CN116887723A

CN116887723A - Machine and compacting mechanism

Info

Publication number: CN116887723A
Application number: CN202180093299.8A
Authority: CN
Inventors: M·L·霍洛威; T-K·贡; 任翔; 乔瓦尼·贝兹·阿尔瓦雷斯; N·奥利韦里亚; 克里斯托弗·彼得·汉密尔顿·哈代; S·R·巴特; B·J·高斯林; A·拉德维格; C·K·K·李
Original assignee: Breville Pty Ltd
Current assignee: Breville Pty Ltd
Priority date: 2020-12-23
Filing date: 2021-12-22
Publication date: 2023-10-13
Also published as: CN219940342U; CN116829034A; CN116867404A

Abstract

A machine has a grinder, a grinding chute for delivering coffee powder along a flow path into a handle fitted on the machine, and a compacting unit having a compacting mechanism for compacting coffee powder held by the handle into a cake, wherein the compacting mechanism comprises a connection to a hammer, which connection is arranged to press a face of the hammer in an axial direction with respect to the handle during a compacting operation, and wherein the connection returns the hammer to an idle position in which the compacted face is moved along a lateral flow path. The application also relates to a machine for delivering coffee powder to a handle, a compacting mechanism and a coffee grinder.

Description

Machine and compacting mechanism

RELATED APPLICATIONS

The present application claims priority from australian patent application No. AU2020904817 and australian patent application AU2021221718, the contents of which are incorporated by reference.

Technical Field

The present application relates to a machine for grinding coffee and a compacting mechanism.

Background

Coffee machines generally have a grinder for grinding coffee beans and a grinder chute for delivering the ground coffee into a handle fitted in a handle holder of the coffee machine, in which the coffee is pressed into a cake using a hammer, and then steam and/or water is injected, which is filtered through the cake and extracted into a cup positioned under the handle.

Consistency in cake preparation is important for continuous extraction. This requires a uniform distribution of the coffee powder, a uniform compaction pressure for each compact, and when the dose of coffee powder and other variables, etc.

Maldistribution of the coffee grounds may result in a compacted coffee grounds cake having non-uniform spacing, density, and/or thickness of the coffee grounds and may result in a phenomenon known as the "channeling effect" in which steam and/or water preferentially passes through the cake along certain paths, resulting in non-uniform coffee extraction and insufficient aroma of the extracted coffee beverage.

Disclosure of Invention

According to an aspect of the invention, there is provided a machine having a grinder, a grinding chute for delivering coffee powder along a flow path into a handle fitted on the machine, and a compacting unit having a compacting mechanism for compacting coffee powder held by the handle into a cake, wherein the compacting mechanism comprises a connection to a hammer, the connection being arranged to press a face of the hammer in an axial direction with respect to the handle during a compacting operation, and wherein the connection returns the hammer to an idle position in which the compacted face is moved along the flow path.

In one embodiment, a coupling connects the hammer to the connector to enable the hammer to rotate relative to the mechanism between the rest position and the compacting position.

In one embodiment, the hammer engages the guide structure of the adjacent mechanism as the hammer moves between the rest position and the compacting position.

In one embodiment, the guide structure is a rail and the hammer includes a pivot spaced from the coupling to control pivotal movement of the hammer relative to the link.

In one embodiment, the hammer includes a pair of pivots and a pair of couplings, and the machine includes two sets of rails to guide the couplings and pivots.

In one embodiment, the guide means and pivot are vertically arranged when in the compacting position, and the guide structure comprises double tracks to guide the coupling and pivot respectively, the tracks being vertically aligned along the lower part and horizontally diverging in the upper part to move the guide means and pivot horizontally to rotate the hammer to the rest position.

In one embodiment, the guide and the pivot are attached to a support member extending from the body of the hammer, and the pivot extends laterally of the hammer a greater distance than the guide.

In one embodiment, a clearance space is defined between the support members, the clearance space providing clearance for the grinding chute when the hammer is rotated to the rest position.

In one embodiment, the mechanism is driven by a rotatable shaft operated by a lever connected to the shaft via a clutch to allow the lever to rotate freely when lifted from the home position.

In one embodiment, the machine includes a switch for initiating operation of the grinder, the switch being activated by lifting the lever.

In one embodiment, the machine further comprises a compaction force control assembly that biases the hammer toward the coffee grounds when the hammer is in the compacted position and applies a compressive force to the coffee grounds during formation of the compact.

In one embodiment, the mechanism includes a hinged connection driven by the shaft to move the hammer between the rest position and the compacting position, the compacting force control assembly biasing the hammer toward the coffee grounds when the hammer is in the compacting position and applying a compressive force to the coffee grounds during formation of the compact.

In one embodiment, the compaction force control assembly is a biasing element coupled between the members.

In one embodiment, the biasing element is in the form of a spring piston having a piston rod biased between the members by a spring.

In one embodiment, the members are connected for limited relative movement to accommodate different height positions of the hammer when the hammer is in the compacting position.

In one embodiment, the machine further comprises a sensor for determining the relative extension of the piston, thereby measuring the height of the compact formed by the hammer and determining the depth of compaction.

In one embodiment, the compaction force control assembly includes one or more springs positioned between a fixed portion of the assembly and a movable carriage that moves against a reaction pressure applied to the hammer when the hammer is engaged with the coffee grounds in the compaction position.

In one embodiment, the limit coupler limits the travel of the movable carriage.

In one embodiment, the position of the movable carriage is used to determine the relative height of the compact formed by the hammer.

In one embodiment, the mechanism comprises a connection in the form of a slider that is driven linearly by rotation of the shaft, the slider being connected to the hammer by an articulated arm that translates the hammer along the guide rail between the rest position and the compacting position.

In one embodiment, the mechanism is operated by a linear actuator connected to the body of the hammer by an articulated arm, the upper portion of the hammer having another pivot connection to rotate about the end of the grinding chute as the linear actuator moves the hammer between the rest position and the compacting position.

In one embodiment, the machine further comprises a handle support below the compacting unit, the handle support comprising a docking seat for receiving the handle, for receiving the coffee grounds, and a resilient clasp for retaining the handle in the docking seat.

In one embodiment, the handle bracket includes an access ramp for engaging the tab of the handle to automatically align the handle during insertion and lift the tab off the clasp and into the docking station.

In one embodiment, the handle support includes a sensor for determining whether the handle is loaded into the handle support.

In another aspect, there is provided a machine for delivering coffee grounds to a handle, the machine comprising: a grinder for grinding coffee powder into the handle; a compacting mechanism for compacting coffee powder in a handle along a path, the compacting mechanism comprising: a hammer comprising a surface for compacting coffee powder; and a connector connected to the hammer, wherein during a first portion of the path the connector orients the first surface in a first direction and during a second portion of the path the connector orients the first surface in a second direction, wherein the first direction and the second direction are different.

In another aspect, there is provided a machine for delivering coffee grounds to a handle, the machine comprising: a grinder for grinding coffee powder into the handle; a compacting mechanism for compacting coffee powder in a handle along a path, the compacting mechanism comprising: a hammer comprising a surface for compacting coffee powder; and a compaction actuator for moving the surface along the path, wherein during a first portion of the path the surface is oriented in a first direction and during a second portion of the path the surface is oriented in a second direction, wherein the first direction and the second direction are different.

In one embodiment, the compaction mechanism moves the hammer through a first portion and a second portion of the path between a rest position in which the surface is oriented in a first direction and a compaction position in which the surface is oriented in a second direction for performing a compaction operation.

In one embodiment, during the compacting operation, the compacting mechanism rotates the hammer between the first portion and the second portion of the path such that the compacting surface faces in the second direction to compact the coffee grounds.

In one embodiment, the hammer rotates in the rest position relative to the compacting position such that the compacting surface faces in a first direction that is offset from the second direction by an angle, whereby the hammer does not interfere with delivering coffee powder from the grinder into the handle.

In another aspect, a compacting mechanism for compacting coffee powder delivered from a coffee grind chute into a handle is provided, the compacting mechanism comprising a connector connected to a hammer, the connector being arranged to press a face of the hammer in an axial direction relative to the handle during a compacting operation, and wherein the connector returns the hammer to a rest position along a non-axial path relative to the handle between compacting operations such that the hammer does not interfere with delivering coffee into the handle when in the rest position.

In one embodiment, the compaction mechanism according to claim 36, wherein a clearance space is defined between the support members, the clearance space providing clearance for the grinding chute when the hammer is rotated to the rest position.

In one embodiment, the compacting mechanism further comprises a compacting force control assembly that biases the hammer towards the coffee powder when the hammer is in the compacting position and applies a compressive force to the coffee powder during formation of the compact.

In one embodiment, the mechanism includes a hinged connection driven by the shaft to move the hammer between the rest position and the compacting position, the pretension assembly biasing the hammer towards the coffee grounds when the hammer is in the compacting position and applying a compressive force to the coffee grounds during cake formation.

In one embodiment, the compacting mechanism further comprises a sensor for determining the relative extension of the piston, thereby measuring the height of the compact formed by the hammer and determining the depth of compaction.

In one embodiment, the limit coupler limits the travel of the movable carriage.

A coffee grinder comprising a coffee grinder, a grind chute from which coffee grounds are delivered into a handle for compaction into a compact, wherein the grind chute is centrally positioned above the handle and axially aligned with a bowl of the handle.

In one embodiment, the machine further comprises a compacting mechanism for compacting coffee powder delivered from the coffee grind chute into the handle, the compacting mechanism comprising a connection to the hammer, the connection being arranged to press the face of the hammer axially with respect to the handle during compacting operations, and wherein the connection returns the hammer to the rest position along a non-axial path with respect to the handle between compacting operations such that the hammer does not interfere with delivering coffee into the chute when in the rest position.

In one embodiment, the machine further comprises a compaction chute positioned in axial alignment with the grinding chute.

In one embodiment, the machine includes a handle support for positioning the handle below the compaction chute, the handle support including a docking seat for receiving the handle, a resilient clasp for receiving the coffee grounds, and for retaining the handle in the docking seat.

In one embodiment, the access ramp opens to a support surface that is vertically offset to accommodate a vertically offset tab of the handle.

In one embodiment, the machine further comprises a sensor for determining whether the handle is loaded into the handle holder.

Drawings

The present invention will now be described more fully, by way of non-limiting example only, with reference to the accompanying drawings, in which:

FIG. 1 is a perspective view of a machine;

FIG. 2 is another perspective view of the machine;

FIG. 3 is a partial cross-sectional view of the machine showing the compacting mechanism in an upper position;

FIG. 4 is a view similar to FIG. 3 showing the mechanism in a lower position;

FIG. 5 is a similar view showing the lever in a lowered position;

FIG. 6 is a perspective cross-sectional view showing a compacting mechanism;

FIG. 7 is a side cross-sectional view of the machine with the mechanism in a raised position;

FIG. 8 is a side cross-sectional view showing the mechanism in an intermediate position;

FIG. 9 is a side cross-sectional view showing the mechanism in a compacting position;

FIG. 10 is a side cross-sectional view showing the handle fitted to the machine in an under-dosed condition;

FIG. 11 shows the ideal height position of the hammer for an ideal dose condition;

FIG. 12 is a cross-sectional view showing the position of the hammer in an excess condition;

FIG. 13 is an enlarged view of the top of the machine showing the return means;

FIG. 14 is a view similar to FIG. 13, showing the return device in an extended state;

FIG. 15 illustrates the lever and compaction force control assembly in a raised position;

FIG. 16 is a view similar to FIG. 15 with the lever in the home position;

FIG. 17 is a perspective view of another example of a compacting mechanism with the lever in a home position;

FIG. 18 is a similar view showing the lever in a lower position;

FIG. 19 is a cross-sectional view of the mechanism of FIGS. 17 and 18 in a raised position;

FIG. 20 is a view similar to FIG. 19 showing the mechanism in an intermediate position;

FIG. 21 is a view similar to FIG. 20, showing the mechanism in a compacting position;

FIG. 22 is a schematic side perspective view of another example of a compaction mechanism;

FIG. 23 is a similar view of the mechanism as seen from the other side;

FIG. 24 shows the mechanism in a lower position;

FIG. 25 shows the mechanism in an upper position;

FIG. 26 is a partial cross-sectional view of the mechanism of FIG. 25;

FIG. 27 is a partial cross-sectional view of the mechanism as seen from the other side;

FIG. 28 is a cross-sectional view of the mechanism with the lever in the home position;

FIG. 29 is a cross-sectional view of the mechanism in a lower position;

FIG. 30 is a cross-sectional view of the mechanism in an intermediate position;

FIG. 31 is a top perspective view of a portion of a compaction mechanism;

FIG. 32 is a top perspective view of the mechanism as seen from the other side;

FIG. 33 shows a switch activated by a shaft;

FIG. 34 is a top perspective view showing the return device;

fig. 35 is a perspective view showing the position of the VR sensor;

FIG. 36 shows gears associated with levers;

FIG. 37 shows a mating gear for a drive mechanism;

FIG. 38 is a cross-sectional view of an example of another compaction mechanism in a lowered position;

FIG. 39 is a view similar to the view of FIG. 38, showing the mechanism in an intermediate position;

FIG. 40 is a cross-sectional view showing the mechanism in a raised position;

FIG. 41 is a perspective view showing the mechanism in a lowered position;

FIG. 42 is a perspective view of the mechanism in a raised position;

FIG. 43 is a perspective view of a portion of a compacting unit illustrating another example of a compacting mechanism;

fig. 43a to 43d show possible positions of the sensors in the compacting unit;

FIG. 44 is a cross-sectional view showing the mechanism in a raised position;

FIG. 45 is a view similar to FIG. 45 showing the mechanism in an intermediate position;

FIG. 46 is a view similar to FIG. 45, showing the mechanism in a compacting position;

FIG. 47 is an exploded view of the clutch;

FIG. 48 is another exploded view of the clutch;

FIG. 49 is a perspective view of an example of a hammer;

FIG. 50 is a cross-sectional view of the hammer;

FIG. 51 is an exploded view of the hammer as viewed from the underside;

fig. 52 is an exploded view of the hammer as seen from the upper side;

FIG. 53 is an exploded view of another example of a hammer;

FIG. 54 is an exploded view of the hammer of FIG. 53 as viewed from the upper side;

FIG. 55 is a cross-sectional view of another example of a hammer;

FIG. 56 is an enlarged cross-sectional view of a section of the hammer of FIG. 55;

FIG. 57 is a cross-sectional view of another example of a compacting unit;

FIG. 58 is a cross-sectional view of the compacting unit showing the hammer in an idle position;

FIG. 59 is a similar view of the compacting unit with the compacting mechanism removed for clarity;

FIG. 60 is a cross-sectional view of a portion of a compacting unit;

FIG. 61 is a perspective view of the compacting unit with a portion of the compacting mechanism removed to show the dual track;

FIG. 62 is an enlarged view of a sensor and damper used in the compacting unit;

FIG. 63 is an end view of the handle in the handle support;

FIG. 64 is a cross-sectional view of the handle support of FIG. 63;

FIG. 64A is a perspective view of a handle support;

FIG. 65 is an exploded view of the handle support;

FIG. 66 is a bottom perspective view of the handle in the handle bracket;

FIG. 67 is a diagrammatic representation of a system for operating a machine;

FIG. 68 shows a dosing algorithm;

FIG. 69 shows additional steps in the algorithm of FIG. 68;

FIG. 70 illustrates further steps in the algorithm of FIG. 68;

FIG. 71 shows another dose algorithm;

FIG. 72 is a front view of the machine;

FIG. 73 shows a portion of a user interface of the machine showing the correct dose;

FIG. 74 illustrates a user interface displaying an excessive number of conditions;

FIG. 75 illustrates a user interface showing an extreme overdose condition;

FIG. 76 shows a user interface showing an under-dose condition;

FIG. 77a is a perspective view of a cover on a compaction chute of a machine;

FIG. 77b is a perspective view of the cover removed from the machine;

FIG. 78 shows another example of a handle support;

FIG. 79 illustrates a front view of the bracket of FIG. 78;

FIG. 80 is a cross-sectional view taken along line A-A of FIG. 79;

FIG. 81 is a side view of the bracket of FIG. 78;

FIG. 82 is a cross-sectional view taken along line B-B of FIG. 81;

FIG. 83 illustrates an exploded view of another example of a hammer;

FIG. 84 shows an exploded view of the hammer of FIG. 83;

FIG. 85 is a side view of the hammer of FIG. 83;

FIG. 86 is a cross-sectional view taken along line A-A of FIG. 85;

FIG. 87 is a side view of the hammer of FIG. 83;

FIG. 88 is a cross-sectional view taken along line A-A of FIG. 87;

FIG. 89A is an exploded view of another example of a hammer;

FIG. 89B is an exploded view of the hammer of FIG. 89A; and is also provided with

Fig. 90 is a cross-sectional view of the machine of fig. 1 including the hammer of fig. 83-89.

Detailed Description

Examples of compaction mechanisms

Examples of compaction mechanisms will be described below, wherein like reference numerals will be used to refer to like parts.

Example 1

Fig. 1 shows an embodiment of a machine 1 having a compacting unit 2, a coffee bean hopper 3, a housing 4, a user interface panel 5, a lever 6 and a handle support 7 positioned above a drip tray 8.

Fig. 2 shows that the machine 1 has an adjustment dial 9 for setting the grinding size.

Fig. 3 is a partial cross-sectional view of the machine 1. A coffee grinder 10 is shown interfacing with the adjustment dial 9 for grinding coffee beans delivered from the hopper 3 of fig. 1 into coffee grounds. The lever 6 is shown in a home position corresponding to the compacting mechanism 11 being in a raised position.

In fig. 4, the lever 6 has been moved to a lowered position, which corresponds to the mechanism 11 being in the compacting position.

Fig. 5 also shows the lowered lever 6. The lever 6 is connected to a shaft 12 which serves as an actuator 13 to drive the mechanism 11 along the length of travel between a raised position and a compacting position.

Fig. 6 is a partial cross-sectional view, in which the lever 6 has been returned to the original position and the mechanism 11 is in the raised position. The mechanism 11 is coupled to a hammer 14 which is held in a raised rest position.

The mechanism 11 is provided with a compaction force control assembly 15 formed by a housing 16 which houses a biasing element 17 in the form of a compression spring 18. In some embodiments, the biasing element 17 may be in the form of other types of springs, such as tension springs. It is preferred that the biasing element 17 is preloaded/pretensioned (i.e. the biasing element is not in its natural position when installed) such that: the compaction force can be more precisely controlled; reducing the stroke length of the compacting mechanism, which results in a reduced height/size of the coffee machine to provide a more compact machine; reducing the necessary rotation of the lever 6 by the user; and reducing the force with which the user needs to compact the coffee grounds. It is preferable to have one or more biasing elements 17 acting on the connection 7 to control the compacting force applied to the ground coffee.

More specifically, the pre-tensioned or preloaded biasing element 17 provides the following benefits compared to a non-pre-tensioned (non-preloaded) biasing element 17: lower bias rates (lower spring rates in the current embodiment) to give a more consistent and accurate compaction force over the stroke length; and reducing the compression distance of the coffee powder over the stroke length of the mechanism 11 to achieve a predetermined compaction force, which allows to reduce the rotation of the lever 6 by the user and to reduce the force required by the user to rotate the lever 6 to compact the coffee powder, which, as mentioned above, can reduce the height and size of the machine 1 to provide a more compact design.

A sensor 20 is provided comprising a connecting rod 19 and the relative position of this connecting rod 19 can be used to monitor the distance travelled by the compacting mechanism 11. Upon compacting/pressing the coffee pad, the biasing element 17 is compressed, which results in a movement of the connecting rod 19. It should be noted that the sensor 20 with the connecting rod 19 is only an example of a means for measuring the travel distance of the compacting mechanism 11.

The grind chute 21 extends from the grinder 10, which when activated delivers ground coffee along a flow path 22 and through the compaction chute 23 to a central location of the handle support 7, which is directly below the compaction chute 23. The compacting mechanism 11 also travels within the compacting chute 23 between a raised position and a compacting position.

The rest position of the hammer 14 is outside the flow path 22 of the ground coffee when the mechanism 11 is raised, so as not to interfere with the delivery of the coffee through the compacting chute 23.

The relative positioning of the hammer 14 and the grinding chute 21 is more clearly shown in fig. 7.

The grinding chute 21 is positioned directly above and within the top region of the compaction chute 23 and is substantially aligned with the centerline 24 of the compaction chute 23. The mechanism 11 is in a raised position such that the face 25 of the hammer 14 and the mechanism 11 are rotated away from the lower end 26 of the chute 21.

The mechanism 11 comprises a connection 30 connected at one end 31 to the shaft 12 for fixed rotation with the shaft 12. Hammer 14 includes a base 27, a body 28, and a coupling 29 for connecting hammer 14 to a connector 30 through a rotational coupling 32 that allows hammer 14 to rotate when moving out of the rest position and returning to the rest position.

The compacting unit 2 has an inner housing 33 extending upwardly from the compacting chute 23. The housing 33 helps to contain the coffee grounds as they travel toward the compaction chute 23. The housing 33 has a guide structure 34 in the form of a slot 35 that guides the hammer 14 as it is rotated by the connector 30 and out of and back to the rest position.

Fig. 8 shows the lever 6 in a partially lowered state, which has caused the mechanism 11 to rotate to an intermediate position. The link 30 of the mechanism 11 is hinged with a first member 36 fixed to rotate with the shaft 12 when the lever 6 is depressed. The first member 36 is hinged to a second member 37 which pivots away from the first member 36. The second member 37 is connected to the hammer 14 such that downward movement of the second member 37 causes the hammer 14 to be lowered along the guide structure 34 and rotated under the grinding chute 21.

Fig. 9 shows that the second member 37 also includes a recess 38 for receiving the coupling 32 when the mechanism 11 is in the compacted position and the connector 30 is fully extended. In this position, rotational force from shaft 12 is translated into axial load on hammer 14 through coupling 32.

Fig. 10 shows the handle 40 fitted into the handle holder 7. The switch 41 is used to detect the presence of the handle 40 which previously enabled the grinder to be activated and caused the coffee grounds (not shown) to be delivered into the bowl 42 carried by the handle 40.

The mechanism 11 is in a compacting position in which the hammer 14 has been lowered through the compacting chute 23 of the compacting unit 2 to be inside the bowl 42 for pressing the coffee powder into a cake (also not shown for clarity).

Fig. 10 illustrates an under-dosing condition in which the amount of coffee powder that has been delivered to the handle 40 for compaction is less than the desired amount. The "ideal" quantity of coffee may be based on a number of parameters, such as coffee bean characteristics, grinder settings, brew settings, filter bowl geometry parameters, etc. The amount of coffee that it deems appropriate may also be selected by the user. In any event, in an under-dosed condition, the hammer 14 has been pressed to a position lower than ideal, and the second member 37 of the connector 30 is pushed towards the lower end 43 of the limited movement connection 44 with the first member 36 under the influence of the compaction force control assembly 15. Although an under-dosage condition is described, in an under-dosage, over-dosage or ideal condition: under the influence of the compacting force control assembly 15, the second member 37 is pushed towards the end of the limited movement connection 44 with the first member 36, wherein the reaction force of the hammer 14 on the coffee powder pushes the second member 37 against the bias of the compacting force control assembly 15, while the connecting rod 19 is driven back into the housing 16. The difference between the different states is the position of the end with respect to the limited movement connection 44.

Fig. 11 shows the height of the hammer 14 when a desired dose of coffee powder has been delivered into the handle 40. At this height, the reaction force of the hammer 14 on the coffee powder pushes the second member 37 against the bias of the compaction force control assembly 15 to drive the second member 37 to a higher position in the limited movement connection 44 such that the second member 37 pushes the connecting rod 19.

Fig. 12 shows an over-dosage condition in which more than the desired amount of coffee grounds have been delivered to the handle 40. In this condition, the hammer 14 is in a higher position and the reaction force on the hammer 14 causes the second member 37 to be pushed towards the upper end 45 of the limited movement connection 44 and the connecting rod 19 to be driven back into the housing 16.

Referring now to fig. 13, a cross-sectional view 46 of machine 1 is shown. The lever 6 is shown in the home position and the mechanism 11 in the corresponding raised position. Also shown is a return means 47 which biases the shaft 12 and lever 6 to the home position. The return means 47 are shown as an extension spring 48 acting between a fixed mounting bracket 49 and a control gear 50 connected to the shaft 12.

A rotational position sensor 51 is also provided which receives input from the cog 52 engaged with the gear 50 and allows the position of the lever 6 to be monitored by the relative rotational position of the shaft 12 which also provides an indication of the corresponding position of the mechanism 11. The rotation sensor 51 may also be placed in an alternative position and may for example be used to alternatively monitor the rotation of: a gear 50; a shaft 12; a damper 53; or lever 6

Also shown is a damper 53 which provides rotational resistance through a cog 54 which is also engaged with the gear 50.

Fig. 14 shows the lever 6 in a lowered position in which the mechanism 11 is in a corresponding compacting position. The spring 48 is shown in an extended state whereby the return means 47 biases the lever 6 back to the original position under the force of the spring. The damper 53 is configured to balance the spring force when the lever 6 is lowered and the mechanism 11 is in the compacting position, and to slow the return of the mechanism 11.

Fig. 15 provides a clearer illustration of the compaction force control assembly 15 and the sensor 20. Mechanism 11 is also shown in a raised position with hammer 14 supported by second member 37 in a raised rest position via coupling 32. The second member 37 is attached by a limited movement connection 44 to effect a hinged movement relative to the first member 36, the limited movement connection being formed by a pivot 55 slidably received in a slot 56 formed at an end 57 of the first member 36. The sensor assembly 20 is secured to the first member 36 and is connected to the second member 37 by a connection assembly 58 in the form of a cross bar. The connecting rod 19 passes through a sensor 20 integrated into the PCB 59 so that the relative position of the connecting rod 19, and hence the hammer 14, can be determined.

The sensor 20 is preferably a linear position/displacement sensor (also referred to as a VR sensor), although any other suitable form of linear position sensor may be used. Feedback from the sensor allows the height of the hammer 14 to be determined when the mechanism 11 is extended to the compacting position at the end of the downward stroke, which in turn reveals the depth of compaction (i.e. the height of the coffee pad). The rotational position sensor 51 may also be used to provide information about the linear extension of the mechanism 11, as the measured rotational position of the shaft 12 is directly related to the extent of the mechanism 11. This information may be provided to the user to understand where hammer 14 is located during and/or after compaction. The depth of compaction will vary depending on the dose of coffee powder to be compacted. In an overdose condition, when the connector 30 is fully extended, the extension of the mechanism 11 will decrease, resulting in a decrease in compaction depth (i.e. an increase in cake height), while in an underdose condition the mechanism 11 will extend further, resulting in an increase in compaction depth (i.e. a decrease in cake height). More specifically, in the event of an excess condition, as the hammer travel distance decreases, the extension of the mechanism 11, and thus the compression of the biasing element 7, is also reduced, as detected by the sensor assembly 20 (via the connecting rod 19).

Fig. 15 also shows the lever 6 in the raised position. The lever 6 is connected to the shaft 12 by a tooth clutch 60 which allows free rotational movement of the lever 6 from the home position to the raised position. This means that the shaft 12 is held in the neutral position while the hub 61 of the lever 6 is rotated counter-clockwise as shown until the projection 62 engages with the grinder activation switch 63 which is used to activate the grinder 10 shown in figure 14.

After activating grinder 10, lever 6 may be rotated back or biased toward the home position to move projection 62 out of engagement with switch 63, as shown in fig. 16, ready to depress lever 6 to lower mechanism 11 into the compacting position.

Example 2

Fig. 17 shows a further compacting unit 2 with a compacting mechanism 11 and a compacting force control assembly 15, similar to the compacting unit described with reference to fig. 1 to 16.

The mechanism 11 comprises a hinged connection 30 to the shaft 12, the lever 6 being in the home position and the mechanism 11 being in the raised position holding the hammer 14 away from the grinding chute 21. The compaction force control assembly 15 includes a compression spring 64 mounted on a post 65 that is attached to a fixed structure 66 of the compaction unit 2. The spring 64 acts between an end washer 67 and a bracket 68 that supports the shaft 12.

The shaft 12 is coupled to the lever 6 by a U-shaped section 69 that allows the rotational movement of the lever 6 to be transferred to the terminal extension 70 of the shaft 12 while providing clearance for the spring 64 of the compaction force control assembly 15 that is located within the U-shaped section 69.

The tip extension 70 is coupled to a limited motion connector 71 that includes a rocker 72 that rotates about a pivot 73 that is connected to the fixed structure 66. One end 74 of the rocker 72 is rotatably mounted to the extension 70 and the other end 75 of the rocker 72 is provided with an elongated opening 76 that receives a follower 77. The follower 77 slides up and down along a vertical channel 78 provided in a bracket 79 that is also secured to the structure 66. As shown, the follower 77 is at the upper end 80 of the channel 78 when the lever 6 is in the home position.

Fig. 17 also shows that the lever 6 is connected to the hub 61 of the shaft 12 by means of a clutch 60 which allows the lever 6 to rotate freely in an upward direction without rotating the shaft 12.

Fig. 18 shows the lever 6 in a lowered position in which the mechanism 11 has been lowered and compaction pressure has been applied. When lever 6 is depressed, the reaction pressure on hammer 14 is transmitted back through mechanism 11, which causes shaft 12 and bracket 68 to rise relative to fixed structure 66 against the bias of spring 64. As a result, the end 74 of the rocker 72 is raised, which causes the rocker 72 to rotate and send the follower 77 to the lower end 81 of the channel 78 to provide an end-of-travel stop for limiting any further raising of the carriage 68 so that a constant spring load of the compaction force control assembly 15 is maintained for the compaction operation.

Referring now to fig. 19, lever 6 is shown in an original position in which mechanism 11 is raised and hammer 14 is in an idle position. In fig. 20, the lever 6 is depressed, which extends the link 30 of the mechanism 11 to an intermediate state. In this state, the hammer 14 has moved from the rotational rest position along the guide structure 34, which guides the coupling 32 and the pivot 82 of the hammer 14 so that the compacting surface 25 is oriented in a horizontal direction, in a position above a dose of coffee 83 in the bowl 42 held by the handle 40.

Further rotation of the lever 6 causes the mechanism 11 to move to a compacting position in which the connector 30 is extended, as shown in figure 21, and the compacting force control assembly 15 forces the face 25 of the hammer 14 into the coffee 83 to form a compact 84. The relative rotation of the shaft 12 and the degree of compression of the tensioning assembly 15 may be used to determine the depth of compaction. After compaction, the compacting mechanism 11 returns to the rest position shown in fig. 19, so that another dosing operation can be performed.

Example 3

Referring now to fig. 22, another example of a compacting mechanism 11 is shown and like reference numerals are also used to designate like components to the embodiments described above.

The mechanism of fig. 22 includes a link 30 formed by a rack 85 with a fixed arm 86. The rack 85 is in a vertical orientation and includes vertical legs 87 engaged by a cross beam 88. Each leg 87 has gear teeth 89 that mesh with a pinion 90 to drive the rack 85 up and down. A slot 91 is provided in each leg 87 to receive a roller 92. Beams 93 connect the bases 94 of each leg 87 and support a respective one of the arms 86 of the connector 30 at a fixed angle.

The lever 6 is shown in an original position in which the link 30 is raised and the roller 92 is at the lower end 95 of the slot 91.

Fig. 23 shows the shaft 12, the rotational position sensor 51 and the damper 53 mounted in the fixed structure 66. Pinion 90 is connected to shaft 12, which in turn is attached to lever 6.

Fig. 24 shows the lever 6 in a lowered position, associated with the mechanism 11 in a compacting position in which the roller 92 is located at the top 96 of the slot 91 of the rack 85. The hammer has a pivot 82 which projects in a lateral direction into the guide structure 34 in the form of a slot 35. The slot 35 is formed in the housing 33 and has a vertical portion 97 and a curved top 98. Additionally or alternatively, the coupler 32 also protrudes in a lateral direction for guided engagement with the guide structure 34.

Hammer 14 has the same pivot 82 on the other side which is received in a mating slot 35 in housing 33 on the opposite side of hammer 14.

The pivot 82 follows the path of the slot 33 and additionally or alternatively, the coupler 32 follows the path of the slot 33 as the mechanism 11 is raised and lowered, such that the hammer 14 rotates back to the inclined orientation as the pivot 82 moves past the curved top 98 of the slot 33, and returns to the position shown in fig. 25 as the mechanism 11 is raised and the lever 6 returns to the rest position.

Referring to fig. 26, with the hammer 14 in the rest position, the face 25 of the hammer 14 and the mechanism 11 are rotated away from the lower end 43 of the grinding chute 21, which means that the coffee grounds may be centrally delivered for compaction by the compaction chute 23 without interference from the hammer 14.

Fig. 26 also shows a roller 92 at the lower end 95 of slot 91, which acts to prevent further lifting of rack 85.

The rotational coupling 32 connects the distal end 99 of the arm 86 to one side of the hammer 14 such that as the hammer 14 is raised along the guide slot 25, the hammer 14 rotates about the arm 86, thereby tilting the face 25 of the hammer 14 away from the end 43 of the chute 21. The other arm 86 is connected in the same manner as shown in fig. 27.

Fig. 28 shows the relative positions of the face 25 of the hammer 14 and the grinding chute 21 more clearly. With the lever 6 in the home position, the hammer 14 rotates up against the shaft 12 and out of the end 43 of the chute 21.

In fig. 29, the mechanism 11 has been lowered and the hammer 14 is extended from the compaction chute 23, again in a compaction position in which the coupler 32 is aligned with the vertical portion 97 of the slot 25 such that the hammer 14 is in a vertical state and the face 25 of the hammer 14 is horizontal.

Fig. 30 shows the lever 6 and the hammer 14 in an intermediate position in which the hammer 14 is partly rotated below the grinding chute 21 about the coupling 32 and the pivot 82, which moves along the slot 25 between the rest position and the compacting position.

Fig. 31 shows a return means 47 in the form of an extension spring 48 connected between a fixed mount 49 and a control gear 50 which is fixed for rotation in cooperation with the shaft 12. The rotational position sensor 51 detects the rotational position of the shaft 12 through the cog 52 engaged with the gear 50. The sensor 51 is preferably a potentiometer or POT sensor. The compaction mechanism 11 is in a raised state and the output signal of the sensor 51 is used to monitor the depth of compaction based on the relative rotation of the shaft 12 when the mechanism is lowered to the compaction position. Likewise, the sensor 51 may be placed in an alternative location to monitor, for example, rotation of the gear 50, the shaft 12, the damper 53, or the lever 6.

In fig. 31, the lever 6 is raised so that the projection 62 engages with the grinder activation switch 63, which is more clearly shown in fig. 32.

Fig. 32 also shows that the projection 62 is integrally formed with a ring gear segment 100 that is fixed to the lever 6. When the lever 6 is raised from the home position, the gear segment 100 is out of driving engagement with the shaft 12, which allows the lever 6 to be independently raised to engage with the grinder activation switch 63. In this regard, the gear segment acts as a clutch 60 between the lever 6 and the shaft 12.

Fig. 33 shows the lever 6 in a lowered position away from the switch 63. Gear segment 100 is reengaged with shaft 12 by intermediate gear 101, which is keyed to shaft 12, such that downward movement of lever 6 after passing through the home position causes corresponding rotation of shaft 12 and activation of the compacting mechanism.

Fig. 34 shows the spring 48 in an extended state when the mechanism 11 is in the compacted position. In this state, the spring 48 of the return means 47 pushes the mechanism 11 back to the raised position. Damper 53 engages at the end of the downward travel of mechanism 11 to resist return device 47 and slow down movement of mechanism 11 near the compacting position. However, the primary purpose of damper 53 is to slow the return of mechanism 11 from the compacting position to the raised position.

As mentioned above, the rotation sensor 51 may be used to monitor the extension of the mechanism 11 and the resulting compaction position in order to determine the compaction depth. However, the compaction position and compaction depth may also be measured using a sensor 20 that monitors the vertical height of the rack 85 to provide a direct VR or linear distance reading.

For the sake of completeness, fig. 36 shows a gear segment 100 attached to the lever 6, while fig. 37 shows an intermediate gear 101, which engages with the gear 100 in order to drive the compacting mechanism 11 to move the hammer 14 between the rest position and the compacting position. The arc length of the gear 100 is limited so that the lever 6 can only drive the corresponding intermediate gear 101 when it is moved between the rest position and the lowered position. If the lever is moved upwards from the home position, gears 100 and 101 will disengage from the driving engagement, which allows the lever 6 free rotational movement to start grinding, while maintaining the mechanism 11 in the raised position during the grinding operation.

Example 4

Fig. 38 shows another example of the compacting mechanism 11 of the compacting unit 2, and the same components as those of the above example will be denoted by the same reference numerals.

The mechanism 11 is shown in a lowered compacting position in which the hammer 14 is within the bowl 42 of the handle 40. The mechanism 11 comprises a connection 30 in the form of an arm 86 connected to a rod 102 of an actuator 13 in the form of a linear drive shaft 103 which moves up and down through a support 104.

Fig. 39 shows the mechanism 11 in an intermediate position in which the shaft 103 has been operated to raise the link 30 and at the same time pivot the hammer 14 about the rotational coupling 32. Hammer 14 is connected to arm 86 by a rotational coupling on either side of hammer 14, with arm 86 itself bridging chute 21, so as to avoid any interference between arm 86 and chute 21 as the shaft moves mechanism 11 between the raised and lowered positions.

In fig. 40, the mechanism 11 is in a raised position in which the shaft 103 has been raised and the hammer 14 is rotated out of the chute 21. In this position, coffee can be centrally dispensed in the compacting chute 23 via the centrally located chute 21 and directly into the bowl 42 of the handle 40 without any obstruction. More importantly, chute 23 is centrally located with respect to handle 40 so that the coffee grounds are centrally delivered to bowl 42.

Fig. 41 is a perspective view of the mechanism 11 in a lowered position. A second connection 105 is provided, hinged to the fixed structure 66 in the vicinity of the compaction chute 23 of the compaction unit 2. Links 30, 105 work cooperatively to move hammer 14 between the compacting position shown and the raised position shown in fig. 42.

More specifically, second link 105 is connected to hammer 14 by pivot 82, and link 30 is connected to hammer 14 by rotational coupling 32 between compacting surface 25 and pivot 82 to allow hammer 14 to pivot between different tilt orientations as link 30 moves in a linear direction relative to hinged second link 105.

The linear upward movement of the drive shaft 103 causes the hammer to lift and rotate away from the lower end 43 of the grinding chute 21, while the linear downward movement of the shaft 103 causes the hammer to rotate back to the compacting position shown in fig. 41.

Fig. 42 also more clearly shows that hammer 14 has a body 106 and two sides 107 carrying respective pivots 82 and rotational couplings 32. The side portions 107 project away from the body 106 to define a space 108 therebetween that provides clearance around the grinding chute 21 during rotation of the hammer 14.

Example 5

Fig. 43 shows another example of the compacting mechanism 11, and like parts will be denoted with like reference numerals as used above.

The mechanism 11 is shown to include a link 30 in the form of a rack 85 driven by a pinion 90 attached to the drive shaft 12. Rack 85 is connected to hammer 14 by arm 86 and rotational coupling 32 such that hammer 14 moves up and down in a linear fashion indicated by the directional arrow as rack 85 is raised and lowered by rotation of shaft 12.

The shaft 12 is operated by the lever 6 through the clutch 60. The clutch 60 includes an annular groove 109 which receives a pin 110 extending from the fixed structure 66 to allow limited rotational movement of the clutch in cooperation with the lever 6.

It will be appreciated that the clutch 60 may be used in connection with other examples of the machine 1 described above.

The relative positions of the lever 6 and the compacting mechanism 21 may be monitored by one or more different sensors, as desired. Fig. 43a shows the positions of a linear sensor 184 and a time of flight (ToF) sensor 185 arranged to monitor the linear movement of the rack 85. The time-of-flight sensor calculates the distance between the two points. In this case, the upper sensor 185 will be in a fixed position. As an alternative to the upper sensor 185, the lower sensor 184 would be attached to the rack 85 so that the linear movement of the arm 86 could be measured.

Alternatively, a rotation sensor 51 may be used in the position shown in fig. 43b to measure the relative rotation of the pinion 90. As a further alternative, the rotation sensor 186 may be positioned to directly monitor the rotation of the lever 6.

Fig. 43c shows yet another option of a rotation sensor 51 mounted to the end of the shaft 12, while fig. 43d shows another option of a rotation sensor 51 directly engaged with a rack 85.

Fig. 44 shows the lever 6 in the home position and the mechanism 11 at the top of the stroke, such that the rack 85 is raised and the hammer 14 is in the rest position above and away from the grinding chute 21.

When lever 6 is depressed, mechanism 11 lowers hammer 14 through the neutral position shown in fig. 45.

At the end of the stroke, rack 85 is in the lowered position and hammer 14 is in the compacting position as shown in fig. 46.

Turning to fig. 47 and 48, clutch 60 is described in more detail. The clutch 60 includes a first disc 112, an annular groove 109, a connecting member 113, and a biasing element 114. Preferably, the first connecting member 113 is located radially outside the element 114. Preferably, the biasing element 114 is a rectangular boss. Preferably, the connection member 113 is a cylindrical protrusion.

The second disc 115 is attached to the lever 6 and comprises a connection recess 116 for receiving the connection member 113 of the first disc 112 to inhibit relative rotation between the first and second discs 115. The second disc 115 further comprises a biasing element 117. Preferably, the biasing element 117 is similar to the biasing protrusion 114, but faces in the opposite direction.

The clutch 60 also includes a clutch disc 118 having a central shaft that receives a clamp 119 and a radial array of annular grooves 120. The connecting member 113 passes through an annular groove 120 having an annular dimension sufficient to allow limited movement between the clutch plate 118 and the first disc 112, for example, such that the lifting lever 6 is not translated into any movement of the clutch plate 118.

The clutch disc 118 further comprises two annular openings 121 for receiving the biasing elements 114 and 117 of the first and second clutch discs 112 and 115, such that the first and second clutch discs 112 and 115 can drive the clutch disc 118 under pretensioned bias and transmit torque from the lever 6. Thus, the discs 112 and 115 are coupled with the biasing elements 114 and 117 to form the compaction force control assembly 15 to apply the biasing force during the compaction operation.

As can be appreciated from the foregoing, an aspect of the invention is a machine 1, which in a broad sense is a machine for delivering coffee powder to a handle, comprising: a grinder for grinding coffee powder into the handle; a compacting mechanism for compacting coffee powder in a handle along a path, the compacting mechanism comprising: a hammer comprising a surface for compacting coffee powder; and a connector connected to the hammer, wherein during a first portion of the path the connector orients the surface in a first direction and during a second portion of the path the connector orients the surface in a second direction, wherein the first and second directions are different.

The invention also provides a machine for delivering coffee powder to a handle, the machine comprising: a grinder for grinding coffee powder into the handle; a compacting mechanism for compacting coffee powder in a handle along a path, the compacting mechanism comprising: a hammer comprising a surface for compacting coffee powder; a compaction actuator for moving the surface along the path, wherein during a first portion of the path the surface is oriented in a first direction and during a second portion of the path the surface is oriented in a second direction, wherein the first direction and the second direction are different.

The compaction mechanism moves the hammer through the first and second portions of the path between a rest position in which the surface is oriented in the first direction and a compaction position in which the surface is oriented in the second direction for performing a compaction operation. In all the above examples, the connection is arranged to press the face of the hammer in an axial direction with respect to the handle during the compacting operation and to return the hammer to the rest position in a non-axial path with respect to the bowl held in the handle between compacting operations, so that the hammer does not interfere with delivering coffee into the chute when in the rest position.

During the compacting operation, the compacting mechanism rotates the hammer between the first and second portions of the path such that the compacting surface faces in the second direction to compact the coffee grounds. In the above example, the connection returns the hammer to the rest position along a non-axial path relative to the handle between compaction operations, such that the hammer does not interfere with delivering coffee into the handle when in the rest position.

The hammer rotates in the rest position relative to the compacting position such that the compacting surface is oriented in a first direction that is offset from the second direction by an angle, whereby the hammer does not interfere with the delivery of coffee powder from the grinder into the handle.

Example of hammer

Turning now to fig. 49, hammer 14 is depicted and like components to those described above will be designated with like reference numerals.

The ram has a base 27, a body 28, and a coupler 29 for connection to the connector 30 described above. The coupler 29 includes a support structure 122 extending upwardly from the body 28. Transverse pin 123 provides rotational coupling 32 for hammer 14. A second pin 123 extends from the other side of the support structure 122 to provide a second rotational coupling 32.

Guide pivot 82 extends laterally of hammer 14 in line with, but vertically spaced from, the associated coupling 32. The guide pivot 82 extends laterally a greater distance from the support structure 122 than the coupling 32.

The support structure 122 is in the form of two spaced apart support members 124 that define the interstitial space 108 therebetween.

Fig. 50 is a cross-sectional view of hammer 14, showing rotation mechanism 125 converting axial force into rotational motion of base 27.

The base 27 has a collar 126 that slides up and down along a cylinder 127 that is secured to the body 28 by a set screw 128. The biasing element 129 is located between the body 28 and the base 27. The biasing element 129 is preferably in the form of a spring 130 that is located on the collar 126 and is connected between the base 27 and the body 28.

The rotation mechanism 125 includes a cam structure 131 that generates rotational movement of the base 27 as the base 27 moves axially or telescopically relative to the body 28. The cam structure 27 is in the form of a series or ramp 132 and corresponding projection 133.

The base 27 also includes a side wall 134 that slides up and down along an outer wall 135 of the body 28, and the body 28 has a locating flange 136 for supporting a seal 137 that forms a seal with the side wall 133 during relative axial movement. The flange 135 also carries a retaining ring 138 for holding the seal 137 in place.

The base 27 includes a circular slot 139 in the side wall 134 for receiving an attachment skirt 140 that supports the compacting surface 25 on the underside of the base 27.

Hammer 14 is shown in an expanded state. As can be appreciated, during the compaction operation, when an axial load is applied to the hammer 14, the hammer 14 compresses as the base 27 moves toward the body 28. During this axial movement, the ramp 132 and the projection 133 engage and slide along each other, resulting in rotation of the base 27.

After the compaction operation, the axial load is removed and the spring 130 pushes the seat 27 away from the body 28, which causes the camming action to be reversed. When the hammer 14 returns to the expanded state, this causes the base 27 to counter-rotate as the ramp 132 and the projection 133 are reversed to the original orientation.

The rotational movement of the base 27 helps to "polish" the compact during compaction and provides a more uniform distribution of coffee grounds. At the same time, any coffee grounds that may adhere to compacting surface 25 may be released, which may aid in cleaning hammer 14, which may be beneficial because the accumulated coffee grounds on hammer 14 may otherwise form a desired cake.

The relative rotation of the base 27 of the hammer 14 in both directions during and after formation of the compact serves to self-clean the hammer 14 and to clear the face 25 of the hammer 14 of coffee grounds, as the hammer base 27 rotates relative to the body 28 during compaction and, in turn, rotates relative to the body when the axial load on the hammer 14 is removed after the compaction operation.

Turning now to fig. 51, the cam structure 131 in the body 28 is more clearly shown as radially disposed ramps 132 that engage corresponding protrusions 133 formed in the base 27, as shown in fig. 52.

Fig. 51 and 52 also show that the pivot 82 is formed by a collar 141 that is fitted onto a shaft 142 integrally formed with the support member 124. The coupling 32 is formed by a shaft 143 which is inserted into an opening 144 and held in place by circlip 145. The shaft carries a hoop 146.

Hammer 14 is shown with only a single spring 130 for biasing base 27 away from body 28, however, additional springs or alternative biasing means may be used as desired.

Hammer 14 of fig. 51 and 52 is also shown with a seal 137, which is preferably made of felt to prevent coffee from entering hammer 14, but any other suitable seal may alternatively be used in place of felt seal 137 as desired.

Fig. 53 and 54 illustrate an alternative hammer 14, wherein like features are designated with like reference numerals. The rotation mechanism 125 also includes a series of ramps 132 on the underside of the body 28 and mating protrusions 133 in the base 27. The felt seal of fig. 51 and 52 is replaced by a rubber seal 147 having an inner ring 148 fitted within a base cap 149 and an annular shoulder 150 arranged to slide up and down along the periphery of the outer wall 135 of the body 28. The base cover 149 defines a compacting surface 25.

Fig. 55 shows that the seal 137 is in the form of a wiper mounted in an annular groove 151 in the base 27. The seal 137 is preferably formed from rubber such that the seal 137 provides a rubber wiper blade 152 that is more durable than many other alternatives.

As shown in fig. 56, the wiper blade 152 is resiliently pressed against the outer wall 135 of the main body 28. Body 28 is preferably formed of plastic and the connection of wiper 152 and wall 135 is a point contact that reduces friction while ensuring a tight seal when hammer 14 is compressed and depressurized during and after a compaction operation. The body 28 is also preferably formed of a relatively high density plastic so that there is minimal friction between the blade 152 and the body 28.

The hammer 14 shown in any one of fig. 49-56 preferably also includes a vent for equalizing the pressure inside the hammer during compression of the hammer. The vent holes are preferably located near the top region of the body 28 where access to the coffee grounds is unlikely to occur. For example, it may be located on the support structure 124 or the item 108.

Fig. 83-90 relate to another example of hammer 14, where appropriate, like reference numerals being used to designate like components. It should be noted that any of the various forms of hammer 14 described above may be used as a manual hammer independent of machine 1 described above.

As shown in fig. 83, hammer 14 has a body 28 with a central axis 217. Hammer 14 also has a compacting surface 25 for compressing ground coffee in handle 40. Hammer 14 also has a connection assembly 218 that is located between body 28 and compacting surface 25 and connects body 28 to compacting surface 25 such that pressure can be applied to compacting surface 25 through body 28 and connection assembly 218. During compaction, the coffee grounds tend to adhere to the compacting surface 25 and accumulate over time if the user does not clean it. This problem is more likely to occur with built-in compacting mechanisms because compacting surface 25 is not as accessible as a conventional hammer. The rotary hammer 14 can reduce the amount of accumulation on the compacting surface 25. To further enhance the effectiveness of rotary hammer 14, a non-stick surface or material on compacting surface 25 may be used in conjunction with rotary hammer 14. The non-stick surface or material may also be used as an alternative to the rotary hammer 14.

As can be better seen in fig. 84, the connection assembly 218 includes a first inclined surface 219 disposed about a central axis 217. Preferably, the first inclined surface 219 includes a plurality of inclined surfaces. As shown in the cross-sectional view of fig. 86, the connection assembly 218 further includes a cam 220 adapted to abut the first sloped surface 219. Preferably, the cam 220 is a second inclined surface 221 disposed about the central axis 217. The connection assembly 218 further includes a hammer biasing member 222 connected between the compacting surface 25 and the body 28 such that when the distance between the compacting surface 25 and the body 28 decreases, the hammer biasing member 222 applies a force to urge the compacting surface 25 and the body 28 away from each other.

As shown in fig. 86 and 89, as compressive force is applied to compacting surface 25 and body 28 is held stationary, compacting surface 25 moves (preferably translates) from the rest position shown in fig. 86 toward body 28 to the compacting position shown in fig. 88, compressing hammer biasing member 222. As the compaction face 25 and the body 28 move toward each other, the cam 220 abuts the first inclined surface 219, which abutment results in a normal force being exerted on the cam 220 from the inclined surface 219 and thereby causes the cam 220 and the compaction face 25 to pivot about the central axis 217 relative to the body 28. When the compressive force applied to the compacting surface 25 is removed, the compacting surface 25 is urged away from the body 28 by the hammer biasing member 222. As the compacting surface 25 and the body 28 move away from each other, the cam 220 is similarly urged against the first inclined surface 219, and as the distance between the compacting surface 25 and the body 28 increases, the cam 220 allows the compacting surface 25 to pivot back to the rest position about the central axis 217, thereby moving the compacting surface 25 relative to the ground coffee in the handle. Preferably, the rotation of the compacting surface 25 relative to the body 28 is about 5 degrees for a distance between the compacting surface 25 and the body 28 of about 3 mm.

Preferably, the hammer biasing member 222 has a pretension for urging the compacting surface 25 toward the rest position. More preferably, the hammer biasing member 222 also has a pretension for urging the compacting surface 25 toward the rest position in both axial translation relative to the body 28 and rotation relative to the body 28.

As shown in fig. 84, the first inclined surface 219 is preferably a helical spline. Referring to fig. 86, the connection assembly 218 may further include a stop member 223 adapted to prevent the cam 220 from moving along the first sloped surface 219 to a position beyond the stop member 223.

In a preferred embodiment, the hammer 14 is sealed. An indicator 224 (shown in fig. 83) is provided that depicts the rotation of the compacting surface. In another preferred embodiment, the compacting surface 25 is removably attached to the attachment assembly 218, such as by a tab 225 (shown in fig. 84).

Referring now to fig. 89A and 89B, another embodiment of hammer 14 is shown. Hammer 14 is substantially similar to hammer 14 of fig. 88-88, however, hammer 14 of fig. 89 is suitable for use in machine 1 disclosed herein, or in another type of coffee powder compaction assembly involving a hammer. Hammer 14 of fig. 89 includes a circular pin 226 for guiding movement of hammer 14 relative to the pivot as disclosed herein. As shown in fig. 90, hammer 14 may be used in machine 1.

Double-track quantitative feeding unit

In fig. 57, a dosing unit 2 is shown, wherein the same parts mentioned above are indicated with the same reference numerals.

In fig. 57, hammer 14 is shown in an idle position prior to compaction. The guide structure 34 is double-tracked _[DH3][SW4] 153. 154 are provided in the housing 33 to guide the respective couplings 32 and pivots 82 of the hammer as the mechanism 11 is raised and lowered.

As described above with reference to fig. 49 and 50, the pivot shaft 82 protrudes to the outside of the hammer 14 by a larger distance than the lower coupling 32, so that the upper pivot shaft 82 can be guided by the rail 154 while the rail 153 serves to guide the lower coupling 32. Due to the geometry (e.g., depth and/or width) of the rails 153, 154 and pivot 82 and the coupling 32, the pivot and coupling may be independently guided by the dual rails. The geometry of the coupler 32 matches the geometry of the track 153 and likewise the geometry of the pivot 82 matches the geometry of the track 154. For example, the width of the tracks 153, 154 matches the diameter of the coupler 32 and the pivot 82, respectively.

By independently guiding the pivot 82 and the coupling 32, it is easy to rotate the hammer 14 into and out of the rest position without following the wrong path (e.g., otherwise the hammer 14 might rotate in the opposite direction, thereby blocking the grinding chute).

Fig. 58 shows that the rails 153, 154 are aligned and parallel along the lower portion 155 and diverge at the respective upper portions 156, 157. The pivot 82 is located in an upper portion 157 of the track 154 and the coupler 32 is located in a corresponding upper portion 156 of the outer track 153. With the roller positioned in this manner, the mechanism 11 is in the raised position and the hammer 14 rotates such that the face 25 is tilted to a nearly vertical orientation, thereby leaving a gap for the grinding chute 21.

Fig. 59 shows the relative positions of the coupler 32 and the pivot 82 in the upper portions 156, 157 of their respective tracks 153, 154. The upper portions 156, 157 of the rails 153, 154 are bent away from each other in a horizontal direction such that the coupling 32 and the pivot 82 adopt a nearly horizontal orientation, thereby leaving a gap for the grinding chute 21.

For compaction, the coupling 32 is guided out of the upper portion 156 of the rail 153 and downwardly to the vertically oriented lower portion 155 of the rail 153. While the pivot 82 is guided out of the upper portion 157 of the track 154 and then down to the vertical portion 155 of the track 154.

Fig. 60 shows the mechanism 11 extended and the coupler 32 and pivot 82 oriented vertically in their respective tracks 153, 154.

In this position, hammer 14 is ready for compaction. The centre line 158 of the mechanism 11 passing through the centre of the shaft 12 and the coupling 32 is offset from the vertical indicated by the vertical line 159 by an angle which helps to tilt the face 25 of the hammer 14 further in the vertical direction when the hammer is raised to the rest position, which in turn provides an improved clearance so that the hammer 14 does not impede the flow of coffee grounds during a dosing operation.

The use of dual tracks 153, 154 provides the benefit that each pivot point of the hammer 14 can be independently controlled to achieve smooth movement and rapid rotation when the mechanism is at the top of the stroke, thereby rapidly moving the hammer 14 into the rest position during the dosing operation and avoiding interference with the flow of coffee.

Fig. 61 more clearly shows the rails 153, 154 formed in the housing 33. Fig. 61 shows yet another example of a return means 47 in the form of a torsion spring 160 mounted at the end of the shaft 12. After the compacting operation, the spring 160 is biased to return the lever 6 to the original position.

The sensor 51 is used to detect relative rotation and position of the shaft 12 during a compaction operation. The sensor 51 monitors rotation of the shaft by means of cogs 52 which mesh with a control gear 50 attached to the shaft 12. The gear 50 has teeth 161 on only a limited segment 162.

A damper 53 is provided below the sensor 50 as shown in fig. 62. Damper 53 is in the form of a cog 54 which meshes with teeth 161 of gear 50 and resists rotational movement of gear 50. With the lever 6 of fig. 61 in the home position, the damper 53 is disengaged from the control gear 50, since the teeth 161 are provided only on a limited segment 162 of the gear 50. Pressing down on the lever 6 will result in a rotation of the gear 50 and a final connection of the tooth 161 with the damper 53. Thus, when the lever 6 is in the lowered position, the action of the damper 53 on the gear 50 can be limited to the end stroke of the lever 6. When the lever is in the up position, no teeth on the gear are engaged. Thus, the damper is not engaged and only affects rotation in a lower range of motion, which in turn reduces the strength (i.e., size) of the return device 47, as the return device 47 need not overcome the damper 53 at its lowest deflection (i.e., highest mechanical load). The reduced size of the return means 47 reduces the return speed of the compacting mechanism 11, which helps to reduce mess. In addition, by reducing the size of the return device 47, the compaction force can be reduced as needed.

The damper 53 is used to momentarily reduce the speed of the compacting mechanism before and after the compacting operation. This may help to reduce mess due to the hammer impacting the coffee powder at high speed when approaching or high release from the pad after the compaction operation, which may result in loosening of the pad in the handle, causing poor extraction of coffee.

Handle support

The following is a description of the handle holder 7, and the same components as those described above will be denoted by the same reference numerals.

Referring now to fig. 63, the handle 40 has a grip 163 attached to a cup portion 164 of the handle 40. Around the cup-shaped portion 14, a positioning tab 165 is disposed adjacent the upper peripheral edge 165.

The handle bracket 7 includes an access opening 167 and an abutment 168 defined by a top support surface 169 and a bottom support surface 170 that securely grasp and retain the tab 165 when the handle 40 is in the illustrated, abutment position.

Inclined surfaces 171 are provided on either side of the opening 167 to guide the tab 165 into the docking station 168 and retaining members 172 are also provided to resiliently retain the handle 40 in the docked position. The retaining member 172 is formed of two biasing elements 173, preferably in the form of spring clips 174, although any other suitable clamping device may be employed as desired.

To load the handle 40 into the handle support 7, the handle 40 is first introduced into the opening 167 such that the tab 165 engages the ramp 171. This helps center and align the handle 40. The handle 40 is then pushed against the biasing element 173 using the knob 163, which is separated to allow insertion of the handle 40, after which the spring clip 174 is closed against the handle 40 to bias the handle 40 to the docked position.

Fig. 64 is a cross-sectional view taken along line G-G of fig. 63, with the handle 40 omitted for clarity. The upper support surface 169 slopes slightly downwardly from the horizontal line 175 from the opening 167 to the end wall 176 of the docking station to accommodate the tilting action of gravity on the handle 40 during insertion and/or compaction to provide fore-aft leveling of the handle to ensure that the coffee pad is leveled during compaction. A microswitch or the like (not shown) may be positioned in or adjacent to the wall 176 to detect when the handle 40 is loaded into the handle support 7.

Fig. 64 also shows the forward bevel 171 of the retaining member 172 positioned adjacent the opening 167 to ensure that the tab 165 of the handle 40 is lifted into the docking station 168 without interference from the retaining member 172.

Conventional bayonet-type handles have vertically offset tabs and the lower support surface 170 opens into a support surface 171a (shown in fig. 64 a) which is correspondingly biased in a vertical direction to ensure that the handle remains horizontal when loaded into the docking station, thereby levelling the compact during compaction.

Turning now to fig. 65, the handle holder 7 has an opening 177 for receiving coffee grounds and a recess 178 on the underside 179 for the retaining member 172. The retaining member 172 has a generally U-shaped body 180 with a curved interior profile 181 to match the exterior shape of the cup-shaped portion 164 of the handle 40. The body 180 is inserted into the recess 178 with the biasing member 173 projecting forwardly into the opening 167. The locating tangs 182 on the body 180 ensure that the retaining member 172 is properly oriented and located prior to securing the retaining member 172 to the underside 179 of the handle bracket 7 using fasteners 183.

Fig. 66 shows an underside view of the handle 40 inserted in the handle holder 7. The spring clips 174 of the retaining members 172 are clearly seen to hold the handle 40 in the docked position ready for compaction.

As can be appreciated, the handle 40 can be reliably positioned and held in the handle holder 7 by a single insertion action, and there is no need to raise and rotate the handle 40 as is typically required with bayonet-type handles. This helps to simplify use and reduce the overall design height of the handle support.

Fig. 78 to 82 relate to the bracket 7, wherein the same components as those described above will be denoted by the same reference numerals.

As shown in fig. 78, the bracket 7 includes a support surface 170 for supporting the positioning tab 165 of the handle 40. As better seen in the cross-sectional view of fig. 80, the bracket 7 further comprises a rear wall 176, the shape of which conforms to the shape of the at least one cup-shaped portion 14 of the body 180 of the handle 40. The rear wall 176 is positioned such that a center 210 of the filter bowl 211 is aligned with a central axis 212 of the compaction chute 23 when the handle 40 is against the rear wall 176. As shown in fig. 82, the bracket 7 further includes a retaining member 172 for pushing the body 180 of the handle 40 against the rear wall 176. The central chute axis 212 is preferably perpendicular to the bowl bottom surface 214 and extends through the center 214 of the bowl bottom surface 214.

The retaining member 172 preferably urges the body 180 of the handle 40 by exerting a retaining force on the handle 40. The holding force is preferably parallel to the support surface 170. Further, the rear wall 176 preferably includes a handle detection switch 215 (shown in fig. 82) for cooperating with the handle 40 to provide a handle signal indicative of whether the handle 40 is present in the cradle 7.

The retaining member 172 preferably applies a retaining force by elastically deforming from a position that interferes with the position of the handle 40 when the handle 40 abuts the rear wall 176. The tendency of the retaining member 213 to elastically deform back to this position urges the handle 40 against the rear wall 176. In another embodiment, the retaining member 213 comprises a spring (not shown) with pretension to apply the retaining force. Preferably, the bracket 7 comprises two holding members 172 located on opposite sides of the bracket 7 and thus comprises a handle 40 held by the bracket 7. Preferably, the retaining member 172 is located in a plane parallel to the support surface 170 but vertically below the support surface 170.

Coffee grinding system

Fig. 67 is a schematic representation of a system 200 for operating the machine 1 described above.

The system 200 includes a controller 201 and a motor status sensor 202 that provides information regarding the grinder current or motor speed to indicate whether coffee beans are in the hopper and/or are jammed.

The system 200 also includes a grinder module 202 that receives start and stop signals from the controller 201 and provides feedback to the controller 201 when grinding is complete.

A hammer module 203 is also provided for performing the compaction operation and providing compaction position information to the controller.

Finally, the system includes a user interface module 204 to facilitate user operation of the system. The interface module 204 provides operational cues to the user and allows the user to operate the grinder and perform compaction operations.

The system 200 is used to implement one or more of the following dosing algorithms.

Dose algorithm

Using the various examples of the compaction mechanism 11 described above, the compaction position is monitored and the compaction depth may be determined during a compaction operation. The compaction depth information provides feedback for the purpose of determining the proper dose of coffee powder to be delivered into the handle 40. For example, if the position of hammer 14 is too high or too low during a compaction operation, the grinding may be changed to adjust the current and/or next dose accordingly.

Referring to fig. 68, an algorithm flow chart is shown that illustrates some of the method steps that should be taken to determine if any dose adjustments are needed.

Step S101 represents an initial step of activating the grinder to a predetermined grind to produce a predetermined quantity of coffee grounds. _[DH5][SW6] The predetermined amount of coffee grounds may be accomplished by detecting whether the predetermined amount of coffee grounds is delivered using one of a predetermined grinding time or using a weight sensor.

Once the grinder is activated, the coffee beans are ground in the hopper and transferred to the handle through the grinding chute.

In step S103, the hammer position is checked, it is determined that it is in an idle state, after which in step S105 the hammer assembly is moved from the idle position to the compacting position. Compaction pressure is then applied to initially compact the coffee grounds using the hammer to form a cake of coffee grounds in the handle. In step 106, the hammer state is recorded as an initial state, and in step 107, the mechanism is also recorded as being in an extended state.

In step 109, the total compaction depth is determined by comparing the position information when the hammer is in an idle state with the hammer position when the mechanism is in an extended state. Any deviation between the compaction depth and the desired depth may then be determined in step 111.

If the deviation is less than the predetermined tolerance, no action needs to be taken and information indicating the desired depth may be provided to the user interface, as in step 115. However, if the deviation is greater than a predetermined tolerance, information indicating the sign of the deviation may be provided to the user interface, as per step 117. The dose may then be adjusted for the current and/or next use.

With respect to FIG. 69, after step 117, in step 123, the grinding may be changed by varying the degree of deviation based _[SW7] To adjust the dose (as shown in figure 70). The grinding adjustment may be done manually by the user or automatically.

Fig. 70 shows the case that: the deviation indicates an under-dose and a second grind is determined in step 121 to make up the dose prior to extraction. Steps S101 to S111 are then repeated to ensure that the depth of compaction is within a predetermined tolerance.

With respect to the measured compaction depth, this may be determined based on feedback from any suitable measurement sensor. If a rotation sensor and a linear sensor are used, the depth may be provided by:

depth=d=p-x

Wherein:

x＝R·cos0+L·sinφ

and

θ: hammer status signal (preferably the difference between initial and extended hammer status) from a rotation sensor

R: the length of the first member 36 (including the movement of the connecting rod 19 detected by the linear sensor 20)

L: length of the second member 37

P: ideal depth of compaction

In one example, the preferred predetermined desired compaction depth may be 6.75±0.5mm. The depth of compaction may be characterized as under-dosed or over-dosed depending on the amount of ground coffee deposited in the handle. An insufficient dose as shown in fig. 10 may result in a compaction depth of between 7.25mm and 10mm, while an excessive dose as shown in fig. 12 may result in a compaction depth of between 1mm and 6.25 mm. A serious overdose (e.g., compaction depth less than 1 mm) requires removal of the ground coffee before the handle can be used with the machine.

As shown in fig. 69, in step S119, the processor may adjust the grinding of the current and/or subsequent grinding operations based on the deviation (when operating in "automatic mode") or in response to a user input (if "manual" mode is selected). In manual mode, the user may determine grinding by himself with reference to the compaction depth measurements. The processor may not update the polish for further polishing operations.

For a typical dosing operation, the adjustment calculation may be performed in an automatic mode using a linear relationship between the compaction depth and the predetermined volume of compressed coffee compact:

Volume [%]＝c ₁ * Depth of compaction [ mm]+c ₂

In one embodiment, c ₁ And c ₂ The values of (c) are-0.0638 and 1.4326, respectively, where c ₁ And c ₂ May vary based on the geometry of the bowl (e.g., a single dose bowl or a double dose bowl, bowls with different diameters).

Using this relationship, the processor determines how much volume needs to be increased or decreased in the current and/or later coffee pads. The adjustment of the milling may then be achieved by a linear relationship between the volume and the milling time, which may be determined by the processor by dividing the determined volume by the current milling. The current and/or next grinding is then determined as the inverse of the gradient.

The compaction depth calculation for a mechanism with an articulated connection can also be derived by:

forward kinematics and Denavit-Hartenberg (DH) parameters

Deriving a 1-linear approximation

The mechanism 11 can be considered as the construction of a two degree of freedom (DoF) planar manipulator in the x and y coordinate system. The following diagram shows the coordinate system at the different joints. Specifically, [ x ] ₀ ,y ₀ ]、[x ₁ ,y ₁ ]、[x ₂ ，y2]The coordinate system at the joint of the shaft 12, at the joints of the first member 36 and the second member 37, and at the rotational coupling 32 are shown, respectively.

This gives us the following formula for calculating the y-coordinate.

y＝l ₁ sin(q ₁ )+l ₂ sin(q ₁ +q ₂ )---(1)

Knowing that the offset between the end effector and the origin axis is x=c ₁ (this value is negative based on the orientation described above). As a result, we can get q-based ₁ Solving for q at any joint angle ₂ Is defined by the formula:

x＝c ₁ ＝l ₁ cos(q ₁ )+l ₂ cos(q ₁ +q ₂ )---(2)

to derive a single formula for determining the y-coordinate end effector, we can apply q ₂ The formula for substituting y:

in the preferred embodiment, the spring is located on the first member 36, so l ₂ Is a constant value, the only variable being l ₁ And q ₁ . As previously discussed, a sensor 20 is provided comprising a connecting rod 19, and the relative position of this connecting rod 19 can be used to monitor the distance traveled by the hammer (i ₃ )。

It should be noted that if the biasing element 7 is located on the second member 37, l ₂ Will be variable, and l ₁ Will be a constant value. If the biasing element 7 is not in both the first member 36 and the second member 37, l can be eliminated from all equations ₃ (＝0)。

The distance (l) monitored by the sensor 20 ₃ ) And/l ₁ The linear relationship of (c) may be:

this yields the following formula:

alternatively, the relationship of the first member 36 and the distance monitored by the sensor 20 may be non-linear. The relationship may be derived from trigonometry.

Wherein l ₄ Is a constant value, and l ₅ Representing the distance monitored by the sensor 20.

l ₅ ＝a ₁ -l ₃

The two formulas above will yield y and l ₃ Nonlinear relationship between the two.

Simplifying computation

To simplify the calculation we can assume q in the extended state we assume ₁ =90°, q2=0°, which means that we can calculate the compaction height based on the linear sensor 20 using the above formula without the measurement from the rotation sensor.

In this way, y and l can be obtained ₃ Linear relationship between:

y＝c ₂ -l ₃

deriving 2-Denavit-Hartenberg (DH) parameters( An inherently unique alternative derivation. DH is typically used for a robot/robotic arm. It also derives the rotation and point of each link at any position and can also be used to derive force equations )

Using the q ₂ (from equations (1) and (2)), we now have the Denavit-Hartenberg (DH) parameters of the institution. To test these two formulas, l is ₁ 、l ₂ 、q ₁ And q ₂ Is input to a DH calculator to find a transformation matrix from one coordinate system to the next.

Where y is the amount of movement of the first member 36 (or the second member 37 if the biasing element 7 is located in the second member 37).

q: amount of rotation about the z-axis

l: distance in z-axis

b: the length of each common normal (joint offset)

Alpha: angle between two consecutive z-axes (joint torsion)

Dose algorithm coupled with grinder state detection

The dose algorithm is based on two main parts: compaction readings and current grinding. At the user's press, the compacted height is measured and if the compact is not at the desired height, the length of time of the current and/or next grinding is updated accordingly. If the above system 200 detects an underdose, the milling will be increased, and if an excess is detected, the milling will be decreased.

During the grinding cycle, if the coffee beans in the hopper are depleted and/or the grinder is blocked, and the grinder continues to operate until its set time is over, the user will receive an under-dose reading while compacting (otherwise it is assumed that it will be the ideal dose). This results in the algorithm attempting to overcompensate by adding more time to the current and/or next mill. When the user again fills the hopper and attempts to grind, they will receive an excess dose in the current and/or next compaction operation, as the algorithm has attempted to compensate for the under-dosing that should be the ideal dose.

This problem becomes more serious if the dose should be originally excessive but the coffee beans in the hopper are used up and/or the grinder is blocked during the grinding cycle. If the height reading is again under-dosed, the mill will self-renew to a severe overdose.

By using a sensor to detect coffee beans in the hopper and/or any potential grinder blockage, the grinder may be stopped if no coffee beans and/or grinder is blocked. This prevents the grinding from being completed unless coffee beans are present and the grinding of the algorithm is updated accordingly. In this way, at the end of the milling, the algorithm will be correctly tuned so that the current and/or next milling cycle produces the desired dose. This eliminates the possibility of algorithm errors due to coffee bean depletion.

An optional or alternative step is that the grinder state may be checked prior to grinding to allow the user to: i) Refilling the hopper in case the hopper becomes empty; and ii) checking the grinder if the hopper is blocked.

1) Grinder state detection method

a) The normal, empty and jammed status of the hopper is detected by current sensing.

The method relies on the current consumed by the grinder. The current in the presence of coffee beans will be greater than in the absence of coffee beans, as shown in the graph above. The threshold to turn off the grinder will be slightly higher than the current consumption of "no coffee beans". If the current is higher than when coffee beans are present, this indicates that the grinder is clogged and will be turned off.

b) The normal and empty status of the hopper is detected by speed sensing.

A similar comparison to the above may be based on the motor speed of the grinder, which varies depending on whether or not coffee beans are present in the grinder, as indicated by the following graph.

2) How to update grinding

a) If the hopper is empty or the grinder is blocked during the grinding cycle, the actual grinding time T1 is stored.

b) The remaining T2 is evaluated against the nominal value T0 and T2 is completed.

c) If the user refills the hopper after T1, then a sub-interval T3 is increased before T2.

T3 is considered to be the "zero flow time" of the coffee beans, since after refilling the empty hopper with coffee beans, there is no coffee beans between the brushes of the grinder, since the coffee beans need to move downwards from the hopper.

Fig. 71 is a flowchart of algorithm steps, where S130 represents the start of the algorithm, and step S131 is to determine whether a hopper is detected, followed by the detection of a handle in step S132.

If both the hopper and the handle are detected, the grinder is enabled in step S133 and the grinder LED is illuminated in step S134 to indicate that the grinder is on. The user can then begin grinding in step 135, such as by raising the lever of the machine.

A check is then made in step 136 to determine if there are coffee beans in the hopper. If the hopper is empty, the grinder is turned off in step S137 and the grinder LED is flashed in step 138. A check is made in step S139 to determine whether the user has removed the handle.

If the handle is still in the handle holder, the user may have refilled the hopper with coffee beans, thus checking in step 140 if the user has restarted grinding. If the user has restarted the grinder, the actual grinding time until the grinder is stopped needs to be recorded and the remaining grinding time needs to be updated in step S141, after which the process returns to step S135.

If the user does not restart grinding, the preset time is checked in step S142, after which the actual grinding is recorded in step S143 and the grinding time is updated in step 144, after which the algorithm ends at step S145.

If the user removes the handle after interrupting the grinding, a timer is started in step S146. If it is determined in S142 that the preset time is not reached and it is detected in step S147 that the handle has been inserted back into the handle holder, the process returns to step S140. Alternatively, if the preset time has elapsed, steps 143 and 144 are performed to update the grinding.

It is of course important that the grinder should not be operated if there is no handle in the handle support. Thus, if the handle is not detected in step S148, the grinder is stopped in step S149, the grinder is reset in step S150 and disabled in step S151, followed by turning off the grinder LED in step S152.

If no hopper is detected in step S153, a similar process of turning off the grinder is performed. If a hopper and handle are detected in step 148, the process returns to step 136 to check if the hopper is empty.

In step 154, the position of the lever is checked. If the lever has been moved from its original position, the grinder may be stopped by the process of step 137. If the lever position is not changed, it is checked in step S155 whether grinding is completed.

If grinding is complete, the grinder is stopped in step S156. The grinder LED is turned off and the compaction LED is turned on to indicate that the system is ready for a compaction operation.

Step S158 represents a compaction operation. The grind is updated after the compaction operation, and the process ends at 145.

Another important step in the above process is to check for any blockages in the grinder. This is done in step S159. If a jam is detected, the grinder is stopped in step S160, and an LED light on the user interface is flashed in step S161 to indicate the jammed state of the grinder. If the grinder is not plugged, the system may continue to monitor the status of the hopper and handle at steps S136, S148, and S153.

Bowl sizing inspection

One of the wrong scenarios for manual compaction systems is that the user may incorrectly select the wrong bowl size for the dosing operation. This will be: i) The next polish for the next cycle is updated erroneously; and ii) adding an incorrect grinding time to the current cycle.

In case a single dose bowl set for dosing operation has been selected but a double dose bowl is used, the resulting volume of coffee provided into the handle will be severely under dosed. To calibrate this error, a much longer grind is required.

Conversely, if a double dose bowl arrangement has been selected but a handle with only a single dose bowl is used, the amount of coffee provided to the handle will be severely excessive and the handle needs to be removed and the excess coffee cleaned.

Similar problems exist if two or more grinding cycles are performed on one handle. For example, the first grinding cycle and compaction operation is completed, the handle with coffee grounds delivered from the first grinding cycle is removed, reinserted without removing coffee grounds delivered from the first grinding cycle, and the second grinding cycle is performed again. This also causes the same problems in the subsequent grinding cycle as the use of a single dose bowl at a double dose bowl setting.

To address the above, the system 200 described above may be used to check the dosage when the compacting mechanism 11 is in use, and then a check of the calculated grinding time may be made to determine if the grinding cycle is related to the measured compaction depth to indicate if the bowl setup is incorrect. For example, if a single dose bowl setting has been selected, the compaction depth will indicate that the double dose bowl is only half full, as the grinding volume of the single dose bowl is approximately half that of the double dose bowl. The adjustment of the grinding will depend on the different scenarios according to the table below. When this is applied to each scene, a setting range is required.

Milling with single dose bowl but double dose bowl was selected

/>

Milling with double dose bowl but single dose bowl was selected

This may be accompanied by a notification, such as a filter LED flashing or a screen prompting the user that the bowl or filter setting selection may be incorrect.

Adding during the second grinding cycle to a handle containing the quantity of coffee grounds delivered from the first grinding cycle More coffee powder

This may also be accompanied by some form of false flashing or screen prompting.

User interface

With respect to fig. 72, an example of a user interface 184 is shown comprising a panel 5 with a power button 185, a grind button 186 for adding additional coffee grounds to the current use in case of under dosing, a dose control dial 187 and a filter button 188 that can be pressed to switch between filter bowl sizes. The small bowl icon 189 indicates that a single dose bowl is being used, while the larger icon 190 indicates that a double dose bowl is being used. The panel 5 also comprises an LED display 191 which displays the coffee dose in the bowl. In addition, a compaction indicator 192 (such as an LED) may be provided above the handle support 7 to indicate whether a compaction operation is in progress.

Preferably, controller 201 is configured to operate compaction indicator 192 to illuminate in at least two states, for example, a first state is red and a second state is green. The controller 201 is also preferably configured to operate the LED of the compaction indicator in a first state when the magnitude of the deviation is within a predetermined tolerance deviation and to operate the LED of the compaction indicator in a second state when the magnitude of the deviation is outside the predetermined tolerance deviation.

If the compaction depth deviates from the predetermined desired compaction depth by more than a predetermined tolerance (e.g., 0.5 mm), the controller 201 provides information to the user interface 184 indicating the sign of the deviation. For example, the user interface 184 may display "overdose" or "underdose" or "increase grind" or "decrease grind" respectively. Alternatively, the user interface 184 may display flavor-based feedback or adjustment settings, such as "weak", "strong", "ideal". Alternatively, the indicator may indicate to the user how to adjust the grinding time to calibrate the deviation. For example, in an "under dose" scenario, the LED may illuminate on the appropriate side of the dose control dial, or the LED on the button may flash to request the user to press the button to add additional grinding.

Fig. 73-76 illustrate LED lighting patterns indicating various dose conditions.

For example, if the variance in compaction depth does not exceed a predetermined tolerance, the controller 201 can illuminate one or more central LEDs 193 of the user interface 184, as shown in fig. 73, to indicate an acceptable dose. If the deviation exceeds a predetermined tolerance and the magnitude is positive, the controller 201 may illuminate one or more upper LEDs 194, as shown in FIG. 74, to indicate an excess.

If the deviation exceeds a predetermined tolerance by a predetermined threshold and the magnitude is positive, one or more upper LEDs 194 (preferably including also a central LED 193 and one or more lower LEDs 195) of the indicator panel 5 will illuminate and a warning LED 196 (as shown in FIG. 75) indicates that ground coffee should be removed from the handle. If the deviation exceeds a predetermined tolerance and the magnitude is negative, the processor 50 may illuminate one or more lower LEDs 195 of the indicator, as shown in FIG. 76, to indicate an under-dosage.

Machine calibration

The algorithmic calculations will be slightly different between different machines due to manufacturing tolerances. Therefore, factory calibration is required to solve this problem.

Assume that

All parts have been assembled correctly

The measurement is only carried out when the lever 6 is at the end dead point (=0)

In order to calibrate the machine, it is necessary to use plastic powder cakes of different heights. The plastic cakes can be, for example, -2 and +2 cakes, indicating that the height of the cake is-2 mm offset height and +2mm offset height compared to the ideal compacted height. Measurements are made on each of the compact separately to determine the relationship between the measurement result obtained from the linear sensor 20 and the distance from the ideal value. This is the so-called kinematic algorithm.

x: distance from ideal value

V: measurement results obtained from the linear sensor 20

Method

1. The on press button, filter button, and 2 cup extract button are held down for 5 seconds to enter the factory calibration mode (of course, any predetermined combination of buttons may be selected).

2. The-2 compact was placed into a double dose bowl and the handle was placed into the handle holder.

3. The lever 6 is held in the end dead center position by compaction until a beep is sounded, and then the lever 6 is returned to its original position.

4. The +2 compact was placed into a double dose bowl and the handle was placed into the handle holder.

5. The lever is held in the end dead center position until a beep is generated, and then the lever 6 is returned to its original position.

6. After the lever 6 has returned to its home position, the unit will return to standby mode.

Calculation of

After measurement using-2 and +2 plastic cakes respectively, the unit will find the formula relating the sensor 20 to the distance from the ideal value.

The gradient solution for m is found as follows,

the gradient and two points are then used to find a constant offset,

C ₄ ＝-m·V ₁ +x ₁

-combining m and C ₄ Substituting x to obtain:

∴x＝m·V+C ₄

the distance between the ideal value and the measured compaction height can thus be found by two calibration measurements. Referring to the following example, this example includes the obtained and solved measurements:

x＝3.6-V

[SW10]

user calibration

During the service life of the machine, coffee may accumulate inside the rotary hammer, which reduces the rotation and the variability of the height of the hammer. This affects the dose algorithm, as the constants calculated during factory calibration are now different.

Assume that

All parts have been assembled correctly.

Measurement only when the handle is at end dead point (θ=0)

The gradient relating the linear sensor 20 to the distance from the ideal value is the same, no matter what angle the rotary hammer is at.

The rotary hammer may have a reduced rotation angle, resulting in a compaction height varying between 0mm and 3 mm.

For calibration purposes, one measurement is required using a single-wall, single-dose bowl inserted into the handle to determine the relationship between the measurement obtained from the linear sensor 20 and the distance from the ideal value. In this case, the kinematic algorithm is as follows.

x＝m·(V-V ₁ )+x ₁

x: distance from ideal value

V: measurement results obtained from the linear sensor 20

Method

1. The on button, filter button, and 1 cup extract button are held for 5 seconds to enter the factory calibration mode, beeping for 1 second (again, this can be any combination of buttons).

2. The single dose bowl is inserted into the handle and the handle is placed into the handle holder.

3. Compaction holds the hammer in the end dead center position until a beep is generated, and then returns the lever to its home position.

4. After the lever 6 has returned to its home position, the unit will return to standby mode, sounding a 1 second beep.

Calculation of

-performing a single measurement as described in the method. The unit will now find a formula relating the linear sensor 20 to the distance from the ideal value.

x-x ₁ ＝m·(V-V ₁ )

x＝m·(V-V ₁ )+x ₁

x＝m·V-m·V ₁ +x ₁

From the factory calibration, assume that the gradients are the same, for this example, assume m= -1.

Next, a constant offset is found using the gradient and two points, where the measured variable in the formula is V recorded from the linear sensor 20 ₁ 。

C ₄ ＝-m·V ₁ +x ₁

3.6＝-(-1)·(1.2)+(2.4)

-combining m and C ₄ Substituting x to obtain:

∴x＝m·V+C ₄

x＝-1*V+3.6

x＝3.6-V

thus, the distance of the ideal value from the measurement result obtained from the sensor 20 can be found by a single calibration measurement and a constant gradient.

-[SW11]

-

Referring finally to fig. 77a and 77b, the machine includes a removable cover 187 positioned over the compaction chute 188. Cover 187 allows a user to clean the interior area of compaction chute 188. The cover 187 may also enrich the user experience so that the user can actually see the real-time compaction motion. In addition, the cover helps the user understand how the compaction is working and understand how the system 200 described above should be operated (e.g., applying appropriate forces to the handle in different positions) to obtain the best results. It also allows for the investigation of any potential problems (e.g., clogging) within compaction chute 188 without the need to separate the entire machine 1, thereby facilitating repair.

In a preferred embodiment, the cover is magnetically attached directly over the handle support 7 or removed therefrom by a slide-in/slide-out motion.

Advantages are that

Many advantages can be achieved with the machine and compacting mechanism described above.

The rotational connection between the connection and the hammer allows the hammer to be rotated away from the grinding chute on the top stroke of the mechanism, which means that the coffee grounds can be guided unhindered into the handle. Thus, the grinding chute may be located directly above the handle, which optimizes the distribution of the coffee grounds into the handle, as the coffee grounds are delivered as a centered mass, rather than from a lateral direction, which may result in maldistribution of the coffee in the resulting compacted cake. By swinging the hammer away from the chute, the chute may be centrally located without interference with the hammer during the compaction operation.

Since the compacting mechanism rotates the hammer at the top of the stroke, rather than linearly lifting the hammer off the chute, the overall height of the machine can be minimized.

The compacting mechanism preferably relies on an articulated connection formed by articulated members that provides mechanical advantage while also minimizing the overall height requirements of the machine. If racks and pinions are used instead of large-sized pinions, a larger stroke length can be achieved by combining the connector lengths. This also allows the rotation angle of the lever to be reduced, thus implementing the stroke length of the compacting mechanism in a compact form without the need for gear means.

This mechanism provides a good "handle feel" for the lever because the torque curve is not constant for a given load, whereby peak loads occur only at the end of travel. This also improves the mechanical advantage near the end of travel by reducing the force at the start of travel length. Only at the end of the stroke of the lever a maximum force is required.

A rotation sensor and/or a linear sensor associated with the lever detects a lever position and/or a compaction position that may be displayed on a user interface. The user interface may also provide possible subsequent steps so that the user may be instructed/taught to make a cup of coffee.

The grinder switch may be activated by lifting (rotating) the lever from its original position to activate the grinder. The movement of the lever and piston may be manual or electric.

The compaction force control assembly provides a biasing force to assist in compaction, which means that the required compression distance is shorter, thus making the design more compact. Pretension also means that a lower spring rate spring can be used, which can provide a more consistent force over the compression distance.

By measuring the compression of the compaction force control assembly and/or the rotation of the shaft, a compaction depth may be calculated, which may in turn be used to adjust the dose. The machine may provide feedback of the dose to the user via a user interface. This compaction depth can then also be used to calculate the optimal grinding for the correct dose. If the dose is insufficient, grinding may be increased. In the event of an excess, the next grind may be automatically reduced or displayed to the user for manual adjustment.

The manual grinding mode may be implemented if the user lifts the lever for a predetermined time. By raising the lever, the user activates the grinder switch to activate the grinder, which allows the user to manually control the amount of grinding.

The handle may be slid into a handle holder in which the handle is centrally located by a spring clip. A button may also be activated to activate the grinder. The handles are supported by handle detents, wherein one of the handle detents may be supported by the button itself. The push-in design allows for easier insertion and if a vertical fit is used, the clearance required under the handle support for insertion can be reduced.

By enclosing the compacting means in the housing, the coffee grounds can be contained inside and the resulting mess is greatly reduced.

The "handle feel" may be improved compared to a rack and pinion design, and the force required to compact the coffee grounds may also be reduced compared to a rack and pinion having the same lever rotation angle.

The spring preload of the compaction force control assembly can be used to apply and control compaction forces at different dosage levels without requiring the user to judge the handle force.

Dose feedback of compaction depth or compact height may be achieved electronically.

The electronic measurement of the cake height can be used to calculate the optimal grinding time and "more" amount.

The handle support design allows the handle to simply slide into the handle support rather than raise and rotate the handle as is required for conventional bayonet connections. This provides an improved user experience.

Parts list

1. Machine for processing a sheet of material

2. Compacting unit

3. Hopper

4. Outer casing

5. User interface panel

6. Lever

7. Handle support

8. Water dripping disk

9. Dial scale

10. Grinder

11. Compacting mechanism

12. Shaft

13. Actuator with a spring

14. Hammer

15. Compaction force control assembly

16. Piston

17. Biasing element

18. Spring

19. Connecting rod

20. Sensor for detecting a position of a body

21. Grinding chute

22. Flow path

23. An outlet

24. Center line

25. Flour with a plurality of grooves

26. End portion

27. Base seat

28. Main body

29. Coupling device

30. Connecting piece

31. End portion

32. Coupling device

33. Shell body

34. Guiding structure

35. Slot groove

36. First component

37. Second component

38. Recess (es)

39.

40. Handle

41. Switch

42. Bowl

43. Lower end of

44. Limited motion connection

45. Upper end

46. Segment(s)

47. Return device

48. Extension spring

49. Fixed mounting rack

50. Control gear

51. Rotary position sensor

52. Cog teeth

53. Damper

54. Cog teeth

55. Pivot shaft

56. Slot groove

57. End portion

58. Cross bar

59.PCB

60. Clutch device

61. Hub

62. Protrusions

63. Grinder activation switch

64. Spring

65. Column

66. Fixing structure

67. End gasket

68. Bracket

U-shaped section

70. Extension part

71. Limited motion connector

72. Rocker bar

73. Pivot shaft

74. End of rocker

75. End of rocker

76. Elongated opening

77. Driven piece

78. Channel

79. Support frame

80. Upper end

81. Lower end of

82. Pivot shaft

83. Coffee machine

84. Powder cake

85. Rack bar

86. Fixing arm

87. Landing leg

88. Cross beam

89. Teeth

90. Pinion gear

91. Slot groove

92. Roller

93. Beam

94. Base seat

95. Lower end of

96. Top part

97. Vertical portion

98. Curved top

99. Distal end

100. Gear segment

101. Intermediate gear

102. Rod

103. Driving shaft

104. Support member

105. Second connecting piece

106. Hammer body

107. Side portion

108. Gap space

109. Annular groove

110. Pin

111. Arrows

112. First disc

113. Connecting component

114. Biasing element

115. Second disc

116. Connection recess

117. Biasing element

118. Clutch disc

119. Clamp forceps

120. Annular groove

121. An opening

122. Supporting structure

123. Transverse pin

124. Support member

125. Rotary mechanism

126. Collar ring

127. Cylinder body

128. Screw bolt

129. Biasing element

130. Spring

131. Cam structure

132. Inclined plane

133. Protrusions

134. Side wall

135. Outer wall

136. Flange

137. Sealing element

138. Retaining ring

139. Notch groove

140. Skirt portion

141. Hoop ring

142. Shaft

143. Shaft

144. An opening

145. Circlip

146. Hoop ring

147. Rubber sealing member

148. Inner ring

149. Base cover

150. Shoulder part

151. Annular groove

152. Wiper blade

153. Rail track

154. Rail track

155. Lower part

156. Upper part

157. Upper part

158. Center line

159. Vertical line

160. Spring

161. Teeth

162. Segment(s)

163. Handle grip

164. Cup-shaped portion

165. Positioning lug

166. Peripheral edge

167. Access opening

168. Butt joint seat

169. Support surface

170. Support surface

171. Inclined plane

171a. Support surface

172. Clasp hook

173. Biasing element

174. Spring clip

175. Horizontal line

176. End wall

177. An opening

178. Concave part

179. Underside of the lower part

180. Main body

181. Internal profile

182. Tang of tang

183. Fastening piece

184. Sensor for detecting a position of a body

185. Sensor for detecting a position of a body

186. Sensor for detecting a position of a body

187. Removable cover

188. Compaction chute

200. System and method for controlling a system

201. Controller for controlling a power supply

202. Grinder module

203. Hammer module

204. User interface module

210. Center of the machine

211. Filter cup

212. Central axis

213. Retaining member

214. Center of the machine

215. Bottom surface of filter bowl

216. Switch

217. Central axis

218. Connection assembly

219. A first inclined surface

220. Cam

221. A second inclined surface

222. Biasing member

223. Stop member

224. Indicator device

225. Tab

226. Pin

Claims

1. A machine having a grinder, a grinding chute for delivering coffee powder along a flow path into a handle fitted on the machine, and a compacting unit having a compacting mechanism for pressing the coffee powder held by the handle into a cake, wherein the compacting mechanism comprises a connection to a hammer, the connection being arranged to press a face of the hammer in an axial direction with respect to the handle during a compacting operation, and wherein the connection returns the hammer to an idle position in which a compacted face is moved laterally out of the flow path.

2. The machine of claim 1, wherein a coupling connects the hammer to the connection to enable the hammer to rotate relative to the mechanism between the rest position and a compacting position.

3. The machine of claim 1 or 2, wherein the hammer engages with a guide structure adjacent the mechanism as the hammer moves between the rest position and the compacting position.

4. A machine according to claim 3, wherein the guide structure is a rail and the hammer includes a pivot spaced from the coupling to control pivotal movement of the hammer relative to the link.

5. The machine of claim 4, wherein the hammer includes a pair of pivots and a pair of couplings, and the machine includes two sets of rails to guide the couplings and the pivots.

6. The machine of claim 5, wherein in the compacting position, the guide and pivot are vertically arranged and the guide structure includes dual tracks to guide the coupler and pivot, respectively, the tracks being vertically aligned along a lower portion and diverging horizontally in an upper portion to move the guide and pivot horizontally to rotate the hammer to the rest position.

7. A machine according to claim 5 or 6, wherein the guide means and the pivot are attached to a support member extending from the body of the hammer and the pivot extends laterally to the hammer a greater distance than the guide means.

8. The machine of claim 7, wherein a clearance space is defined between the support members, the clearance space providing clearance for the grinding chute when the hammer is rotated to the rest position.

9. A machine according to any one of claims 1 to 8, wherein the mechanism is driven by a rotatable shaft operated by a lever connected to the shaft via a clutch to allow the lever to rotate freely when lifted from a home position.

10. The machine of claim 9, wherein the machine includes a switch for initiating operation of the grinder, the switch being activated by lifting the lever.

11. The machine of any one of claims 1 to 10, further comprising a compaction force control assembly that biases the hammer toward the coffee grounds when the hammer is in the compacted position and applies a compressive force to the coffee grounds during formation of the compact.

12. The machine of claim 11, wherein the mechanism includes a hinged connection driven by the shaft to move the hammer between the rest position and the compacting position, the compacting force control assembly biasing the hammer toward the coffee grounds when the hammer is in the compacting position and applying a compressive force to the coffee grounds during formation of the compact.

13. The machine of claim 12, wherein the compaction force control assembly is a biasing element connected between the members.

14. The machine of claim 13, wherein the biasing element is in the form of a spring piston having a piston rod spring biased between the members.

15. The machine of claim 14, wherein the members are connected for limited relative movement to accommodate different height positions of the hammer when the hammer is in the compacting position.

16. The machine of claim 15, further comprising a sensor for determining the relative extension of the piston, thereby measuring the height of the compact formed by the hammer and determining the depth of compaction.

17. The machine of claim 11, wherein the compaction force control assembly includes one or more springs positioned between a fixed portion of the assembly and a movable carriage that moves against a reaction pressure applied to the hammer when the hammer is engaged with the coffee grounds in the compaction position.

18. The machine of claim 17, wherein a limit coupler limits travel of the movable carriage.

19. The machine of claim 18 wherein the position of the movable carriage is used to determine the relative height of the compact formed by the hammer.

20. The machine of claim 11, wherein the mechanism includes a connection in the form of a slider that is driven linearly by rotation of a shaft, the slider being connected to the hammer by an articulated arm that translates the hammer along a guide rail between the rest position and the compacting position.

21. The machine of claim 1, wherein the mechanism is operated by a linear actuator connected to the body of the hammer by an articulated arm, an upper portion of the hammer having another pivot connection to rotate about an end of the grinding chute as the linear actuator moves the hammer between the rest position and the compacting position.

22. The machine of any one of claims 1 to 21, further comprising a handle mount below the compacting unit, the handle mount comprising a docking station for receiving the handle.

23. The machine of claim 22, wherein the handle support includes a sensor for determining whether the handle is loaded into the handle support.

24. A machine for delivering coffee grounds to a handle, the machine comprising:

a grinder for grinding coffee grounds into the handle;

a compacting mechanism for compacting coffee powder in the handle along a path, the compacting mechanism comprising:

a hammer comprising a surface for compacting coffee powder;

a connector connected to the hammer, wherein during a first portion of the path, the connector orients a first surface in a first direction and during a second portion of the path, the connector orients the first surface in a second direction, wherein the first direction and the second direction are different.

25. A machine for delivering coffee grounds to a handle, the machine comprising:

a grinder for grinding coffee grounds into the handle;

a hammer comprising a surface for compacting coffee powder;

a compaction actuator for moving the surface along the path, wherein during a first portion of the path, the surface is oriented in a first direction and during a second portion of the path, the surface is oriented in a second direction, wherein the first direction and the second direction are different.

26. A machine according to claim 24 or 25, wherein the compacting mechanism moves the hammer through the first and second portions of the path between a rest position in which the surface is oriented in the first direction and a compacting position in which the surface is oriented in the second direction for a compacting operation.

27. The machine of claim 26, wherein the compacting mechanism rotates the hammer between the first portion and the second portion of the path such that a compacting surface faces the second direction during the compacting operation to compact coffee powder.

28. A machine according to claim 26 or 27, wherein the hammer rotates in the rest position relative to the compacting position such that the compacting surface faces the first direction at an angle offset from the second direction, whereby the hammer does not interfere with the delivery of coffee grounds from the grinder into the handle.

29. A compacting mechanism for compacting coffee powder delivered from a coffee grind chute into a handle, the compacting mechanism comprising a connector connected to a hammer, the connector being arranged to press a face of the hammer axially with respect to the handle during compacting operations, and wherein the connector returns the hammer to an idle position along a non-axial path with respect to the handle between compacting operations such that the hammer does not interfere with delivering coffee into the handle when in the idle position.

30. The compaction mechanism of claim 29, wherein a coupling connects the hammer to the connection to enable the hammer to rotate relative to the mechanism between the rest position and a compaction position.

31. A compacting mechanism according to claim 29 or 30, wherein the hammer engages with a guide structure adjacent the mechanism as the hammer moves between the rest position and the compacting position.

32. The compaction mechanism of claim 31, wherein the guide structure is a rail and the hammer includes a pivot spaced from the coupling to control pivotal movement of the hammer relative to the link.

33. The compaction mechanism of claim 32, wherein the hammer includes a pair of pivots and a pair of couplings, and the machine includes two sets of rails to guide the couplings and the pivots.

34. A compacting mechanism according to claim 33, wherein in the compacting position, the guide means and the pivot are vertically arranged and the guide structure comprises dual tracks to guide the coupling and the pivot respectively, the tracks being vertically aligned along a lower portion and diverging horizontally in an upper portion to move the guide means and the pivot horizontally to rotate the hammer to the rest position.

35. A compacting mechanism according to claim 33 or 34, wherein the guide means and the pivot are attached to a support member projecting from the body of the hammer and the pivot extends laterally to the hammer a greater distance than the guide means.

36. The compaction mechanism of claim 35, wherein a clearance space is defined between the support members, the clearance space providing clearance for the grinding chute when the hammer is rotated to the rest position.

37. A compacting mechanism according to any one of claims 29 to 36, wherein the mechanism is driven by a rotatable shaft operated by a lever connected to the shaft via a clutch to allow the lever to rotate freely when lifted from a home position.

38. A compacting mechanism according to any one of claims 29 to 37, further comprising a compaction force control assembly that biases the hammer towards the coffee grounds when the hammer is in the compacted position, and applies a compressive force to the coffee grounds during formation of the compact.

39. The compacting mechanism of claim 38, wherein the mechanism includes an articulating connection formed from articulating first and second members, the articulating connection driven by the shaft to move the hammer between the rest position and the compacting position.

40. The compaction mechanism of claim 39, wherein the compaction force control assembly is a biasing element coupled between the members.

41. The compacting mechanism of claim 40, wherein the biasing element is in the form of a spring piston having a piston rod spring biased between the members.

42. The compacting mechanism of claim 41, wherein the members are connected for limited relative movement to accommodate different height positions of the hammer when the hammer is in the compacting position.

43. The compacting mechanism of claim 42, further comprising a sensor for determining a relative extension of the piston to measure a height of a compact formed by the hammer and to determine a compaction depth.

44. A compacting mechanism according to claim 40, wherein the compaction force control assembly includes one or more springs positioned between a fixed portion of the assembly and a movable carriage that moves against a reaction pressure applied to the hammer when the hammer is engaged with the coffee grounds in the compacting position.

45. The compacting mechanism of claim 44, wherein a limit coupler limits travel of the movable carriage.

46. The compacting mechanism of claim 45, wherein a position of the movable carriage is used to determine a relative height of the compact formed by the hammer.

47. A compacting mechanism according to claim 29, wherein the mechanism comprises a connection in the form of a slider driven linearly by rotation of the shaft, the slider being connected to the hammer by an articulated arm which translates the hammer along a guide rail between the rest position and the compacting position.

48. The compaction mechanism of claim 29, wherein the mechanism is operated by a linear actuator connected to the body of the hammer by an articulated arm, an upper portion of the hammer having another pivot connection to rotate about an end of the grinding chute when the linear actuator moves the hammer between the rest position and the compaction position.

49. A coffee grinder comprising a coffee grinder, a grind chute from which coffee powder is delivered into a handle for compaction into a cake, wherein the grind chute is centrally positioned above the handle and axially aligned with a bowl of the handle.

50. A coffee grinder according to claim 51, comprising a compacting mechanism for compacting the coffee powder delivered from the coffee grind chute into the handle, the compacting mechanism comprising a connector connected to a hammer, the connector being arranged to press a face of the hammer axially with respect to the handle during a compacting operation, and wherein the connector returns the hammer to an idle position along a non-axial path with respect to the handle between compacting operations such that the hammer does not interfere with delivering coffee into the chute when in the idle position.

51. Coffee grinder according to claim 49 or 50, further comprising a compaction chute positioned in axial alignment with the grinding chute.

52. The coffee grinder of claim 51, including a handle bracket for positioning said handle below said compaction chute, said handle bracket including a docking station for receiving said handle for receiving said coffee grounds.

53. Coffee grinder according to any one of claims 49 to 52, comprising a sensor for determining whether the handle is loaded into the handle holder.