MECHANISM

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority from Indian provisional patent application No. 201841015919, filed April 27, 2018, which is incorporated herein in its entirety by this reference thereto.

TECHNICAL FIELD

[0002] The present disclosure relates to a mechanism for converting a rotary motion into a reciprocating motion, more particularly, to an apparatus employing the mechanism for flattening a doughball to prepare a flatbread.

BACKGROUND

[0003] Press tool or mechanical press is known in the art for altering the shape of a workpiece or an object by application of pressure force. As such, the press tool is generally used for deforming or altering the shape of the object. One such application, where pressure force is required for deforming the object is the cooking application. The modem technology has allowed incorporation of devices used in the cooking industry in home appliances, for automating food preparation process for users.

[0004] One such home cooking appliance may be a flatbread making apparatus. The flatbread making apparatus generally includes devices for dosing metered quantity of flour and water. A mixer unit receives the metered quantity of flour and water, for kneading the flour into a doughball, which is required for preparing the flatbread such as a chapati, a tortilla, a pita bread, a crepe and the like. The doughball is subsequently routed to a mechanical press, where the flattening and baking operations are carried out. The mechanical press includes a platen surface which traverses from a retracted position to an extended position for engaging and flattening the doughball. Thus, apart from the ingredients used in the flour and the quality of the kneading, flattening of the doughball also plays a significant role in the quality of the flatbread prepared.

[0005] However, in the conventional mechanical presses, a constant force is exerted from the point of actuation of the platen surface from its retracted position. The constant force applied onto the doughball is insufficient to flatten the doughball completely, due to the inherent elastic property of the flour, particularly wheat flour. In other words, for flattening the wheat flour, a dynamic force which increases in magnitude while traversing towards the extended position is required for flattening the doughball, which is not attained from the conventional mechanical presses. Moreover, as the pressure force requirement is minimal while engaging the doughball, the additional pressure is unutilized resulting in wastage of energy. Though a mechanical press of higher capacity or size can be replaced to suit the requirement of flattening the doughball, the aforementioned problems persist and intensify, rendering the device unsuitable as a home appliance. Additionally, the conventional mechanical presses include plurality of contact surfaces, which magnifies energy losses in the presses during relative motion between contact surfaces movement therein, which is undesirable.

[0006] Therefore, there exists a need for techniques of flattening the doughball, which can overcome one or more limitations stated above in addition to providing other technical advantages.

[0007] The information disclosed in this background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgment that this information forms the prior art already known to a person skilled in the art.

SUMMARY

[0008] Various embodiments of the present disclosure provide a mechanism for converting a rotary motion into a reciprocating motion. The mechanism includes a frame member and a crankshaft member pivotally mounted to the frame member. The crankshaft member is coupled to an actuator, which is configured to rotate the crankshaft member. A first link including a first end pivotally coupled to the crankshaft member via a connecting member and a second end pivotally coupled to a movable member is provided, wherein the first link is adapted to reciprocate the movable member between an extended position and a retracted position corresponding to the rotation of the crankshaft member. A coupler link having one end pivotally mounted to a junction of the first end and the connecting member, and another end pivotally mounted to the frame member is provided. The coupler link is adapted to guide the movable member during the reciprocating motion between the extended position and the retracted position. In an embodiment, a press tool is provided. The press tool includes a first platen surface and a second platen surface mounted to a frame member. The second platen surface is aligned coaxially to the first platen surface. The crankshaft member is pivotally mounted to the frame member and coupled to an actuator, which is configured to rotate the crankshaft member. The first link including the first end and the second end is provided. The first end is pivotally coupled to the crankshaft member via a connecting member and the second end is pivotally coupled to the first platen surface. The first link is adapted to reciprocate the first platen surface between the extended position and the retracted position relative to the second platen surface corresponding to the rotation of the crankshaft member. The coupler link having one end pivotally mounted to the pivoting junction of the first end and the connecting member, and another end pivotally mounted to the frame member is provided. The coupler link is adapted to guide the first platen surface during the reciprocating motion between the extended position and the retracted position. Additionally, a control module electronically coupled to the actuator is provided. The control module is configured to control operation of the crankshaft member for controlling the reciprocating motion of the first platen surface between the extended position and the retracted position.

[0009] In an embodiment, a flatbread making apparatus is provided. The flatbread apparatus includes a flour container mounted to a support frame, for dispensing a metered quantity of flour and a water container mounted to the support frame for dispensing a metered quantity of water. A mixer unit is juxtaposed below the flour container and the water container. The mixer unit is configured to receive the flour dispensed from the flour container and water from the water container for kneading the flour into a doughball. The press tool is configured to receive the doughball from the mixer unit and is adapted to flatten the doughball to form a flatbread. The press tool includes the first platen surface and the second platen surface mounted to a bottom portion of the frame member. The second platen surface is aligned co-axially to the first platen surface and is configured to receive the doughball from the mixer unit. The crankshaft member is pivotally mounted to the frame member and is coupled to the actuator, which is configured to rotate the crankshaft member. The first link including a first end pivotally coupled to the crankshaft member via the connecting member and a second end pivotally coupled to the first platen surface is provided. The first link is adapted to reciprocate the first platen surface between an extended position and a retracted position relative to the second platen surface corresponding to the rotation of the crankshaft member. The first platen surface is configured to flatten the doughball at the extended position. The coupler link having one end pivotally mounted to the pivoting junction of the first end and the connecting member, and another end pivotally mounted to the frame member. The coupler link adapted to guide the first platen surface during the reciprocating motion between the extended position and the retracted position. Further, the bracket having the first end pivotally coupled to the frame member via the support link and a second end coupled to the first platen surface. The bracket is supported by the balancer link and is configured to prevent tilting of the first platen surface during the reciprocating motion between the extended position and the retracted position. The bracket, the balancer link, the frame member and the support link form a parallelogram linkage, the parallelogram linkage configured to traverse the movable member about an arcuate path. Additionally, the control module electronically coupled to the actuator is provided. The control module is adapted to control operation of the crankshaft member for controlling the reciprocating motion of the first platen surface between the extended position and the retracted position.

[0010] Other aspects and exemplary embodiments are provided in the drawings and the detailed description that follows.

BRIEF DESCRIPTION OF THE FIGURES

[0011] The following detailed description of illustrative embodiments is better understood when read in conjunction with the appended drawings. For the purpose of illustrating the present disclosure, exemplary constructions of the disclosure are shown in the drawings. However, the present disclosure is not limited to specific methods and instrumentalities disclosed herein. Moreover, those skilled in the art will understand that the drawings are not to scale. Wherever possible, like elements have been indicated by identical numbers:

[0012] FIG. 1 is a perspective view of a mechanism for converting a rotary motion to a reciprocating motion, in accordance with an exemplary embodiment of the present disclosure; [0013] FIG. 2 A is a front planar view of the mechanism of FIG. 1, illustrating a movable member in a retracted position, in accordance with another exemplary embodiment of the present disclosure;

[0014] FIG. 2B is a front planar view of the mechanism of FIG. 1, illustrating the movable member in an intermediate position, in accordance with an exemplary embodiment of the present disclosure;

[0015] FIG. 2C is a front planar view of the reciprocating press in of FIG. 1, illustrating the movable member in an extended position, in accordance with an exemplary embodiment of the present disclosure;

[0016] FIG. 3 is a perspective view of a press tool configured with the mechanism of FIG. 1, in accordance with an exemplary embodiment of the present disclosure;

[0017] FIG. 4A is a front planar view of the press tool of FIG. 3, illustrating a first platen surface in a retracted position, in accordance with another exemplary embodiment of the present disclosure;

[0018] FIG. 4B is a front planar view of the press tool of FIG. 3, illustrating the first platen surface in an intermediate position, in accordance with an exemplary embodiment of the present disclosure;

[0019] FIG. 4C is a front planar view of the press tool of FIG. 3, illustrating the first platen surface in an extended position, in accordance with an exemplary embodiment of the present disclosure;

[0020] FIG. 5A is a front planar view of the flatbread apparatus including the press tool of FIG. 3, illustrating the first platen surface in the retracted position, in accordance with another exemplary embodiment of the present disclosure;

[0021] FIG. 5B is a front planar view of the flatbread apparatus including the press tool of FIG. 3, illustrating the first platen surface in the intermediate position engaging a doughball, in accordance with an exemplary embodiment of the present disclosure; and

[0022] FIG. 5C is a front planar view of the flatbread apparatus including the press tool of FIG. 3, illustrating the first platen surface in an extended position flattening the doughball, in accordance with an exemplary embodiment of the present disclosure.

[0023] The drawings referred to in this description are not to be understood as drawn to scale except if specifically noted, and such drawings are only exemplary in nature.

DETAILED DESCRIPTION

[0024] In the following description, for purposes of explanation, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure. It will be apparent, however, to one skilled in the art that the present disclosure can be practiced without these specific details. Descriptions of well-known components and processing techniques are omitted so as to not unnecessarily obscure the embodiments herein. The examples used herein are intended merely to facilitate an understanding of ways in which the embodiments herein may be practiced and to further enable those of skill in the art to practice the embodiments herein. Accordingly, the examples should not be construed as limiting the scope of the embodiments herein.

[0025] Reference in this specification to“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 of the present disclosure. The appearance of the phrase“in an embodiment” in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. Moreover, various features are described which may be exhibited by some embodiments and not by others. Similarly, various requirements are described which may be requirements for some embodiments but not for other embodiments.

[0026] Moreover, although the following description contains many specifics for the purposes of illustration, anyone skilled in the art will appreciate that many variations and/or alterations to said details are within the scope of the present disclosure. Similarly, although many of the features of the present disclosure are described in terms of each other, or in conjunction with each other, one skilled in the art will appreciate that many of these features can be provided independently of other features. Accordingly, this description of the present disclosure is set forth without any loss of generality to, and without imposing limitations upon, the present disclosure.

OVERVIEW

[0027] Various embodiments of the present disclosure provide a mechanism for converting a rotary motion to a reciprocating motion. The mechanism is modular for use in press tools for applying pressure force onto an object for deformation. The mechanism is configured to apply a dynamic force onto the object via a platen surface of the press tool while preventing tilting of the platen surface during application of the pressure force. The mechanism is thus, configured to provide a stable platform for the platen surface during application of the pressure force and thereby ensuring uniform distribution of the pressure force onto the object. Additionally, the dynamic force exerted by the mechanism, increases in magnitude while deforming the object.

[0028] The mechanism includes a crankshaft member pivotally mounted on a frame member and coupled to an actuator, which is configured to rotate the crankshaft member in either a clockwise direction or an anti-clockwise direction. A first link is provided in the mechanism, which includes a first end pivotally mounted to a crankpin of the crankshaft member via a connecting member and a second end mounted to a movable member. The first link is adapted to reciprocate the movable member between an extended position and a retracted position corresponding to the rotation of the crankshaft member. Further, a coupler link is included in the mechanism, for guiding the movable member during its reciprocating motion between the extended position and the retracted position. The coupler link is included such that, one end is pivotally mounted to a pivoting junction of the first end and the connecting member and another end mounted pivotally to the frame member. Further, a parallelogram linkage is coupled to the first link, for preventing tilt of the movable member in a direction perpendicular to its reciprocating motion while also guiding the movable member along an arcuate path. This configuration also ensures that a higher magnitude of load can be applied uniformly onto the object via the movable member.

[0029] In an embodiment, the mechanism is configured to be incorporated into the press tool, for applying pressure force onto the object for deformation. In the press tool, the mechanism is configured to reciprocate a platen surface, acting as the movable member, used for applying pressure force onto the object. In an embodiment, the press tool incorporating the mechanism is configured in flatbread making apparatus for flattening a doughball.

[0030] In an embodiment, the term‘link’ hereinafter referred to in the description may refer to a kinematic link in a kinematic chain. The‘link’ may be constituted with multiple elements which function as a single unit for transmitting the force to the resistant body. For example, the first link of the mechanism may include multiple elements configured function as a single element with the primary focus being to enhance the stability of the mechanism during transfer of force to the movable member.

[0031] In an embodiment, the term‘movable member’ hereinafter referred to in the description may refer to any member such as but not limited to a piston member, a platen surface or any other member, which is configured to reciprocate corresponding to the actuation of the links in the mechanism.

[0032] Various embodiments of a mechanism for converting a rotary motion into a reciprocating motion are explained below in a detailed manner, herein with reference to FIG. 1 to FIG. 5A-5C.

[0033] FIG. 1 in one exemplary embodiment of the present disclosure illustrates a perspective view of a mechanism (100) for converting a rotary motion into a reciprocating motion. The mechanism (100) includes a frame member (102), which acts as a base structure, for supporting the links of the mechanism (100). The frame member (102) may also act as a shield structure to the mechanism (100), for providing ingress protection. The frame member (102) provides kinematical constraints required for the operation of the links of the mechanism (100). The frame member (102) may be any of a rigid or supporting structure, which can be mounted on a platform, a ceiling, a wall or a floor or any other platform as per feasibility and requirement. In an embodiment, the frame member (102) may be configured as a front frame member (l02a) and a rear frame member (l02b), with the rear frame member (l02b) mounted behind the front frame member (102 a) via a plurality of mounting brackets (105). The mounting brackets (105) engage with the front frame member (l02a) and the rear frame member (l02b) at multiple locations along their perimeters for maintaining an offset therebetween and to form a casing-like structure. The casing-like structure confines the links of the mechanism (100) between the front frame member (l02a) and the rear frame member (l02b), while also enhancing the stability of the frame member (102) during operation of the mechanism (100). The frame member (102) may also include a top portion (l02c) and an intermediate portion (l02d) for supporting the links of the mechanism (100), while a bottom portion (l02e) of the frame member (102) is mounted on the platform (not shown in Figures). Alternatively, the links of the mechanism (100) may be supported interchangeably on any surface of the frame member (102), while either of the top portion (l02c), the intermediate portion (l02d) and the bottom portion (l02e) is mounted on the platform. In an embodiment, the top portion (l02c) may be arch-shaped portion of the frame member (102), the intermediate portion (l02d) may be the side portions of the frame member (102) and the bottom portion (l02e) may be the bottom surface of the of the frame member (102) (as shown in FIG. 2). In an embodiment, the links of the mechanism (100) may be configured to be mounted on either of the front frame member (l02a) or the rear frame member (l02b) as per design feasibility and requirement.

[0034] Further, a crankshaft member (104) is pivotally mounted, for example to the intermediate portion (l02d), of the frame member (102). Alternatively, for the frame member (102) in the form of the casing, the crankshaft member (104) is positioned in between the front frame member (l02a) and the rear frame member (l02b) at the intermediate portion (l02d). The crankshaft member (104) is coupled to an actuator (119), such as an electric motor, a hydraulic actuator, a pneumatic actuator and the like, for receiving power for axial rotation. A crank pin (l04a) extends eccentrically from the axis (not shown in Figures) of the crankshaft member (104). The crank pin (l04a) acts as a cam surface, so that a link when connected to the crank pin (l04a) reciprocates upon rotation of the crankshaft member (104).

[0035] The mechanism (100) further includes a first link (106) pivotally coupled to the crankshaft member (104) via a connecting member (108). The first link (106) includes a first end (l06a) pivotally mounted on the connecting member (108) to form a junction (130), while the connecting member (108) in-tum pivotally connects on to the crank pin (l04a) of the crankshaft member (104). In an embodiment, the first end (l06a) is pinned or pivotally mounted to an end (l08a) (for e.g. as shown in FIG. 2A) of the connecting member (108), while the other end (l08b) (for e.g. as shown in FIG. 2A) of the connecting member (108) is pinned or pivotally mounted to the crank pin (l04a). Alternatively, the first end (l06a) may be pinned or pivotally mounted at any location along the length of the connecting member (108) as per design feasibility and requirement. Further, the first link (106) includes a second end (l06b) pivotally mounted, for example to a central portion, of a movable member (110). This configuration of the first link (106), the connecting member (108) and the movable member (110) ensures transfer of force from the crankshaft member (104) to the movable member (110). The transfer of force results in conversion of the rotational motion of the crankshaft member (104) into a reciprocating motion of the movable member (110), via the connecting member (108). The movable member (110) is adapted to be reciprocate between an extended position (120) (for e.g. as shown in FIG. 2C) and a retracted position (122) (for e.g. as shown in FIG. 2A). In an embodiment, the extended position (120) may be the position of the movable member (110) proximal to the bottom portion (l02e) and the retracted position (122) may be the position of the movable member (110) distant from the bottom portion (l02e). Alternatively, the extended position (120) and the retracted position (122) of the movable member (110) may be adjusted as per requirement, by altering dimensions of any of the first link (106), the connecting member (108) or any other link associated with the movable member (110).

[0036] In an embodiment, similar to the configuration of the frame member (102), the first link (106) may also include a first element (l06c) and a second element (l06d). The second element (l06d) may be mounted parallelly behind the first element (l06c), while maintaining an offset distance therebetween, similar to the rear frame member (l02b). This configuration allows the second end (l06b) of each of the first element (l06c) and the second element (l06d) to be mounted at multiple points about the central portion of the movable member (110), ensuring additional stability to the movement of the movable member (110) during operation. Moreover, the multiple contact points on the movable member (110) ensure better control of operation and transfer of force from the crankshaft member (104) to the movable member (110). As an example the multiple points about the central portion may be proximal to the front end (llOa) and rear end (llOb) of the movable member (110). In an embodiment, the second end (l06b) is preferably mounted on a central portion (not shown in Figures) of the movable member (110) for structural stability during operation or transfer of force from the crankshaft member (104). A coupling bracket (124) may be provided at an intersection of the second end (l06b) and the movable member (110), for facilitating connection therebetween. The coupling bracket (124) is fixed onto the movable member (110), by conventional fixing means, for pivotally receiving the second end (l06b). The coupling bracket (124) may be any support member configured with shaped selected from one of L-shaped bracket, T-shaped bracket, or any other bracket which serves the purpose of facilitating connection between the second end (l06b) and the movable member (110).

[0037] The mechanism (100) further includes a coupler link (112) configured to guide the movable member (110) or facilitate transfer of rotary movement from the crankshaft member (104). The coupler link (112) includes one end (H2a) (for e.g. as shown in FIG. 2A) pivotally mounted to the junction (130) while another end (H2b) (for e.g. as shown in FIG. 2A) is pivotally mounted to the frame member (102) (for e.g. as shown in FIG. 2A). As an example, the another end (H2b) of the coupler link (112) is mounted to the top portion (l02c) of the frame member (102). In an embodiment, the coupler link (112) is mounted between the first element (l06c) and the second element (l06d) for maintaining the offset distance therebetween. The coupler link (112) being pivotally connected to the frame member (102) oscillates upon actuation of the connecting member (108) and the first link (106) via the crankshaft member (104). The oscillation of the coupler link (112) controls movement of the first link (106) for transferring rotary movement of the crankshaft member (104) to a translational movement of the movable member (110), thereby ensuring reciprocating motion of the movable member (110).

[0038] The mechanism (100) further includes a bracket (114) configured to prevent tilting of the movable member (110) during operation between the extended position (120) and the retracted position (122). The bracket (114) includes an aft end (H4a) pivotally mounted to the frame member (102) via a support link (116) and a distal end (H4b) pinned to the movable member (110) (for e.g. as shown in FIG. 2A), while being supported by a balancer link (118). The configuration of the bracket (114), the support link (116), the balancer link (118) and the frame member (102) forms a parallelogram linkage (132) (for e.g. as shown in FIG. 2A). Thus, during reciprocating motion of the movable member (110), the bracket (114), the support link (116) and the balancer link (118) oscillate with respect to their pivotal points on the frame member (102). Particularly, the bracket (114) is configured to traverse about the support link (116) and the balancer link (118), due to the parallelogram linkage (132) configuration. The movable member (110) due to its connection with the bracket (114), traverses the path identical to that of the bracket (114). As an example, when the bracket (114) traverses an arcuate path, the movable member (110) also traverses the arcuate path. In another example, when the bracket (114) traverses a straight-line path the movable member (110) traverses the straight-line path. Further, the parallelogram linkage (132) prevents tilting of the movable member (110) during operation of the movable member (110), which will be described in subsequent sections. In an embodiment, the bracket (114) may be configured with a profile selected from one of a C-shape, an L-shape or any other shape as per design feasibility and requirement. As an example, the bracket (114) is configured with the C-shaped profile in order to accommodate oscillatory motion of the coupler link (112) during operation of the movable member (110).

[0039] In an embodiment, similar to the configuration of the frame member (102) and the first link (106), the bracket (114) may also include a pair of elements (H4c, H4d), with one element (H4c) mounted towards the front end (llOa) of the movable member (110) while the other element (H4d) mounted parallelly behind the element (H4c). The pair of elements (H4c, H4d) may be pinned to the support link (116) by use of conventional mechanical techniques. This configuration of the bracket (114) further enhances the stability of the movable member (110) during its reciprocating motion.

[0040] In an embodiment, the links mounted onto the frame member (102) may be mounted as per the kinematic constraints required for operation of the mechanism (100), while also considering the design feasibility and requirement.

[0041] In an embodiment, the pivotal connection of the components of the mechanism (100) may be enabled by providing one of a hinged connection, a pinned connection or any other connection as per feasibility and requirement.

[0042] In an embodiment, the actuator (119) coupled to the crankshaft member (104) may be configured with a gear mechanism (not shown in the Figures) in order to vary the torque input transmitted to the crankshaft member (104). Alternatively, the actuator (119) may be coupled to any of the power transmission mechanism such as a belt drive mechanism or any other mechanism as per design feasibility and requirement.

[0043] Referring to FIGS. 2A-2C in conjunction with FIG. 1, the operational views of the movable member (110) upon actuation of the crankshaft member (104) is illustrated.

[0044] During initiation of the operation of the mechanism (100), the movable member (110) is located preferably at a retracted position (122). In the retracted position (122) of the movable member (110), the first link (106), the connecting member (108) and the coupler link (112) may be oriented away from the crankshaft member (104), while the bracket (114) of the parallelogram linkage (132) is oriented away from the bottom portion (l02e). Alternatively, the first link (106), the connecting member (108) and the coupler link (112) may be oriented towards the crankshaft member (104), while the parallelogram linkage (132) orients towards the bottom portion (l02e). In an embodiment, the orientation of the first link (106), the connecting member (108), the coupler link (112) and the parallelogram linkage (132) in the retracted position (122) of the movable member (110) may be selected based on at least one parameter such as the position or connecting points of the links on the frame member (102), the dimensions of the links and the shape of the links.

[0045] Referring to FIG. 2B in conjunction with FIG. 2A, upon actuation of the crankshaft member (104) by the actuator (119), for example about an anti-clockwise direction, the connecting member (108) and the first end (l06a) get pulled towards the crankshaft member (104). At this juncture, the coupler link (112) being connected to the first end (l06a) oscillates about a clockwise direction, due to which the first link (106) gets pushed towards the bottom surface (l02e). The actuation of the first link (106) correspondingly actuates the movable member (110) towards the bottom portion (l02e). During actuation of the movable member (110), the first link (106) oscillates about the anti-clockwise direction due to its pivotal connection with the movable member (110) and also due to the connection of the bracket (114) with the movable member (110). The bracket (114) of the parallelogram linkage (132) actuates along with the movable member (110), while the support link (116) and the balancer link (118) oscillate about their pivotal points in the anti-clockwise direction on the frame member (102). The bracket (114) maintains a straight-line path during actuation, due to the dimensions of the support link (116) and the balancer link (118). Due to the pivotal movement of the support link (116) and the balancer link (118) about their connecting points with the frame member (102), the bracket (114) operates the movable member (110) to traverse an arcuate path during its reciprocating movement towards the extended position (120) from the retracted position (122). The radius of the arcuate path traversed by the movable member (110) may vary based on the length of at least one of the balancer link (118) and the support link (116). During traversal of the movable member (110) from the retracted position (122) to the extended position (120) about the arcuate path, the movable member (110) moves towards the intermediate portion (l02d) of the frame member (102). Alternatively, during traversal of the movable member (110) from the retracted position (122) to the extended position (120) about the arcuate path, the movable member (110) may also move away the intermediate portion (l02d) of the frame member (102). The movable member (110) continues its actuation corresponding to the actuation of the crankshaft member (104), until the extended position (120) is reached. In the extended position (120), the first link (106) and the coupler link (112) may be aligned along a straight line, while the connecting member (108) may be oriented perpendicularly to the first link (106) and the coupler link (112) (as shown in FIG. 2C).

[0046] Referring to FIG. 2C, in conjunction with FIGS. 2A and 2B, the movable member (110) after reaching the extended position (120), now begins to retrace its movement towards the retracted position (122), upon further rotation of the crankshaft member (104). Thus, upon further rotation of the crankshaft member (104), the connecting member (108) and the first end (l06a) are pushed away from the crankshaft member (104). At this juncture, the coupler link (112) being connected to the first end (l06a) oscillates about the anti-clockwise direction, due to which the first link (106) gets pulled away from the bottom surface (l02e). The actuation of the first link (106) correspondingly actuates the movable member (110) away from the bottom portion (l02e). During actuation of the movable member (110), the first link (106) oscillates about the clockwise direction due to its pivotal connection with the movable member (110) and also due to the connection of the bracket (114) with the movable member (110). The bracket (114) of the parallelogram linkage (132) actuates along with the movable member (110), while the support link (116) and the balancer link (118) oscillate about their pivotal points in the clockwise direction on the frame member (102). The bracket (114) maintains a straight-line path during actuation, due to the dimensions of the support link (116) and the balancer link (118). Due to the pivotal movement of the support link (116) and the balancer link (118) about their connecting points with the frame member (102), the bracket (114) operates the movable member (110) to traverse the arcuate path during its reciprocating movement towards the retracted position (122) from the extended position (120). The radius of the arcuate path of the movable member (110) may vary based on the length of at least one of the balancer link (118) and the support link (116). During traversal of the movable member (110) from the extended position (120) to the retracted position (122) about the arcuate path, the movable member (110) moves away the intermediate portion (l02d) of the frame member (102). Alternatively, during traversal of the movable member (110) from the extended position (120) to the retracted position (122) about the arcuate path, the movable member (110) may also move towards the intermediate portion (l02d) of the frame member (102). The movable member (110) continues its actuation corresponding to the actuation of the crankshaft member (104), until the retracted position (122) is reached.

[0047] In an embodiment, the mechanism (100) is configured such that the links i.e. the first link (106), the connecting link (108) and the coupler link (112), operate the movable member (110) at a slower speed during its extension to the extended position (120) than that of its traversal or retraction to the retraction position (122), while maintaining uniform angular speed of the crankshaft member (104). In an embodiment, the mechanism (100) is configured such that the links gradually reduce the operating speed of the movable member (110) during its movement towards the extended position (120). As an example, the mechanism (100) is configured such that the links reduce the operating speed of the movable member (110) during its movement to the extended position (120) from the intermediate position (126). This configuration of operation of movable member (110) may be achieved by determining or adjusting the angular displacement of the crankshaft member (104) required for extension and retraction of the movable member (110). In an embodiment, the configuration or dimensions of the links may be suitably adjusted based on the configuration of the crankshaft member (104) for obtaining the desired speed of extension and retraction of the movable member (110) or for adjusting angular displacement of the crankshaft member (104) required for the extension and retraction of the movable member (110). In an embodiment, the configuration of the crankshaft member (104) and the crank pin (l04a) can also be altered as per desired speed of extension and retraction of the movable member (110).

[0048] In an embodiment, the rotary movement of the crankshaft member (104) may be non-linearly transmitted to the movable member (110). In other words, during certain preset angular displacement of the crankshaft member (104) (based on configuration of the links), the rotary movement is utilized for balancing the forces acting on the links, rendering the movable member (110) to retain its position. As an example, during traversal from the intermediate position (126) to the extended position (120), majority of the angular displacement of the crankshaft member (104) is utilized for balancing the forces acting on the links, thereby rendering reduced operating speed of the movable member (110). Alternatively, the rotary movement of the crankshaft member (104) may be transmitted linearly or exponentially based on the configuration of the links. In other words, during certain preset angular displacement of the crankshaft member (104), the rotary movement is utilized for movement of the links. As an example, during certain angular displacement of the crankshaft member (110), the movable member (110) may move correspondingly to the angular displacement, thereby rendering uniform movement of the movable member (110) corresponding to the angular displacement of the crankshaft member (104). In another example, during certain angular displacement of the crankshaft member (104), the movable member (110) may move at a rate greater than the angular displacement, thereby rendering greater movement of the movable member (110) even for smaller angular displacement of the crankshaft member (104).

[0049] In an embodiment, the traversal path of the movable member (110) is dependent on the traversal path of the bracket (114) and thus can be altered by varying the dimensions of the support link (116) and the balancer link (118) as per feasibility and requirement. Alternatively, the traversal path of the movable member (110) may be altered by varying the shape or configuration of the support link (116) and the balancer link (118).

[0050] In an embodiment, the movable member (110) may be operated to an intermediate position (126) upon selective angular displacement of the crankshaft member (104). The angular displacement of the crankshaft member (104) may be monitored by a rotary encoder (128) mounted coaxially to the crankshaft member (104). The rotary encoder (128) is electronically coupled with the control module (320) for determining the angular displacement of the crankshaft member (104).

[0051] In an embodiment, the links are configured such that the time taken for traversal of the movable member (110) to the extended position (120) from the retracted position (122) is equal to the time taken for traversal of the movable member (110) back to the retracted position (122).

[0052] FIG. 3 in one exemplary embodiment of the present disclosure illustrates a perspective view of a press tool (300). The press tool (300) includes the mechanism (100), wherein the second end (l06b) of the first link (106) is pivotally connected to a first platen surface (302) which behaves as the movable member (110) already described. The mechanism (100) is configured to reciprocate the first platen surface (302) relative to a second platen surface (304) which is coaxially fixed below the first platen surface (302) onto the bottom portion (l02e) of the frame member (102). The mechanism (100) in the press tool (300) is configured to apply a dynamic force onto an object secured to the second platen surface (304) via the first platen surface (302) for deformation. The mechanism (100) is also configured to prevent tilting of the first platen surface (302) during application of the pressure force on the object for deformation, thereby ensuring uniform distribution of pressure force onto the object. Therefore, the mechanism (100) in the press tool (300) provides a stable platform for the first platen surface (302) during application of the pressure force. The first platen surface (302) reciprocates between an extended position (120) (for e.g. as shown in FIG. 4C) and a retracted position (122) (for e.g. as shown in FIG. 4A) upon actuation of the crankshaft member (104) of the mechanism (100) as already described. In an embodiment, the dimensions of the first platen surface (302) and the second platen surface (304) are congruent, and are selected based on the configuration of the object that is to be deformed. Accordingly, the first platen surface (302) and the second platen surface (304) are replaceable in the mechanism (100) via conventional mechanical techniques based on feasibility and requirement.

[0053] The press tool (300) also includes a control module (320) (for e.g. as shown in FIG. 4A) which is electronically coupled to the actuator (119) of the mechanism (100). The control module (320) is adapted to control operation of the crankshaft member (104) via the actuator (119) for controlling the reciprocating movement of the first platen surface (302) between the extended position (120) and the retracted position (122). The control module (320) may be associated with a position sensor (306) which is configured to monitor the position of the first platen surface (302). The control module (320) controls operation of the actuator (119), based on the position detected by the position sensor (306). In an embodiment, the control module (320) may vary operation of the actuator (119) based on the magnitude of force to be exerted by the first platen surface (302). The control module (320) may also operate a transmission mechanism suitably, (now shown in Figures) while maintaining uniform operating speed of the actuator (119), for varying the operating speed of the first platen surface (302). In other words, the control module (320) can operate the transmission mechanism in a lower gear-ratio mode (can also be termed as high torque mode or low speed mode) for reducing operating speed of the first platen surface (302) and in a higher gear-ratio mode (can also be termed as low torque mode or high speed mode) for increasing the operating speed of the first platen surface (302). In the low gear mode of the transmission mechanism, maximum force is exerted by the first platen surface (302) while operating at a lower rate of speed. In the high gear mode of the transmission mechanism, minimal force is exerted by the first platen surface (302), while operating at a higher rate of speed.

[0054] In an exemplary embodiment, the configuration of the first platen surface (302) and the second platen surface (304) may be selected from one of a circular disc configuration, a rectangular configuration, a square configuration or any other configuration as per design feasibility and requirement. In an embodiment, the first platen surface (302) and the second platen surface (304) may be made of materials selected from one of a metallic material, a non-metallic material and a composite material. Further, the first platen surface (302) and the second platen surface (304) may be made of food grade materials or may be coated with a non-stick layer, for ensuring usability of the press tool (300) in home appliances, for example, for flattening a doughball (560) (for e.g. as shown in FIG. 5A) to prepare a flatbread (562) (for e.g. as shown in FIG. 5C). Additionally, the first platen surface (302) and the second platen surface (304) may be configured with smooth and polished surface in order to obtain a smooth profile of the flattened dough from the doughball (560).

[0055] In an embodiment, either of the first platen surface (302) and the second platen surface (304) may be configured with a work holding device or a work gripping mechanism (not shown in Figures) for securing the object thereupon. The work holding devices provide a secure mounting platform for the object on either of the first platen surface (302) and the second platen surface (304) during application of pressure onto the object. This configuration ensures that adequate support is provided to the object during deformation. In an embodiment, the work holding device configured on either of the first platen surface (302) and the second platen surface (304) may be selected from one of a T-slot, clamp or any other configuration as per design feasibility and requirement.

[0056] In an embodiment, the mechanism (100) may be connected to at least one of the first platen surface (302) and the second platen surface (304) as per design feasibility and requirement.

[0057] Referring to FIGS. 4A-4C in conjunction with FIG. 3, the operational view of the first platen surface (302) is illustrated.

[0058] During initiation of operation of the press tool (300), the control module (320) may firstly determine placement of the object onto the second platen surface (304), via at least one sensor (not shown in Figures) mounted proximal to the second platen surface (304). Upon determining the position of the object on the second platen surface (304), the control module (320) operates the actuator (119) for controlling operation of the first platen surface (302) which is located preferably at a retracted position (122). In the retracted position (122) of the first platen surface (302), the first link (106), the connecting member (108) and the coupler link (112) may be oriented away from the crankshaft member (104), while the parallelogram linkage (132) is oriented away from the bottom portion (l02e).

[0059] Referring to FIG. 4B in conjunction with FIG. 4A, upon actuation of the crankshaft member (104) by the actuator (119), for example about an anti-clockwise direction, the connecting member (108) and the first end (l06a) get pulled towards the crankshaft member (104). At this juncture, the coupler link (112) being connected to the first end (l06a) oscillates about a clockwise direction, due to which the first link (106) gets pushed towards the bottom surface (l02e). The actuation of the first link (106) correspondingly actuates the first platen surface (302) towards the bottom portion (l02e). During actuation of the first platen surface (302), the first link (106) oscillates about the anti-clockwise direction due to its pivotal connection with the first platen surface (302) and also due to the connection of the bracket (114) with the first platen surface (302). The bracket (114) of the parallelogram linkage (132) actuates along with the first platen surface (302), while the support link (116) and the balancer link (118) oscillate about their pivotal points in the anti-clockwise direction on the frame member (102). This configuration prevents tilting of the first platen surface (302) during application of pressure force onto the object. The first platen surface (302) continues its movement upon further actuation of the crankshaft member (104) while deforming the object (for e.g. as shown in FIG. 5C), until the extended position (120) is reached. The first platen surface (302) continues its traversal to the extended position (120) via the intermediate position (126), wherein the intermediate position (126) (for e.g. as shown in FIG. 4B) may be the position of contact of the first platen surface (302) with the object subjected to the deformation. However, the operating speed or movement speed of the movable member (110) reduces from the intermediate position (126), due to which a greater force acts on the object for deformation. In the extended position (120), the first link (106) and the coupler link (112) may be aligned in a straight line or in a substantially straight line (based on configuration of the links), while the connecting member (108) may be oriented perpendicularly to the first link (106) and the coupler link (112) (as shown in FIG. 4C).

[0060] The first platen surface (302) after reaching the extended position (120), now retraces its movement towards the retracted position (122), upon further rotation of the crankshaft member (104). Thus, upon further rotation of the crankshaft member (104), the connecting member (108) and the first end (l06a) are pushed away from the crankshaft member (104). At this juncture, the coupler link (112) being connected to the first end (l06a) oscillates about the anti-clockwise direction, due to which the first link (106) gets pulled away from the bottom surface (l02e). The actuation of the first link (106) correspondingly actuates the first platen surface (302) away from the bottom portion (l02e). During actuation of the first platen surface (302), the first link (106) oscillates about the clockwise direction due to its pivotal connection with the first platen surface (302) and also due to the connection of the bracket (114) with the first platen surface (302). The bracket (114) of the parallelogram linkage (132) actuates along with the first platen surface (302), while the support link (116) and the balancer link (118) oscillate about their pivotal points in the clockwise direction on the frame member (102). The first platen surface (302) continues its actuation corresponding to the actuation of the crankshaft member (104), until the retracted position (122) is reached. [0061] In an embodiment, the first platen surface (302) may be operated to an intermediate position (126) upon selective angular displacement of the crankshaft member (104). The angular displacement of the crankshaft member (104) may be monitored by a rotary encoder (128) mounted coaxially to the crankshaft member (104). The rotary encoder (128) is electronically coupled with the control module (320) for determining the angular displacement of the crankshaft member (104).

[0062] In an embodiment, the alternatives, examples and/or the embodiments of the mechanism (100) described in the Figures 1-2C, suitably apply for the press tool (200).

[0063] FIGS. 5 A in one exemplary embodiment of the present disclosure illustrates a flatbread making apparatus (500). The apparatus (500) is configured to prepare the flatbread (562) (for e.g. as shown in FIG. 5C) from the doughball (560). The flatbread making apparatus (500) includes a support frame (502) supporting a flour container (504) and a water container (506). The flour container (504) is configured for dispensing a metered quantity of the flour, while the water container (506) is configured for dispensing a metered quantity of water. A mixer unit (508) is juxtaposed below the flour container (504) and the water container (506) for receiving the flour and water, respectively. The mixer unit (508) is configured to knead the flour into the doughball (560). The mixer unit (508) is coupled to a motor (not shown in Figures) for rotating the mixer unit (508), to facilitate kneading of the flour into the doughball (560).

[0064] The apparatus (500) further employs a press tool (300) as already described with reference to FIG. 3, and thus the embodiments described in the FIG. 3 are suitably applicable in this section of the description. The press tool (300) is configured to receive the doughball (560) from the mixer unit (508) and adapted to flatten the doughball (560). The press tool (300) is also configured with heating elements (534a, 534b), provided on the first platen surface (302) and the second platen surface (304) respectively, for baking the flattened doughball to form the flatbread (562). The heating elements (534a, 534b) may be in direct or indirect contact with the first platen surface (302) and the second platen surface (304) respectively, for dissipating heat energy, required for baking the flattened doughball. Each of the heating elements (534a, 534b) are electrically coupled to a power source (not shown in Figures) for receiving power required for heating the first and the second platen surfaces (302, 304). Further, each of the heating elements (534a, 534b) is electronically coupled with the control module (320), so that the control module (320) can control the amount of heat energy dissipated during baking process. In an embodiment, the control module (320) controls dissipation of the heat energy by controlling the duration of a‘powered ON’ condition of the heating elements (534a, 534b). In an embodiment, the first platen surface (302) and the second platen surface (304) is configured with a temperature sensor (not shown in Figures), coupled to the control module (320), for determining surface temperature. The control module (320) may accordingly operate the heating elements (534a, 534b) for optimal dissipation of heat energy from the first platen surface (302) and the second platen surface (304) during the baking process. The control module (320) may also shut down the heating elements (534a, 534b) or the apparatus (500), when the temperature of the heating elements (534a, 534b) exceeds a threshold value, which may be defined by the user or may be pre-fed in the control module (320) based on the type of flour used. Further, the dissipation of heat energy from the heating elements (534a, 534b) may be based on parameters selected from one of type of flatbread (562) to be baked, type of flour used for preparing the doughball (560), quality of the flour used for preparing the doughball (560), a roast level of the flatbread (562) selected by the user and the like. In an embodiment, the heating elements (534a, 534b) may preferably mounted at a central portion of the first platen surface (302) and the second platen surface (304), for ensuring uniform heating of flattened doughball (560) during the baking process.

[0065] Moreover, a skirt member (541) is also provided on the first platen surface (302), for confining a hot air in the vicinity of the first platen surface (302), thereby reducing the baking time and the power required for heating the first and the second platen surfaces (302, 304). The skirt member (541) is configured to match the size of the second platen surface (304), so that the first platen surface (302) and the second platen surface (304) form an enclosure, thereby enabling optimum baking of the flatbread (562). The metal skirt (541) is configured to thermally isolate both the first platen surface (302) and the second platen surface (304) from the surroundings during the extended position (as shown in Fig. 5C). The skirt member (541) also ensures to trap hot air around the first platen surface (302) and the second platen surface (304), for maintaining their temperatures even when the heating elements (534a, 534b) are disabled by the control module (320). This configuration enhances thermal efficiency of the apparatus (500) during the baking operation. In an embodiment, the skirt member (541) may be made of materials selected from one of a metallic material, a non-metallic material or any other material as per design feasibility and requirement.

[0066] Furthermore, the apparatus (500) comprises an image sensor (542) mounted on the intermediate portion (l02d) of the frame member (102) and configured to capture images for determining the degree of baking of the flatbread (562) during the baking process. Alternatively, the image sensor (542) may be mounted on each of the first platen surface (302) and the second platen surface (304) for capturing images of baking of the flattened doughball. The image sensor (542) may be electronically coupled to the control module (320) for transferring the captured images of the flatbread (562) in form of series of images for illustrating the degree of baking. The control module (320) may be communicably coupled to the mobile communication device (546) of the user for sending the captured images. The user upon analysing the images may provide instructions to the control module (320) via the mobile communication device (546) for controlling the baking process. The image sensor (542) may be selected from one of a colour sensor, a camera, an image processing sensor or any other sensor as per requirement.

[0067] Further, at the retracting position (122) of the first platen surface (302) the doughball (560) is routed to the second platen surface (304) from the mixer unit (508). Upon determining the placement of the doughball (560), the control module (320) operates the crankshaft member (104), say the anti-clockwise direction, for operating the first platen surface (302). As the crankshaft member (104) displaces angularly, the first platen surface (302) moves towards the second platen surface (304) as already described above. At the intermediate position (126), the first platen surface (302) engages with the doughball (560) for deformation. Upon further angular displacement of the crankshaft member (104), the first platen surface (302) moves further towards the bottom portion (l02e) while deforming the doughball (560) into a flattened dough (for e.g. as shown in FIG. 5B). The process of deformation continues until the first platen surface (302) reaches the extended position (120), until the doughball (560) is completely deformed into the flattened dough (for e.g. as shown in FIG. 5C). In this juncture, the control module (320) operates the heating elements (534a, 534b), for baking the flattened dough. The baking process of the flattened dough is carried out, while the first platen surface (302) is in the near extended position (120). This arrangement is retained for a predetermined duration of time, for allowing baking of the flattened dough, due to the configuration of links as already described. Upon further actuation of the crankshaft member (104) via the control module (320) the first platen surface (302) retracts back to its retracted position (122). The retraction of the first platen surface (302) at this juncture enables puffing of the flattened doughball, thereby providing the flatbread (562). In an embodiment, to enable puffing of the flatbread (562), the first platen surface (302) may be maintained at a predetermined height (for e.g. in the range of about 2 mm to about 10 mm) above the flattened dough for a predetermined duration of time (for e.g. in the range of about 30 seconds to about 60 seconds). Subsequently, the first platen surface (302) may again move towards the retracted position (122) by the predetermined height for facilitating puffing. In an embodiment, the predetermined duration of time and the predetermined height of the first platen surface (302) may vary based on parameters such as but not limiting to recipe, type of dough, or any other parameter as per feasibility and requirement. Alternatively, for enabling puffing of the flattened doughball during the baking process, the control module (320) may operate the crankshaft member (104) for retracting the first platen surface (302) to a predetermined height and maintaining this position for a predefined duration of time.

[0068] Further, the image sensor (542) captures the images of the baked flatbread (562) and analyses the images for determining the quality of the baking process. The control module (320) based on the analysis of the images, may determine necessity of a second iteration of the baking process and accordingly control the apparatus (500). In an embodiment, the image sensor (542) may be configured to detect brown spots, or height of puffing, or any other parameter for determining the quality of the baking process. If the baking process is determined to be successful, the control module (320) operates the crankshaft member (104) further, for retracting the first platen surface (302).

[0069] In an embodiment, the predetermined duration of time where the first platen surface (302) maintains its extended position (120) may be based on parameters selected from one of quality of the flour, baking requirements of the user, size of the flattened doughball, or any other parameters as per design feasibility and requirement.

[0070] In an embodiment, the extended position (120), particularly in the apparatus (500) is selected based on the thickness requirement of the flatbread (562). Accordingly, the control module (320) may adjust the stroke length of the first platen surface (302) as per the thickness requirement of the flatbread (562). Alternatively, the extended position (120), particularly in the apparatus (500) is selected based on the force that is required to be applied onto the object or the doughball (560) for deformation.

[0071] In an embodiment, in the event of mis-positioning of the doughball (560) on the second platen surface (304) i.e. in other words not positioned on the centre of the second platen surface (304), the parallelogram linkage (132) provides additional stability to the first platen surface (302) so that the imbalance that may be caused during deformation of the doughball (560) is eliminated. The parallelogram linkage (132) also ensures stability to the first platen surface (302) during application of greater magnitude of force on the doughball (560), as the surface area of the flattened dough increases. In an embodiment, the control module (320) is configured to vary the angular speed of crankshaft member (104) for applying a dynamic force onto the doughball (560). In an embodiment, the control module (320) is configured to increase the angular speed of crankshaft member (104) for applying a greater magnitude of dynamic force onto the doughball (560) via the first platen surface (302) for flattening, while reducing the angular speed of crankshaft member (104) during retraction of the first platen surface (302). In an embodiment, the control module (320) may control angular speed of the crankshaft member (104) based on the desired diameter of the flattened doughball.

[0072] In an embodiment, an optical sensor or a camera (538) may determine the height of the puffed flatbread (562) and correspondingly sends a signal to the control module (320) for maintaining the distance between the first platen surface (302) and the second platen surface (304). Upon detecting the height of puffed flatbread (562), i.e. the height where puffing of the flatbread (562) ceases, the control module (320) controls the operation of the actuator (119) correspondingly for adjusting the gap between the first platen surface (302) and the second platen surface (304). In an embodiment, the control module (320) may increase the temperature of the first platen surface (302) and the second platen surface (304) as faster rate during an initial starting stage of the baking process for reducing a cold start time duration. The reduction in a cold start time is configured to increase the rate of the baking process. The cold start time in the baking process is the time required to initiate baking of the flatbread (562).

[0073] The sequence of operations described above may not be necessarily executed in the same order as they are presented. Further, one or more operations may be grouped together and performed in form of a single operation, or one operation may have several sub-operations that may be performed in parallel or in a sequential manner.

[0074] Various example embodiments of the present disclosure described herein, with reference to various schematic views and flow diagrams, are for illustrative purposes and provided numerous advantages and technical effects. For instance, the press mechanism is configured to scatter the powdered material while dispensing, thereby preventing dispensing of chunks of the powdered material. The prevention of dispensing of chunks inherently improves the accuracy and the precision of dispensing of the powdered material. Additionally, the press mechanism is scalable, modular and inexpensive.

[0075] The foregoing descriptions of specific embodiments of the present disclosure have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the present disclosure to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles of the present disclosure and its practical application, to thereby enable others skilled in the art to best utilize the present disclosure and various embodiments with various modifications as are suited to the particular use contemplated. It is understood that various omissions and substitutions of equivalents are contemplated as circumstance may suggest or render expedient, but such are intended to cover the application or implementation without departing from the spirit or scope of the claims.