Description:FORM 2

THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENT RULES, 2003

COMPLETE SPECIFICATION
(See Section 10 and Rule 13)

TITLE OF INVENTION:
A DIFFERENTIAL IMPULSE CONVEYOR SYSTEM WITH THREE PULLEY MECHANISM AND A METHOD THEREOF

APPLICANT:
SIDDHI VINAYAK AGRI PROCESSING PRIVATE LIMITED
An Indian Entity
having address as:
E/1/18, HERMES HERITAGE PHASE-2, SHASTRI NAGAR, YERWADA PUNE 411006 Maharashtra India

The following specification describes the invention and the manner in which it is to be performed.
CROSS-REFERENCE TO RELATED APPLICATIONS AND PRIORITY
The present application does not claim priority from any other patent application.
TECHNICAL FIELD
The present subject matter described herein, in general, relates to the field of conveyor management system. More specifically, the present subject matter discloses a system and a method for conveying articles via a conveyor management system. More particularly, the present subject matter relates to a system and a method for conveying articles comprising a drive mechanism and a tensioning mechanism.
BACKGROUND
The subject matter discussed in the background section should not be assumed to be prior art merely because of its mention in the background section. Similarly, a problem mentioned in the background section or associated with the subject matter of the background section should not be assumed to have been previously recognized in the prior art. The subject matter in the background section merely represents different approaches, which in and of themselves may also correspond to implementations of the claimed technology.
In any industry, article or product conveying is an integral part of the product management system. Conventionally, belt conveyors are used in such product management systems. Further, for applications where distribution of product is required, conveyor systems such as high frequency electromagnetic vibratory conveyors, pneumatic conveyors, chain conveyors, etc. are developed as per the requirement of the industrial process. However, these conveyor systems mutilate the product quality.
Several varieties of conveyor systems have been devised that employ an elongate tray or pan having a planar surface for transporting articles thereupon. Traditionally, these conveyor trays have sides projecting upward from the planar floor of the tray, such that the tray, generally, has a U-shaped cross-sectional configuration. Conveyor systems with such types of trays are preferred for various applications since the articles conveyed along the conveyor tray need to be engaged with the conveyor tray during the conveying operation, and hence, the conveyor tray may be easily cleaned.
As known in the art, one such type of conveyor system which utilizes an aforementioned conveyor tray is a vibratory or shaker conveyor system. These conveyor systems employ a drive mechanism that essentially vibrates the conveyor tray, so that the articles move along a slightly inclined or horizontal to the conveyor tray floor due to the forward direction imparted to the articles while raised off the floor. These conveyor systems may also utilize one or more crank arms that cause a change in the rotational speed of a driven pulley.
Thus, differential impulse conveyor systems have a significant advantage over the vibratory/shaker conveyor systems for many applications. Differential impulse conveyors slide articles along a conveyor tray, but do not require vertical movement of the articles with respect to the conveyor tray. The articles conveyed with a differential impulse conveyor system are generally subject to less damage than articles transported by a vibratory/shaker conveyor system. Further, the drive mechanism of a differential impulse conveyor system may operate in a quieter manner and may be less susceptible to maintenance problems.
Further, as conventionally known in the art, the differential impulse conveyor systems may utilize an elongated conveyor tray to move articles along the conveyor tray. Such differential impulse conveyor system may include a drive unit or drive assembly that moves the conveyor tray forward at a first speed and then backward at a greater speed such that the articles slide relative to the conveyor tray and thus move forward along the conveyor tray.
However, all the differential impulse conveyor systems known in the art show a typical problem of undesirable vibration and mechanical knocking in their drive mechanism and the conveyor tray. Due to this, there is deterioration of the drive mechanism and hence, the articles also get damaged while being conveyed by the conveyor tray of such differential impulse conveyor systems.
Thus, to address and discard the aforementioned and other related flaws, there is a long-felt need for a well-designed, technically advanced, and well-built conveyor system for conveying articles with a drive mechanism with an improved drive efficiency and reduced and mechanical knocking for powering the conveyor system for gentle conveying of the articles keeping the product quality intact.
SUMMARY
This summary is provided to introduce concepts related to a system and a method for conveying articles, and the concepts are further described below in the detailed description. This summary is not intended to identify essential features of the claimed subject matter nor is it intended for use in determining or limiting the scope of the claimed subject matter.
In an embodiment, a system for conveying articles may comprise a drive motor, a conveyor tray, a flywheel, a drive mechanism, a counter mass assembly, and a tensioning mechanism. The drive motor may be mounted on a system frame for providing a driving motion to a timing pulley which is mounted on an output shaft of the drive motor. The conveyor tray may be mounted on one end of a plurality of oscillating links, and the other end of the plurality of oscillating links may be pivoted on the system frame. Further, the flywheel may be configured to receive the driving motion from the timing pulley via a connecting belt. The drive mechanism may be configured for converting the driving motion of the flywheel into a motion of the conveyor tray for conveying articles. The counter mass assembly may be configured to move in a direction opposite to the motion of the conveyor tray. The tensioning mechanism may be configured to maintain a pre-defined tension in a driving belt of the drive mechanism.
In another embodiment, a method for conveying articles comprises the steps of: providing a driving motion to a timing pulley; receiving the driving motion from the timing pulley to a flywheel; transmitting the driving motion from the flywheel to a driving pulley; receiving the driving motion from the driving pulley a driven pulley; providing a belt compensation of the driving belt; converting the driving motion of the driven pulley into an oscillatory motion of a plurality of oscillating links; transmitting the oscillatory motion as a two dimensional motion of a conveyor tray; oscillating a counter mass assembly in a direction opposite to the motion of the conveyor tray; and conveying articles in the direction of the motion of the conveyor tray.
BRIEF DESCRIPTION OF DRAWINGS
The detailed description is described with reference to the accompanying figures. The same reference numerals are used throughout the drawings to refer like features and components.
Figure 1(a) illustrates a schematic representation of a system 100 in an isometric view for conveying articles, in accordance with an embodiment of the present disclosure.
Figure 1(b) illustrates a schematic representation of the system 100 in a front view for conveying articles, in accordance with an embodiment of the present disclosure.
Figure 2 illustrates a schematic representation 200 of a drive mechanism 25 of the system 100, in an isometric view, for conveying articles, in accordance with an embodiment of the present disclosure.
Figure 3(a) illustrates a schematic representation of an assembly 300 of the system 100, in an isometric view, for conveying articles with a conveyor tray 1, in accordance with an embodiment of the present disclosure.
Figure 3(b) illustrates a schematic representation of a front view of the assembly 300 of the system 100 for conveying articles with a conveyor tray 1, in accordance with an embodiment of the present disclosure.
Figure 4 illustrates a schematic representation of a front view of a driven pulley 8 or an idler pulley 9 with eccentricity ‘e’, in accordance with an embodiment of the present disclosure.
Figure 5 illustrates an exemplary mounting embodiment 500 of the system 100 for conveying articles with a conveyor tray 1, in accordance with an embodiment of the present disclosure.
Figure 6 illustrates a flow chart representing a method 600 for conveying articles, in accordance with an embodiment of the present disclosure.
DETAILED DESCRIPTION
Reference throughout the specification to “various embodiments,” “some embodiments,” “one embodiment,” or “an embodiment” means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment. Thus, appearances of the phrases “in various embodiments,” “in some embodiments,” “in one embodiment,” or “in an embodiment” in places throughout the specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.
Further, the term “conveyor tray” may interchangeably be used for any conveyor surface like a “tray” or a “sliding surface”, or the like. The term “pulley” may interchangeably be used for “wheel”, “free mounting wheel”, or the like.
In an embodiment of the present disclosure, a system for conveying articles is disclosed. The system may comprise a drive motor, a conveyor tray, a flywheel, a drive mechanism, a counter mass assembly, and a tensioning mechanism. The drive motor may be mounted on a system frame for providing a driving motion to a timing pulley which is mounted on an output shaft of the drive motor. The conveyor tray may be mounted on one end of a plurality of oscillating links, and the other end of the plurality of oscillating links may be pivoted on the system frame. Further, the flywheel may be configured to receive the driving motion from the timing pulley via a connecting belt. The drive mechanism may be configured for converting the driving motion of the flywheel into a motion of the conveyor tray for conveying articles. The drive mechanism may further be a differential impulse drive mechanism for the system. The said motion of the conveyor tray may be a two-dimensional motion in the X-Y cartesian coordinate plane. The counter mass assembly may be configured to move in a direction opposite to the motion of the conveyor tray. The tensioning mechanism may be configured to maintain a pre-defined tension in a driving belt of the drive mechanism. Further, the drive mechanism may comprise an arrangement of one or more pulleys such that the driving motion of the timing pulley may be converted into an oscillatory motion of the plurality of oscillating links, and eventually into the two-dimensional motion of the conveyor tray for conveying articles via the plurality of oscillating links. In an embodiment, the connecting belt may be a high-tension carbon fiber belt with a high fatigue loading capacity.
In an exemplary embodiment of the present disclosure, the drive mechanism may comprise a driving pulley, a driven pulley, and an idler pulley. The driving pulley, the driven pulley, and the idler pulley may be connected via a driving belt. The driving pulley may be concentrically mounted on a transmission shaft of the flywheel and may further be configured to receive the driving motion from the flywheel via the transmission shaft. The driven pulley may be mounted on a driving crankshaft and may be configured to receive the driving motion from the driving pulley via the driving belt. The idler pulley may further be configured to provide a belt compensation of the driving belt, by being a free rotating pulley. The drive mechanism may be responsible for oscillating the counter mass assembly in a direction opposite to the motion of the conveyor tray via the plurality of oscillating links. The drive mechanism may further be configured for conveying articles in the direction of the motion of the conveyor tray via the conveyor tray.
In another embodiment, the drive mechanism may comprise a driver connecting link and a balancer connecting link. The driver and the balancer connecting links may be configured to convert the driving motion of the driven pulley into an oscillatory motion of the plurality of oscillating links. The plurality of oscillating links. may, then transmit the said oscillatory motion into two-dimensional motion to the conveyor tray such that the conveyor tray conveys articles in the direction of the motion of the conveyor tray. Further, the said oscillatory motion of the plurality of oscillating links may enable the counter mass assembly to move in a direction opposite to the motion of the conveyor tray.
In another exemplary embodiment of the present disclosure, the system may comprise a variable frequency drive. The variable frequency drive may be coupled to the drive motor and configured to maintain a constant angular velocity of the drive motor and the timing pulley, and thus, a constant tangential velocity of the connecting belt and the driving belt.
Further, the transmission shaft of the flywheel may be arranged in the system such that the axis of rotation of the flywheel becomes parallel to the axis of rotation of the timing pulley.
The counter mass assembly may be arranged on the bottom side of the conveyor tray. The counter mass assembly may further be configured to counter the linear and angular momentum generated by the two-dimensional motion of the conveyor tray, weight corresponding to a total weight of the articles conveyed by the conveyor tray, be supported by the plurality of oscillating links, and move in a direction opposite to the two-dimensional motion of the conveyor tray at an angular phase difference of 180°.
In an embodiment, the plurality of oscillating links may comprise two pairs of oscillating links. Further, a first pair of oscillating links from the two pairs of oscillating links may be configured to be of a different height than a second pair of oscillating links from the two pairs of oscillating links.
In another exemplary embodiment, the tensioning mechanism may be configured to adjust the tension of the driving belt as well as the connecting belt. The tensioning mechanism may comprise a tensioner wheel configured to rotate freely and engage with the driving belt and/or the connecting belt. This engagement with the driving and/or connecting belt equilibrates the tension and reduces the belt flapping and fatigue loading in the driving and/or connecting belt.
In another embodiment of the present disclosure, the driving pulley may be configured to be concentric with the flywheel. The driven pulley and the idler pulley may be configured to be eccentric pulleys such that the driving pulley, the driven pulley, and the idler pulley form an isosceles triangle arrangement. The isosceles triangle arrangement causes the distance between centres of the driving pulley and the driven pulley being equal to the distance between the centres of the driving pulley and the idler pulley. Further, the driven pulley and the idler pulley may be positioned at an angular phase difference such that the driving belt lost by the driven pulley is gained by the idler pulley to maintain a constant length of the driving belt in the drive mechanism. Here, the angular phase difference being the difference in the angle of the first contact point of the driving belt on the driven pulley and the idler pulley. The isosceles triangle arrangement may enable the placement of the driving belt at a maximum radius of the driven pulley when the driving belt is at a minimum radius of the idler pulley, and vice versa, to maintain a constant length of the driving belt in the drive mechanism.
Further, the driving crankshaft may comprise a first crank pin and a second crank pin. The first and the second crank pins may be placed at a phase difference of 180° from each other and configured to convert the driving motion of the driven pulley into an oscillatory motion of the plurality of oscillating links. The first crank pin may be engaged with a driver connecting link which may be configured to oscillate the first pair of oscillating links. The first pair of oscillating links may be configured to move the conveyor tray in the two-dimensional motion. Furthermore, the second crank pin may be engaged with a balancer connecting link which may be configured to oscillate the second pair of oscillating links. The second pair of oscillating links may be configured to move the counter mass assembly in a direction opposite to the motion of the conveyor tray. The first and the second crank pins and the driver and the balancer connecting links may be connected by roller bearings to reduce the friction on the contact surface. The driver and the balancer connecting links may further comprise connecting rods for passing the motion as the oscillatory motion to the first and the second pair of oscillating links. Further, the height of the connecting rods connected to the first and the second pair of oscillating links determine the vertical and horizontal acceleration of the conveyor tray and the counter mass assembly.
In an embodiment, the phase difference between the axis of the driving crankshaft and the axis of the driven pulley may be configured to govern the acceleration of the two-dimensional motion of the conveyor tray.
In another embodiment, the eccentricities of the driven pulley and the idler pulley and the eccentricities of the first and the second crank pins may be designed in such a way that the articles stay in contact with the conveyor tray during the two-dimensional motion of the conveyor tray.
In an embodiment of the present disclosure, a method for conveying articles is disclosed. The method may comprise the steps of: providing, by a drive motor, a driving motion to a timing pulley; receiving, via a connecting belt, the driving motion from the timing pulley to a flywheel; transmitting, via the transmission shaft, the driving motion from the flywheel to a driving pulley; receiving, via a driving belt, the driving motion from the driving pulley a driven pulley; providing, by an idler pulley, a belt compensation of the driving belt; converting, via a driver connecting link and a balancer connecting link, the driving motion of the driven pulley into an oscillatory motion of a plurality of oscillating links; transmitting, via the plurality of oscillating links, the oscillatory motion as a two dimensional motion of a conveyor tray; oscillating, via the plurality of oscillating links, a counter mass assembly in a direction opposite to the two dimensional motion of the conveyor tray; and conveying articles, via the conveyor tray, in the direction of the two dimensional motion of the conveyor tray. During a forward stroke, the conveyor tray moves in the positive Y axis and positive X axis. The conveyor tray follows a sinusoidal acceleration profile, while the conveyor tray is moving in the positive Y axis, the acceleration of the conveyor tray is also in the positive Y direction, therefore the normal force between the articles on the conveyor tray and tray surface increases. Because of this increased frictional force, the conveyor tray carries the articles with it. During a backward stroke, the conveyor tray moves in the negative Y axis, the acceleration of the conveyor tray is also in the negative Y direction, therefore the normal force between the articles on the conveyor tray and the tray surface decreases. Because of the low friction force on the articles and the tray surface, the article slides on the tray surface, during the backward stroke. With each cycle, the article moves in the direction of conveyor tray movement, equal to the amplitude of the conveyor tray.
In another embodiment, the method for conveying articles may further comprise the steps of: maintaining, by a tensioning mechanism, a constant tension in the driving belt; and maintaining a constant tangential velocity of the driving belt as a result of the constant angular velocity of the driving pulley. The tensioning mechanism may comprise a tensioner wheel that rotates freely and engages with the driving belt to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt.
In another embodiment, converting the driving motion of the driven pulley into an oscillatory motion of a plurality of oscillating links further comprises a conversion of the constant tangential velocity of the driving belt into a variable angular velocity of the driven pulley in proportion to the eccentricity of the driven pulley. Further, the conversion of the constant tangential velocity of the driving belt into a variable angular velocity of the driven pulley may also be in proportion to a mean radius of the driven pulley, the constant tangential velocity of the driving belt, and an angular position of the driving belt.
In another embodiment, the method for conveying articles may further comprises converting, by a drive mechanism formed by the driving pulley, the driven pulley and the idler pulley, the driving motion of the timing pulley into the two-dimensional motion of the conveyor tray; and tensioning, by a tensioning mechanism, the driving belt and/or the connecting belt.
In an embodiment, the drive motor may be placed on a heavy base frame. Further, the selection of the flywheel may be such that it reduces the angular velocity and thus, increasing the torque as required by the system for conveying articles. In one exemplary embodiment, transmission of motion from the drive motor to the driving pulley via the flywheel may efficiently or smoothly transitioning the motion between the driving motor and the driving pulley, which is resulting in less fatigue load on the driving belt and (or) connecting belt, thus increasing the operating life of the belts in the conveyor system.
The drive motor, in connection to the variable frequency drive, allows a constant angular velocity of the driving pulley at a given frequency; hence, the tangential velocity of the driving belt becomes constant. This constant velocity driving belt drives the driven pulley. Due to the eccentricity of the driven pulley, the driven pulley rotates at a variable angular velocity that depends on the tangential velocity of the driving belt, mean radius (r) of the driven pulley, eccentricity (e) of the driven pulley, and angular position (?) of the driving belt. The angular position of the driving belt may be defined as the angle of the first contact point with the driven pulley. The angular velocity of the driving pulley follows a sinusoidal curve as a function of the angular position of the driving belt. The driving belt in connection to the idler pulley acts as a belt compensation pulley. The variable angular velocity of the driven pulley develops an angular acceleration in the driven pulley.
Now, the system and the method for conveying articles may further be described according to the present disclosure with respect to the disclosed drawings:
Referring to figures 1(a) and 1(b), a schematic representation of an isometric view and a schematic representation of a front view of a system 100 for conveying articles is shown in accordance with an embodiment of the present disclosure. The system 100 for conveying articles comprises a drive motor 14, a conveyor tray 1 (as illustrated in Figure 3(a)), a flywheel 13, a drive mechanism 25 (as illustrated in Figure 2), a counter mass assembly 5, and a tensioning mechanism 19 (not illustrated). The drive motor 14 is mounted on a system frame 6 and further configured to provide a driving motion to a timing pulley 20. The timing pulley 20 is mounted on an output shaft of the drive motor 14. The conveyor tray 1 is mounted on one end of a plurality of oscillating links 2, wherein the other end of the plurality of oscillating links 2 is pivoted on the system frame 6. The flywheel 13 receives the driving motion from the timing pulley 20 via a connecting belt 15. The drive mechanism 25 is configured to convert the driving motion of the flywheel 13 into a motion of the conveyor tray 1 for conveying articles. The said motion of the conveyor tray (1) may comprise a two-dimensional motion wherein the two-dimensional motion is operated in X-Y cartesian coordinate plane. The counter mass assembly 5 is further configured to move in a direction opposite to the two-dimensional motion of the conveyor tray 1. The counter mass assembly 5, thus, balances the system 100 by harmonizing the movement of the conveyor tray 1 in the X-Y cartesian coordinate system. The system 100 also comprises a plurality of levelling pads 24 for a levelled placement of the system 100 on any planar surface. The system 100 further comprises a plurality of resistant sliding bushes 11 corresponding to the other end of the plurality of oscillating links 2 which is pivoted on the system frame 6. The resistant sliding bushes 11 aid in the oscillatory movement of the plurality of oscillating links 2.The connecting belt 15 may be a high-tension carbon fiber belt with a high fatigue loading capacity.
In a non-limiting embodiment of the present disclosure, the drive mechanism 25 may be further configured to be a differential impulse drive mechanism or the like for the system 100.
Now, referring to figure 2, a schematic representation 200 of a drive mechanism 25 of the system 100, in an isometric view, for conveying articles, is illustrated. The drive mechanism 25 comprises a driving pulley 7, a driven pulley 8, and an idler pulley 9, The driving pulley 7, the driven pulley 8, and the idler pulley 9 are connected via a driving belt 16. The driving pulley 7 is concentrically mounted on a transmission shaft 17 of the flywheel 13 and receives the driving motion from the flywheel 13 via the transmission shaft 17. The driven pulley 8, mounted on a driving crankshaft 12, receives the driving motion from the driving pulley 7 via the driving belt 16. The idler pulley 9 provides a belt compensation of the driving belt 16. The counter mass assembly 5 is configured to oscillate in a direction opposite to the two-dimensional motion of the conveyor tray 1 using the plurality of oscillating links 2. Further, as a result of the two-dimensional motion of the conveyor tray 1, the articles are being conveyed in the direction of the two-dimensional motion of the conveyor tray 1.
Further, the drive mechanism 25 comprises a driver connecting link 3 and a balancer connecting link 4. The driver connecting link 3 and the balancer connecting link 4 both comprise a connecting rod 21 at their ends configured to engage and attach with the plurality of oscillating links 2. This arrangement of driver connecting link 3 and the balancer connecting link 4, attached at a predefined height, with the plurality of oscillating links 2 converts the driving motion of the driven pulley 8 into an oscillatory motion of the plurality of oscillating links 2. The plurality of oscillating links further transmits the said oscillatory motion into the two-dimensional motion to the conveyor tray 1 such that the conveyor tray 1 conveys the articles in the direction of the said two-dimensional motion. The said oscillatory motion of the plurality of oscillating links 2 also enables the counter mass assembly 5 to move in a direction opposite to the two-dimensional motion of the conveyor tray 1, thereby, balancing the system 100.
The system 100 also comprises a variable frequency drive coupled to the drive motor 14 for maintaining a constant angular velocity of the drive motor 14. Further, the transmission shaft 17 of the flywheel 13 is arranged in the system 100 such that the axis of rotation of the flywheel 13 is parallel to the axis of rotation of the timing pulley 20.
The counter mass assembly 5, arranged on a bottom side of the conveyor tray 1, is configured to counter the linear and angular momentum generated by the two dimensional motion of the conveyor tray 1, weight corresponding to a total weight of the articles conveyed by the conveyor tray 1, be supported by the plurality of oscillating links 2, and move in a direction opposite to the two dimensional motion of the conveyor tray 1 at an angular phase difference of 180°.
The plurality of oscillating links 2 further comprises two pairs of oscillating links, wherein each pair of oscillating links from the two pairs of oscillating links may comprise one or more oscillating links. In one exemplary embodiment, the one or more oscillating links may comprise four oscillating links. A first pair of oscillating links from the two pairs of oscillating links is configured to be of a different height than a second pair of oscillating links from the two pairs of oscillating links.
Further, the driving crankshaft 12 comprises a first crank pin and a second crank pin. The first and the second crank pins are placed at a phase difference of 180° from each other i.e., opposite to each other. The first and the second crank pins are configured to convert the driving motion of the driven pulley 8 into an oscillatory motion of the plurality of oscillating links 2. The first crank pin engages with a driver connecting link 3 for oscillating the first pair of oscillating links, which moves the conveyor tray 1 in the two-dimensional motion. The second crank pin engages with a balancer connecting link 4 for oscillating the second pair of oscillating links which moves the counter mass assembly 5 in the opposite direction of the two-dimensional motion of the conveyor tray 1.
The tensioning mechanism 19, configured to adjust the tension of the driving belt 16 and/or the connecting belt 15, comprises a tensioner wheel 10. The tensioner wheel 10 is configured to rotate freely and engage with the driving belt 16 and/or the connecting belt 15, to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt 16 and/or the connecting belt 15.
In a non-limiting embodiment of the present disclosure, the driving pulley 7 is configured to be concentric with the flywheel 13. The driven pulley 8 and the idler pulley 9 are configured to be eccentric pulleys such that the driving pulley 7, the driven pulley 8, and the idler pulley 9 forms an isosceles triangle arrangement. Due to such isosceles triangle arrangement, the distance between centres of the driving pulley 7 and the driven pulley 8 is equal to the distance between the centres of the driving pulley 7 and the idler pulley 9. Further, the driven pulley 8 and the idler pulley 9 are positioned at an angular phase difference such that the driving belt 16 lost by the driven pulley 8 is gained by the idler pulley 9 to maintain a constant length of the driving belt 16 in the drive mechanism 25. The angular phase difference is the difference in the angle of the first contact point of the driving belt 16 on the driven pulley 8 and the idler pulley 9. The isosceles triangle arrangement also enables the placement of the driving belt 16 at a maximum radius of the driven pulley 8 when the driving belt 16 is at a minimum radius of the idler pulley 9, and vice versa, thus, maintaining a constant length of the driving belt 16 in the drive mechanism 25.
Further, the eccentricities of the driven pulley 8 and the idler pulley 9 and the eccentricities of the first and the second crank pin are designed such that the articles stay in contact with the conveyor tray 1 during the two-dimensional motion of the conveyor tray 1. Additionally, the phase difference between the axis of the driving crankshaft 12 and the axis of the driven pulley 8 governs the acceleration of the two-dimensional motion of the conveyor tray 1.
Now, referring to figures 3(a) and 3(b), a schematic representation of an assembly 300, in an isometric view, of the system 100 for conveying articles with a conveyor tray 1 and a schematic representation of a front view of the assembly 300 of the system 100 for conveying articles with a conveyor tray 1 is illustrated respectively. As seen in figure 3(b), the conveyor tray 1 is configured to move in the two-dimensional motion in the X-Y cartesian coordinate planes, represented by X and Y. The assembly 300 is configured for placement on a planar and/or levelled surface like ground or a concrete layered surface or the like.
Referring to figure 4, a schematic representation of a front view of the driven pulley 8 or the idler pulley 9 with eccentricity ‘e’ is shown. The eccentric pulleys, i.e., the driven pulley 8 and/or the idler pulley 9, have a mean radius ‘r’ and a variable radius of the driving belt 16 contact point ‘r'’. The eccentricity ‘e’ of the eccentric pulleys is defined as the distance between the pulley centre ‘O’ and the pivot centre ‘O'’ the eccentric pulleys. The angular position of the driving belt 16 with respect to the line of eccentricity ‘e’ is defined as ‘?’ (theta). The values of the mean radius ‘r’, the variable radius ‘r'’, the eccentricity ‘e’, the pivot centre ‘O'’, and the angular position ‘?’ may be varied as per the required angular as well as linear velocity of the conveyor tray 1.
Now, referring to figure 5, an exemplary mounting embodiment 500 of the system 100 for conveying articles with a conveyor tray 1 is illustrated in accordance with an embodiment of the present disclosure. The exemplary mounting embodiment 500 of the system 100 shows a hanging mounting arrangement of the system 100 from a structure 26. The structure 26 may be a rigid metallic structure made of a metal like iron. steel, etc. or a concrete structure made of cement or reinforced concrete. The system 100 may be hanged using an arrangement of a cable 27, wherein the cable 27 may be a metallic cable. The structure 26 may be provided with a support base 28, a cable mounting support 29, and a conveyor tray C-bracket 30. The support base 28 may be configured to support the system 100 by placement of the system 100 on the support base 28 via the levelling pads 24 (not shown) of the system 100. The cable mounting support 29 may provide a plurality of pivot or attachment points for the arrangement of the cable 27 for hanging the system 100 on the support base 28. The conveyor tray C-bracket 30 may further be provided for supporting the conveyor tray 1. The system 100 may be configured to work in a similar aforementioned manner for conveying the articles via the conveyor tray 1. Such mounting embodiment 500 of the system 100 as a hanging mounting provision provides the applicator flexibility in industrial plants where the ground space is not sufficiently available, and the material needs to be conveyed overheads.
Referring to figure 6, a flow chart representing a method 600 for conveying articles is illustrated in accordance with an embodiment of the present disclosure. The method 600 comprises the steps of : providing 610 a driving motion to a timing pulley 20; receiving 620 the driving motion to a flywheel 13; transmitting 630 the driving motion to a driving pulley 7; receiving 640 the driving motion to a driven pulley 8; providing 650 a belt compensation of the driving belt 16; converting 660 the driving motion into an oscillatory motion; transmitting 670 the oscillatory motion as a two dimensional motion of a conveyor tray 1; oscillating 680 a counter mass assembly 5 in a direction opposite to the two dimensional motion of the conveyor tray 1; and conveying 690 articles in the direction of the two dimensional motion of the conveyor tray 1.
The method 600 starts at step 610 where the drive motor 14 provides a driving motion to a timing pulley 20. The timing pulley 20 is mounted on an output shaft of the drive motor 14.
At step 620, the driving motion from the timing pulley 20 is received at a flywheel 13 via a connecting belt 15. The flywheel 13 is mounted on a transmission shaft 17.
At step 630, the driving motion received at the flywheel 13 from the timing pulley 20 is transmitted to a driving pulley 7 via the transmission shaft 17 of the flywheel 13. The driving pulley 7 is concentrically mounted on the transmission shaft 17 of the flywheel 13.
At step 640, the driving motion from the driving pulley 7 is received at a driven pulley 8 via a driving belt 16 in connection with the driving pulley 7.
At step 650, the idler pulley 9 provides a belt compensation of the driving belt 16.
At step 660, the driving motion received at the driven pulley 8 from the driving pulley 7 is converted into an oscillatory motion of a plurality of oscillating links 2. This conversion into the oscillatory motion of the plurality of oscillating links 2 is performed via a driver connecting link 3 and a balancer connecting link 4.
At step 670, the oscillatory motion of the plurality of oscillating links 2 is transmitted as a two-dimensional motion of a conveyor tray 1, via the plurality of oscillating links 2.
At step 680, a counter mass assembly 5 is configured to move in a direction opposite to the two-dimensional motion of the conveyor tray 1, via the plurality of oscillating links 2.
At step 690, the articles are finally conveyed in the direction of the two-dimensional motion of the conveyor tray 1, via the conveyor tray 1.
Further, the method 600 comprises maintaining a constant tension in the driving belt 16 and maintaining a constant tangential velocity of the driving belt 16. The constant tension in the driving belt 16 is maintained by a tensioning mechanism 19. The tensioning mechanism 19 comprises a tensioner wheel 10. The tensioner wheel 10 is configured to rotate freely and engage with the driving belt 16 to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt 16. The constant tangential velocity of the driving belt 16 is maintained corresponding to the constant angular velocity of the driving pulley 7.
The step 660 of converting the driving motion of the driven pulley 8 into the oscillatory motion of the plurality of oscillating links 2, further, comprises a conversion of the constant tangential velocity of the driving belt 16 into a variable angular velocity of the driven pulley 8 in proportion to the eccentricity of the driven pulley 8. Furthermore, the step for conversion of the constant tangential velocity of the driving belt 16 into a variable angular velocity of the driven pulley 8 is configured to be in proportion to a mean radius of the driven pulley 8, the constant tangential velocity of the driving belt 16 and an angular position of the driving belt 16.
In a non-limiting embodiment, the method 600 for conveying articles further comprises the steps of: converting the driving motion of the timing pulley 20 into the two dimensional motion of the conveyor tray 1 and tensioning the driving belt 16. The conversion of the driving motion of the timing pulley 20 into the two dimensional motion of the conveyor tray 1 is performed by a drive mechanism 25 formed by the driving pulley 7, the driven pulley 8, and the idler pulley 9. The tensioning of the driving belt 16 is performed by a tensioning mechanism 19. The tensioning mechanism 19 further comprises a tensioner wheel 10. The tensioner wheel 10 is configured to rotate freely and engage with the driving belt 16, thereby equilibrating the tension and reducing the belt flapping and fatigue loading in the driving belt 16.
Below are the advantages provided by the system 100 and method 600 for conveying articles disclosed in the present disclosure:
— Improved drive mechanism.
— Efficient system for conveying articles due to improved differential impulse drive mechanism.
— Provides applicator flexibility in industrial plants.
— Less maintenance requirement.
— Reduced fatigue of the system belt drive.
— Increase efficacy in operation at low frequencies.
Various modifications to the aforementioned embodiment or embodiments will be readily apparent to those skilled in the art and the generic principles herein may be applied to other embodiments. However, one of ordinary skill in the art will readily recognize that the present disclosure is not intended to be limited to the embodiments illustrated but is to be accorded the widest scope consistent with the principles and features described herein.
The foregoing description shall be interpreted as illustrative and not in any limiting sense. A person of ordinary skill in the art would understand that certain modifications could come within the scope of this disclosure.
The embodiments, examples, and alternatives of the preceding paragraphs or the description and drawings, including any of their various aspects or respective individual feature(s), may be taken independently or in any combination. Features described in connection with one embodiment are applicable to all embodiments unless such features are incompatible.
DESCRIPTION OF SYMBOLS
1 : Conveyor Tray
2 : Oscillating Links
3 : Driver Connecting Link
4 : Balancer Connecting Link
5 : Counter Mass Assembly
6 : System Frame
7 : Driving Pulley
8 : Driven Pulley
9 : Idler Pulley
10 : Tensioner Wheel
11 : Resistant Sliding Bushes
12 : Crank Shaft
13 : Flywheel
14 : Drive Motor
15 : Connecting Belt
16 : Driving Belt
17 : Transmission Shaft
18 : U-base Structure
19 : Tensioning Mechanism
20 : Timing Pulley
21 : Connecting Rods
22 : C-bracket
23 : Supporting Studs
24 : Levelling Pads
25 : Drive Mechanism
26 : Structure
27 : Cable
28 : Support Base
29 : Cable Mounting Support
30 : Conveyor Tray C-bracket
, Claims:WE CLAIM:
1. A system (100) for conveying articles, the system (100) comprising:
a drive motor (14) mounted on a system frame (6) and configured to provide a driving motion to a timing pulley (20),
wherein the timing pulley (20) is mounted on an output shaft of the drive motor (14);
a conveyor tray (1) mounted on an end of a plurality of oscillating links (2), wherein the other end of the plurality of oscillating links (2) is pivoted on the system frame (6);
a flywheel (13) configured to receive the driving motion from the timing pulley (20) via a connecting belt (15);
a drive mechanism (25) configured to convert the driving motion of the flywheel (13) into a motion of the conveyor tray (1) for conveying articles; and
a counter mass assembly (5) configured to move in a direction opposite to the motion of the conveyor tray (1).
2. The system (100) as claimed in claim 1, wherein the drive mechanism (25) comprises a driving pulley (7), a driven pulley (8) and an idler pulley (9), wherein:
the driving pulley (7), the driven pulley (8) and the idler pulley (9) are connected via a driving belt (16),
the driving pulley (7) is mounted on a transmission shaft (17) of the flywheel (13) and configured to receive the driving motion from the flywheel (13) via the transmission shaft (17),
the driven pulley (8) is mounted on a driving crankshaft (12) and configured to receive the driving motion from the driving pulley (7) via the driving belt (16), and
the idler pulley (9) is configured to provide a belt compensation of the driving belt (16); and
the drive mechanism (25) is configured to:
oscillate the counter mass assembly (5) in the direction opposite to the motion of the conveyor tray (1) via the plurality of oscillating links (2); and
convey articles in the direction of the motion of the conveyor tray (1) via the conveyor tray (1).
3. The system (100) as claimed in claim 2, wherein the drive mechanism (25) comprises a driver connecting link (3) and a balancer connecting link (4) configured for converting the driving motion of the driven pulley (8) into an oscillatory motion of the plurality of oscillating links (2),
wherein the plurality of oscillating links (2) transmits the said oscillatory motion as a two-dimensional motion to the conveyor tray (1) such that the conveyor tray (1) conveys articles in the direction of the said two-dimensional motion, and
wherein the said oscillatory motion of the plurality of oscillating links (2) enables the counter mass assembly (5) to move in a direction opposite to the two-dimensional motion of the conveyor tray (1).
4. The system (100) as claimed in claim 3, wherein the said two-dimensional motion of the conveyor tray (1) is in X-Y cartesian coordinate plane.
5. The system (100) as claimed in claim 1, wherein the system (100) comprises a variable frequency drive coupled to the drive motor (14) and configured to maintain a constant angular velocity of the drive motor (14).
6. The system (100) as claimed in claim 2, wherein the transmission shaft (17) of the flywheel (13) is arranged such that the axis of rotation of the flywheel (13) is parallel to the axis of rotation of the timing pulley (20).
7. The system (100) as claimed in claim 1, wherein the counter mass assembly (5) is arranged on a bottom side of the conveyor tray (1), and the counter mass assembly (5) is configured to:
counter the linear and angular momentum generated by the motion of the conveyor tray (1);
a weight corresponding to a total weight of the articles conveyed by the conveyor tray (1);
be supported by the plurality of oscillating links (2), wherein the plurality of oscillating links (2) comprises two pairs of oscillating links; and
move in a direction opposite to the motion of the conveyor tray (1) at an angular phase difference of 180°.
8. The system (100) as claimed in claim 2, wherein the system (100) comprises a tensioning mechanism (19) configured to adjust the tension of the driving belt (16),
wherein the tensioning mechanism (19) comprises a tensioner wheel (10) configured to rotate freely and engage with the driving belt (16), to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt (16).
9. The system (100) as claimed in claim 2, wherein the driving pulley (7) is configured to be concentric with the flywheel (13) and the driven pulley (8) and the idler pulley (9) are configured to be eccentric pulleys such that the driving pulley (7), the driven pulley (8) and the idler pulley (9) form an isosceles triangle arrangement,
wherein the distance between centres of the driving pulley (7) and the driven pulley (8) is equal to the distance between the centres of the driving pulley (7) and the idler pulley (9),
wherein the driven pulley (8) and the idler pulley (9) are positioned at an angular phase difference such that the driving belt (16) lost by the driven pulley (8) is gained by the idler pulley (9) to maintain a constant length of the driving belt (16) in the drive mechanism (25),
wherein the angular phase difference is the difference in the angle of the first contact point of the driving belt (16) on the driven pulley (8) and the idler pulley (9), and
wherein the isosceles triangle arrangement enables the placement of the driving belt (16) at a maximum radius of the driven pulley (8) when the driving belt (16) is at a minimum radius of the idler pulley (9), and vice versa, to maintain a constant length of the driving belt (16) in the drive mechanism (25).
10. The system (100) as claimed in claim 7, wherein a first pair of oscillating links from the two pairs of oscillating links is of a different height than a second pair of oscillating links from the two pairs of oscillating links.
11. The system (100) as claimed in claims 2 and 10, wherein the driving crankshaft (12) comprises a first crank pin and a second crank pin, placed at a phase difference of 180° from each other, configured to convert the driving motion of the driven pulley (8) into an oscillatory motion of the plurality of oscillating links (2), wherein:
the first crank pin engages with a driver connecting link (3) configured to oscillate the first pair of oscillating links,
wherein the first pair of oscillating links is configured to move the conveyor tray (1) in the two-dimensional motion,
the second crank pin engages with a balancer connecting link (4) configured to oscillate the second pair of oscillating links,
wherein the second pair of oscillating links is configured to move the counter mass assembly (5) in a direction opposite to the motion of the conveyor tray (1).
12. The system (100) as claimed in claim 11, wherein the eccentricities of the driven pulley (8) and the idler pulley (9) and the eccentricities of the first and the second crank pin are designed such that the articles stay in contact with the conveyor tray (1) during the two-dimensional motion of the conveyor tray (1).
13. The system (100) as claimed in claim 2, wherein the phase difference between the axis of the driving crankshaft (12) and the axis of the driven pulley (8) governs the acceleration of the motion of the conveyor tray (1).
14. The system (100) as claimed in claim 1, wherein:
the connecting belt (15) is a high-tension carbon fiber belt with a high fatigue loading capacity.

15. A method (600) for conveying articles, the method (600) comprising:
providing (610), by a drive motor (14), a driving motion to a timing pulley (20) mounted on an output shaft of the drive motor (14);
receiving (620), via a connecting belt (15), the driving motion from the timing pulley (20) to a flywheel (13) mounted on a transmission shaft (17);
transmitting (630), via the transmission shaft (17), the driving motion from the flywheel (13) to a driving pulley (7) mounted on the transmission shaft (17);
receiving (640), via a driving belt (16), the driving motion from the driving pulley (7) to a driven pulley (8);
providing (650), by an idler pulley (9), a belt compensation of the driving belt (16);
converting (660), via a driver connecting link (3) and a balancer connecting link (4), the driving motion of the driven pulley (8) into an oscillatory motion of a plurality of oscillating links (2);
transmitting (670), via the plurality of oscillating links (2), the oscillatory motion into a motion of a conveyor tray (1);
oscillating (680), via the plurality of oscillating links (2), a counter mass assembly (5) in a direction opposite to the motion of the conveyor tray (1); and
conveying (690) articles, via the conveyor tray (1), in the direction of the motion of the conveyor tray (1).
16. The method (600) as claimed in claim 15, wherein the method (600) comprises:
maintaining a constant tension in the driving belt (16) by a tensioning mechanism (19) comprising a tensioner wheel (10) configured to rotate freely and engage with the driving belt (16), to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt (16); and
maintaining a constant tangential velocity of the driving belt (16) as a result of the constant angular velocity of the driving pulley (7).
17. The method (600) as claimed in claim 15, wherein converting (660) the driving motion of the driven pulley (8) into an oscillatory motion of a plurality of oscillating links (2) comprises a conversion of the constant tangential velocity of the driving belt (16) into a variable angular velocity of the driven pulley (8) in proportion to the eccentricity of the driven pulley (8).
18. The method (600) as claimed in claim 17, wherein the conversion of the constant tangential velocity of the driving belt (16) into a variable angular velocity of the driven pulley (8) is in proportion to a mean radius of the driven pulley (8), eccentricity of the driven pulley (8), the constant tangential velocity of the driving belt (16) and an angular position of the driving belt (16).
19. The method (600) as claimed in claim 15, wherein the method (600) comprises:
converting, by a drive mechanism (25) formed by the driving pulley (7), the driven pulley (8) and the idler pulley (9), the driving motion of the timing pulley (20) into a two-dimensional motion of the conveyor tray (1); and
tensioning, by the tensioning mechanism (19), the driving belt (16),
wherein the tensioning mechanism (19) comprises the tensioner wheel (10) configured to rotate freely and engage with the driving belt (16) to equilibrate the tension and reduce the belt flapping and fatigue loading in the driving belt (16), and
wherein the tensioning mechanism (19) is configured to control the acceleration and velocity of the two-dimensional motion of the conveyor tray (1) and the drive mechanism (25).
Dated this 17th Day of March 2023
Deepak Pawar
Agent for the Applicant
IN/PA-2052