-crank mechanisms <NUM>, <NUM> to operate at the same frequency.

In accordance with a peculiar aspect of the present invention, the main body <NUM>, <NUM> of the first and/or second connecting rod-crank mechanism <NUM>, <NUM> defines a sliding path <NUM>, <NUM> for the respective crank pin <NUM>, <NUM>. In particular, the sliding path <NUM>, <NUM> is delimited by a first end stop <NUM>, <NUM> and a second end stop <NUM>, <NUM>. In addition, the sliding path <NUM>, <NUM> extends around the respective axis of rotation "X", "Y". Preferably, the sliding path <NUM>, <NUM> extends in an arc-of-a-circle about the respective axis of rotation "X", "Y".

At functional level, when the motor <NUM> operates according to the first drive direction, the crank pin <NUM>, <NUM> abuts against the first end stop <NUM>, <NUM> so that the two combs <NUM>, <NUM> mutually take on a first tilting configuration whereas when the motor <NUM> operates according to the second drive direction, the crank pin <NUM>, <NUM> abuts against the second end stop <NUM>, <NUM> so that the two combs <NUM>, <NUM> mutually take on a second tilting configuration, which is offset from the first tilting configuration.

Advantageously, this system allows the mutual tilting configuration to be switched between the two combs <NUM>, <NUM>. In fact, by means of this system, the tool <NUM> can selectively operate in the first drive direction of the motor <NUM> in which the combs <NUM>, <NUM> assume a mutual tilting configuration and in the second drive direction in which the combs <NUM>, <NUM> assume a further mutual tilting configuration, different from the previous one.

Such a result, as will be further clarified in the following of the present description, can be obtained by means of a pair of connecting rod-crank mechanisms <NUM>, <NUM> in which only one of them defines a respective sliding path <NUM> for the crank pin <NUM> or by means of a pair of connecting rod-crank mechanisms <NUM>, <NUM> wherein both of them define respective sliding paths <NUM>, <NUM> for the two crank pins <NUM>, <NUM>, wherein the sliding paths <NUM>, <NUM> have a different angular extension with respect to the axis of rotation "X", "Y" of the respective main body <NUM>, <NUM>.

Preferably, in the first tilting configuration the two combs <NUM>, <NUM> are moved by the respective connecting rod-crank mechanisms <NUM>, <NUM> so that they are mutually in phase. Preferably, in other words, in the first tilting configuration the two combs <NUM>, <NUM> move concordantly.

In accordance with an alternative embodiment, in the first tilting configuration the two combs <NUM>, <NUM> are driven by the respective connecting rod-crank mechanisms <NUM>, <NUM> so that they are mutually in counterphase. Preferably, in other words, in the first tilting configuration the two combs <NUM>, <NUM> move in opposite directions.

In the following of the present description, reference will be made to the embodiment in which the two combs <NUM>, <NUM> are moved by the respective connecting rod-crank mechanisms <NUM>, <NUM> so that they are mutually in phase. However, all of the above concepts will also be applicable to the embodiment in which the two combs <NUM>, <NUM> are moved by the respective connecting rod-crank mechanisms <NUM>, <NUM> in such a way that they are mutually in counterphase without departing from the inventive concept of the present invention.

In the second tilting configuration, the two combs <NUM>, <NUM> are instead moved by the respective connecting rod-crank mechanisms <NUM>, <NUM> so that they are mutually offset by a predetermined phase delay. Preferably, in the second tilting configuration, the two combs <NUM>, <NUM> are moved by the respective connecting rod-crank mechanisms <NUM>, <NUM> so that they are in counterphase.

With regard to the structure of the mechanical transmission <NUM>, four embodiments are described, which are illustrative and therefore not limiting, in accordance with the generality of the invention.

<FIG> show a first possible embodiment of the mechanical transmission <NUM>.

In such an embodiment, the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> are coplanar and placed side-by-side along a longitudinal axis "Z" of the tool <NUM>. In particular, the axes of rotation "X", "Y" of the two main bodies <NUM>, <NUM> are parallel.

The mechanical transmission <NUM> comprises a pinion <NUM> operatively connected to and active on both main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM>. In particular, the pinion <NUM> is operatively arranged substantially along the longitudinal axis "Z" of the tool <NUM> and is operatively arranged in a position interposed between the two main bodies <NUM>, <NUM>.

In this embodiment, only one of the connecting rod-crank mechanisms <NUM>, <NUM> defines the sliding path <NUM>, <NUM> for the respective crank pin <NUM>, <NUM>.

Preferably, the first connecting rod-crank mechanism <NUM> defines the respective sliding path <NUM>.

The sliding path <NUM> extends angularly for an angle comprised between <NUM>° and <NUM>° about the respective axis of rotation "X". Preferably, the sliding path <NUM> extends angularly for <NUM>° about the respective axis of rotation "X" so that in the second tilting configuration the two combs <NUM>, <NUM> are mutually moved in counterphase.

Structurally, the sliding path <NUM> is defined by a groove or slot <NUM> obtained on the respective main body <NUM>, to which the second end 102b, of the respective connecting rod <NUM> is slidably coupled.

Functionally, when the motor <NUM> reverses its drive direction, from the first drive direction to the second drive direction, the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> begin to rotate in the corresponding drive direction. However, in the first connecting rod-crank mechanism <NUM>, the connecting rod <NUM>, slidably constrained in the respective sliding path <NUM>, slides along the sliding path <NUM> from the first end-stop <NUM> to the second end-stop <NUM> in a manner not integral with the respective main body <NUM> so as to remain substantially stationary with respect to the axis of rotation "X" of the main body <NUM> and so as not to move the respective comb <NUM>, which accumulates a phase delay with respect to the comb <NUM> connected to the second connecting rod-crank mechanism <NUM>. When the connecting rod <NUM> finally abuts against the second end stop <NUM> the connecting rod <NUM> resumes movement integrally with the respective main body <NUM> about the aforementioned axis of rotation "X", putting the respective comb <NUM> back in motion. By reversing the drive direction of the motor <NUM> again, in particular from the second drive direction to the first drive direction, the connecting rod returns to abut against the first end stop <NUM> of the respective sliding path <NUM>, so that the two combs are again mutually moved in phase.

<FIG> show a second possible embodiment of the mechanical transmission <NUM>.

In such an embodiment, both connecting rod-crank mechanisms <NUM>, <NUM> define their own sliding path <NUM>, <NUM> for the respective crank pins <NUM>, <NUM>. In particular, the first connecting rod-crank mechanism <NUM> defines a first sliding path <NUM> for the respective crank pin <NUM> while the second connecting rod-crank mechanism <NUM> defines a second sliding path <NUM> for the respective crank pin <NUM>: the first and second sliding paths <NUM>, <NUM> extend angularly about the respective axes of rotation "X", "Y" having an angular extension difference comprised between <NUM>° and <NUM>°. Preferably, the two sliding paths <NUM>, <NUM> have a difference in angular extension of <NUM>° so that in the second tilting configuration, the two combs <NUM>, <NUM> are mutually moved in counterphase.

<FIG> shows the second tilting configuration. Specifically, in the second drive direction of the motor <NUM>, the main bodies <NUM>, <NUM> rotate clockwise, while in the first drive direction of the motor <NUM>, the main bodies <NUM>, <NUM> rotate anticlockwise.

As can be seen in <FIG>, the sliding path <NUM> of the first connecting rod-crank mechanism <NUM> extends at an angle of <NUM>° about the respective axis of rotation "X", while the sliding path <NUM> of the second connecting rod-crank mechanism <NUM> extends at an angle of <NUM>° about the respective axis of rotation "Y".

Structurally, each sliding path <NUM>, <NUM> is defined by a groove or slot <NUM>, <NUM> obtained on the respective main body <NUM>, <NUM>, to which the second end 102b, 202b of the respective connecting rod <NUM>, <NUM> is slidably coupled.

Functionally, when the motor <NUM> reverses its drive direction, from the first drive direction to the second drive direction, the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> begin to rotate in the corresponding drive direction. However, both connecting rods <NUM>, <NUM>, which are slidably constrained in the respective sliding path <NUM>, <NUM>, slide along the sliding path <NUM>, <NUM> from the first end-stop <NUM>, <NUM> to the second end-stop <NUM>, <NUM> in a manner not integral with the respective main body <NUM>, <NUM> so as to remain substantially stationary with respect to the axis of rotation "X" of the main body <NUM>, <NUM> and so as not to move the respective comb <NUM>, <NUM>. Since the sliding path <NUM> of the second connecting rod-crank mechanism <NUM> has a smaller angular extension than the sliding path <NUM> of the first connecting rod-crank mechanism, the connecting rod <NUM> of the second connecting rod-crank mechanism <NUM> comes into contact with the respective second end-stop <NUM> before the connecting rod <NUM> of the first connecting rod-crank mechanism <NUM>. This results in the connecting rod <NUM> of the second connecting rod-crank mechanism <NUM> starting to rotate integrally with the respective main body <NUM> (and thus moving the respective comb <NUM>) before the connecting rod <NUM> of the first connecting rod-crank mechanism. Therefore, as for the embodiment in <FIG>, the comb <NUM> will accumulate a phase delay with respect to the comb <NUM>.

By reversing the drive direction of the motor <NUM> again, in particular from the second drive direction to the first drive direction, the connecting rod returns to abut against the first end stop <NUM> of the respective sliding path <NUM>, so that the two combs are again mutually moved in phase.

<FIG> show a third possible embodiment of the mechanical transmission <NUM>.

The mechanical transmission <NUM> comprises a pinion <NUM> operatively connected to only one of the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> while the other main body <NUM>, <NUM> is connected in a cascaded system. As can be seen in <FIG>, the pinion <NUM> directly moves the main body <NUM> of the first connecting rod-crank mechanism <NUM> while the main body <NUM> of the second connecting rod-crank mechanism <NUM> is operatively connected to the main body <NUM> of the first connecting rod-crank mechanism <NUM> so as to be moved by it. In this embodiment, only one of the connecting rod-crank mechanisms <NUM>, <NUM> defines the sliding path <NUM>, <NUM> for the respective crank pin <NUM>, <NUM>, as in the embodiment of <FIG>.

At functional level, this embodiment operates essentially like the embodiment of <FIG>.

<FIG> show a fourth possible embodiment of the mechanical transmission <NUM>.

Structurally, the first connecting rod-crank mechanism <NUM> comprises an intermediate body <NUM> hinged to the respective main body <NUM> so as to be rotatable about the respective axis of rotation "X"; the second end 102b of the respective connecting rod <NUM> is integrally hinged to the intermediate body <NUM> in a radially peripheral portion thereof.

The main body <NUM> and the respective intermediate body <NUM> have mutual blocking elements <NUM>, <NUM>, such as protuberances and/or recesses, defining the first end-stop 104a and the second end-stop 104b so that the intermediate body <NUM> is rotatable relative to the respective main body <NUM> between two positions defining respectively the two tilting configurations <NUM>, <NUM>.

In other words, the sliding path <NUM> is essentially defined by the mutual movement of the intermediate body <NUM> with respect to the main body <NUM> on which it is constrained and pivots between the aforementioned two positions, defined in turn by the blocking elements <NUM>, <NUM>.

Preferably, the intermediate body <NUM> has a recess or slot <NUM> while the main body <NUM> has a protuberance <NUM> operatively inserted into the recess or slot <NUM> of the intermediate body <NUM>.

The protuberance <NUM> of the main body <NUM> defines the aforementioned first end stop <NUM> and second end stop <NUM>.

On a functional level, this embodiment operates essentially similarly to the embodiment in <FIG>.

According to a embodiment of the mechanical transmission <NUM> not shown, the main bodies <NUM>, <NUM> of the two connecting rod-crank mechanisms <NUM>, <NUM> are integral or permanently connected so as to be integral and are rotatable about the same axis of rotation "X", "Y"; the main bodies <NUM>, <NUM> define a double discoidal body to which the connecting rods <NUM>, <NUM> are rotatably connected on opposite sides of the double discoidal body itself.

In this embodiment, the sliding paths can be realised in accordance with the embodiments described above. In other words, only one of the connecting rod-crank mechanisms <NUM>, <NUM> can be provided to describe the respective sliding path <NUM>, <NUM> in accordance with the above. Alternatively, it can be provided that both connecting rod-crank mechanisms <NUM>, <NUM> describe the respective sliding paths <NUM>, <NUM> in accordance with the above.

Claim 1:
A portable agricultural tool (<NUM>), such as a harvester, comprising:
- a machine body comprising a motor (<NUM>);
- a first comb (<NUM>) and a second comb (<NUM>) connected to the motor (<NUM>) by means of a mechanical transmission (<NUM>), which comprises a first connecting rod-crank mechanism (<NUM>) configured to move the first comb (<NUM>) and a second connecting rod-crank mechanism (<NUM>) configured to move the second comb (<NUM>); each connecting rod-crank mechanism (<NUM>, <NUM>) comprising a main body (<NUM>, <NUM>) fitted to rotate about a respective axis of rotation (X, Y) and a connecting rod (<NUM>, <NUM>) having a first end (102a, 202a) hinged to the respective comb (<NUM>, <NUM>) and a second end (102b, 202b) hinged to a respective main body (<NUM>, <NUM>) in a respective crank pin (<NUM>, <NUM>); in use, said main bodies (<NUM>, <NUM>) being mutually concordant in rotation;
characterised in that the motor (<NUM>) is configured to selectively operate in a first drive direction and a second drive direction opposite the first drive direction, and that
the main body (<NUM>, <NUM>) of the first and/or second connecting rod-crank mechanism (<NUM>, <NUM>) defines a sliding path (<NUM>, <NUM>) for the respective crank pin (<NUM>, <NUM>), the sliding path (<NUM>, <NUM>) being delimited by a first end stop (104a, 204a) and a second end stop (104b, 204b) and extending about the respective axis of rotation (X, Y) so that:
when the motor (<NUM>) operates according to the first drive direction, the crank pin (<NUM>, <NUM>) abuts against the first end stop (104a, 204a) so that the two combs (<NUM>, <NUM>) mutually take on a first tilting configuration; and
when the motor (<NUM>) operates according to the second drive direction, the crank pin (<NUM>, <NUM>) abuts against the second end stop (104b, 204b) so that the two combs (<NUM>, <NUM>) mutually take on a second tilting configuration, which is offset from the first tilting configuration.