EP1818100A1 - Grinding device for granular material, especially for alimentary use - Google Patents

Abstract

The tool has a milling ring (3) surrounding a milling cone (2) such that a mill gap is formed between the cone and the ring. The milling ring is formed in a fixed manner and the milling cone is driven by a motor (5). A gear (10) is arranged between the motor and the milling cone in a drive chain. The gear is formed in a rubber-elastic and modular manner, such that the motor is flexibly coupled to the milling cone. The cone and a drive shaft (22) of the motor are formed as single-piece.

Description

TECHNICAL AREA

The present invention relates to an improved grinding tool for the comminution of granular material from the food sector such as particularly preferred cereal grains, coffee beans, peppercorns, salt or sugar, with a grinding inner body respectively grinding cone and this Mahl-inner body to form a Mahlspaltes surrounding fixed Mahlring, said usually the grinding inner body and the grinding ring at their opposite coats in the upper region each have larger conveyor pockets forming conveying grooves and in the adjoining thereto lower cone designed as Mahlkegel area each having a smaller tooth height.

STATE OF THE ART

For food preparation pepper, salt and grain mills of the type mentioned are known. The problem with such constructions is usually the fact that a large number of different components is required in order to assemble an entire grinding tool. The complexity is increased by the fact that on the one hand as many components as possible from a cheap material like For example, should be made of molded plastic, and on the other hand certain components, ie in particular those that perform the actual grinding process, ie the grinding cone and the Mahlring, should consist of a hard material such as metal or ceramic (or optionally coated materials). In addition, such a grinder should have a compact design and it should be able to be adapted in its outer shape as different conditions.

The DE 195 14 794 relates to such a grinding tool of the type mentioned, with the least possible wear and an ideal geometric design of grinding cone and Mahlring are proposed. The actual construction of the entire structure of a grinder is not described in detail in this document.

PRESENTATION OF THE INVENTION

The invention is therefore based on the object to provide an improved, structurally simplified, and at the same time very reliable grinder of the type mentioned.

Specifically, it is an improvement of a grinding tool for crushing granular material from the food industry, more preferably grain kernels, coffee beans, peppercorns, salt or sugar containing a first refining element e.g. in the form of a grinding cone and a fixed Mahlring (second grinding element) surrounding this first Mahlelement to form a Mahlspaltes (but also the Mahlring moves and the first Mahlelement can be stationary).

The inventive construction is characterized in that between the drive and the non-fixed grinding element in the drive chain at least one coupling element is arranged, which is at least partially formed so rubbery that the drive is elastically coupled to the non-fixed grinding element.

Normally, the drive of such a mill (the drive is usually an electric motor) in a rigid manner via gears or the like connected to the actual grinder. This means that the movable element of the grinder is usually coupled via a gear with gears to the shaft of the motor. A direct coupling, that is the arrangement of the movable element of the grinder on the shaft of the motor, is not usually possible, otherwise would be required to powerful engines. Accordingly, there is a guaranteed over such gears translation.

The problem with such a structure is, inter alia, that loud noises are generated by the repeatedly occurring increased resistances by hard ground material in the grinding gap during the grinding process.

Furthermore, it is problematic that due to the direct feedback of the resistors in the grinding gap on the engine, the motor is exposed to a very irregular load and according to the structure is prone to error. The jerky load of the transmission is also a big burden for the individual gears of the transmission.

The essence of the invention is, inter alia, to some extent soften this rigid connection between the shaft of the motor (or generally the drive) and the moving parts of the grinder by at least one elastic element. This results in that the jerky loads in the grinding gap can be absorbed by the elastic coupling of the drive to the non-fixed grinding element. This leads to a reduction of noise pollution, but also leads to the fact that when striking an obstacle in the grinding gap, the necessary force can be built successively by the elastic coupling element builds up the necessary force at substantially the same speed further motor and when exceeding the limit force under relaxation of the elastic element can deliver.

Basically, the elastic coupling element may be, for example, an elastic V-belt (or an analogous construction) or an elastic lever, an elastic crankshaft, a flexible connecting rod or the like. Preferably, however, the elastic coupling element is a specially designed gear. Preferably, this gear is in relation on torsion (about the axis of rotation) elastic.

This is possible in different ways, for example, it is possible to apply a gear with its hub on a shaft, and to apply between the hub and the shaft with respect to the rotation elastic rubber ring as an elastic material or the like. In other words, it is possible to arrange an elastic material between hub and shaft, which may also be a coating.

Alternatively, and this is the presently preferred variant, it is possible to construct the gear as a two- or multi-component component. In this case, an elastic material can be formed directly on the inside of the hub, and the gear can be attached via this elastic material on the shaft. It is also possible, at least in the region of the hub and in the area of the teeth, to arrange a hard, rigid plastic material, and to provide an elastic material in the circumferential area, preferably circumferentially. This elastic material is arranged such that there is an elastic coupling between the region of the hub and the region of the toothing. In this context, a hard plastic material is to be understood as meaning a material which, for example, has an E.Module (tension) in the range from 2000 to 3500 MPa. The usual plastic materials are suitable for such components, such as polyamide, polyethylene, polypropylene, polycarbonate, ABS polyoxymethylene / polyacetal (POM, preferred), polytetrafluoroethylene (PTFE), polyetheretherketone (PEEK), polyetherimide (PEI), etc., these materials but also fiber-reinforced such as glass fiber reinforced may be formed but also metal such as aluminum, steel, etc ..

Alternatively, it is also possible to form the entire gear of such an elastic material.

According to a further preferred embodiment, in which such an elastic material is used, the elastic material is a material having a hardness in the range of 35-99 Shore or 20-95 Shore, preferably 25-90 Shore, particularly preferably 30- 50 Shore (each Shore A, according to DIN 53505, unless otherwise stated). As materials are especially rubber-elastic Materials in question, such as elastomers, rubber or rubber, preferably with such hardness.

Preferably, the elastic region is a substantially hollow cylindrical (usually circular cylindrical) region, which is delimited on its outside by the region of the toothing and on its inside by the hub, optionally between the hub and the hollow cylindrical region hard spokes and an inner Hard area may be arranged so that the inner hard area adjacent to the inside of the hollow cylindrical area. In this context, it should be noted that such spokes can be made elastic. In this case, harder material can be used, provided that the spokes are designed to thin to achieve the elastic effect.

Preferably, the hollow cylindrical region is non-positively and / or positively connected to the region of the toothing and / or to the inner hard region and / or to the shaft (which may, for example, be a drive shaft connected directly to a milling cone) respectively with these Glued areas. In addition, it is possible for projections and / or webs and / or ribs to project into the elastic region on the axially inner side of the region of the toothing and / or on the axially outer side of the inner hard region. The opposite situation is also conceivable, that is to say that the elastic region has projections and / or webs and / or ribs which protrude into corresponding recesses in the inner hard region and / or in the region of the toothing.

According to a further preferred embodiment of the invention, the projections and / or webs and / or ribs have a radial height which is less than the radial width of the elastic region, wherein particularly preferably the radial height in the range of 30-70%, in particular is preferably formed in the range of 50% of the radial width of the elastic region. An ideal elastic coupling can be achieved if, for example, the projections and / or webs and / or ribs on the region of the toothing (that is, to some extent directed radially inward) and the projections and / or webs and / or ribs on the inner hard area (that is, in a sense directed radially outward to the outside) are arranged circumferentially offset, in particular preferably symmetrical. For example, in each case 3-20, in particular preferably 5-12, such projections may be arranged.

The construction of the gear can be different, so it can be, for example, the gear to a spur gear, a worm gear or a bevel gear.

According to a further preferred embodiment of the invention, the first grinding element is a grinding cone, wherein the grinding ring is stationary, and wherein the grinding cone is indirectly connected to the drive via a coaxial, at least in the bearing area cylindrical, rotatably mounted in a bearing drive shaft and wherein preferably the drive shaft and the grinding cone are integrally formed.

Structurally and in terms of assembly, such a design is particularly advantageous when the drive shaft is connected via a self-locking detent connection with a (preferably the elastic coupling element forming) gear.

Preferably, in this context, the drive shaft is provided with an external thread or at least one thread groove, and this external thread or the at least one thread groove engages directly into an inner thread or guide rib provided in the cylindrical inner surface of the hub of a gearwheel and / or the drive shaft has at least one, preferably two thread grooves on. The toothed wheel has at least one, preferably two guide ribs, which are preferably formed only over an angular range of 5-30 °, wherein in particular preferably the external thread respectively the thread grooves have a collecting pocket, in which the connection between the drive shaft and gear selbsteinrastend when reaching the stop locks.

In such a construction can also be between a preferred as Plain bearing trained bearing and the gear a spring element can be arranged, which ensures a restoring force in the axial direction to support the Selbsteinrastung, which is preferably in this spring element is a corrugated spring. The bearing and / or the gear are, for example, at least partially made of plastic, and particularly preferably produced in an injection molding process.

Preferably, the grinding cone and the drive shaft arranged thereon and / or the grinding ring are made of metal, particularly preferably of steel, of a body coated with a hardened material, or of ceramic.

As already explained, the drive may be a manual drive or, more preferably, an electromotive drive, wherein the gear is particularly preferably driven via a drive gear, which is arranged directly on the shaft of the electric motor.

Further preferred embodiments of the invention are described in the dependent claims.

• Verbindung von Mahlkegel und Abtriebswelle zu einer einstückigen Einheit verringert den Montageaufwand u. reduziert die Summentoleranzen.
• Verbindung von Abtriebswelle und -Zahnrad durch einen angespritzten EinrastVerschluss. Dabei wird das Antriebszahnrad über ein Federelement auf den Antriebsbolzen vorgespannt eingerastet.
• Geräuschdämpfung beim Abrollen des Antriebszahnrades auf dem Abtriebszahnrad durch einen 2-Komponenten-Aufbau des Abtriebzahnrades: Das Zahnrad wird durch eine Dämpfungsschicht aus Gummi unter dem Zahnkranz gegen Schwingungs- und Körperschallübertragungen gedämpft. Weiters verleiht dieser Aufbau eine Elastizität in radialer Richtung am Zahnkranz und dämpft dadurch die Krafteinleitung im Falle des Blockierens.
• Verstellrasterung über angespritzte Halbkugeln auf einem Filmscharnier des Grundgehäuses, welche im Verstellring einrasten (vergleiche die weiter unten im Detail diskutierte Rastnase 9 zusammen mit dem Verstellring 4 und den darin angeordneten Vertiefungen 31). Die Rasterung (Vertiefungen 31) am Verstellring ist ebenfalls mitgespritzt.
• Für eine weiter abgesicherte Variante ist der Einbau einer Rutschkuppelung direkt zwischen Abtriebswelle und Nabe des Abtriebszahnrades vorgesehen.
• Modulbauweise: Durch die Modulbauweise ist es möglich, den Antriebsmotor jeweils zum Beispiel um 90° Grad um die Längsachse zu versetzen, wodurch besser auf die Platzverhältnis in der jeweiligen Kaffeemaschine eingegangen werden kann. Die starke Reduktion der Anzahl der einzelnen Bauteile sowie die modulare Bauweise ist ein grosser Vorteil insbesondere bei derartigen Mahlwerken, welche in grössere Maschinen eingebaut werden sollen, da auf unterschiedlichste Platzverhältnisse angepasst werden kann.
• Verstellmechanismus: Der Verstellmechanismus des Mahlwerks ist durch Integration der Längsführungen (vergleiche die weiter unten diskutierten axialen Führungen 38) in den Mahlring bzw. in das Grundgehäuse (vergleiche das weiter unten diskutierte Führungselement 8) mit lediglich 2 Teilen machbar. Dies ist möglich durch die Integration von Funktionen des Verstellmechanismus' in den Mahlring.

The following elements are taken together either in combination or considered individually in each case per se constructions according to the invention, which also have novelty and inventive character independently of the abovementioned features:

• Connection of grinding cone and output shaft to a one-piece unit reduces the assembly costs u. reduces the sum tolerances.
• Connection of output shaft and gear through a molded snap-in lock. The drive gear is locked biased by a spring element on the drive pin.
• Noise damping when rolling the drive gear on the output gear through a 2-component structure of the output gear: The gear is damped by a rubber damping layer under the ring gear against vibration and structure-borne sound transmissions. Furthermore, this structure gives elasticity in the radial direction on Sprocket and thereby dampens the introduction of force in the case of blocking.
• Verstellrasterung about molded hemispheres on a film hinge of the base housing, which engage in the adjusting ring (see the detail discussed below detent 9 together with the adjusting ring 4 and the recesses 31 disposed therein). The screening (recesses 31) on the adjusting ring is also injected.
• For a more secure version of the installation of a slip coupling is provided directly between the output shaft and hub of the output gear.
• Modular design: Due to the modular design, it is possible to offset the drive motor, for example, by 90 ° degrees around the longitudinal axis, so that the space ratio in the respective coffee machine can be better addressed. The strong reduction in the number of individual components and the modular design is a great advantage especially in such grinders, which are to be installed in larger machines, as can be adapted to different space conditions.
• Adjusting mechanism: The adjusting mechanism of the grinder is feasible by integrating the longitudinal guides (compare the axial guides 38 discussed below) into the grinding ring or into the basic housing (compare the guide element 8 discussed below) with only two parts. This is possible by the integration of functions of the adjusting mechanism 'in the Mahlring.

BRIEF EXPLANATION OF THE FIGURES

Fig. 1

Eine perspektivische Ansicht einer Kaffeemühle gemäss einem ersten Ausführungsbeispiel;

Fig. 2

Eine Ansicht auf die Kaffeemühle gemäss Figur 1 von oben;

Fig. 3

Einen Schnitt durch die Kaffeemühle gemäss Figur 1 entlang der Schnittlinie A-A in Figur 2;

Fig. 4

Eine Kaffeemühle gemäss einem weiteren Ausführungsbeispiel, wobei a) eine perspektivische Ansicht von schräg oben darstellt; b) eine perspektivische Ansicht von schräg unten darstellt; c) eine Ansicht von oben darstellt; d) einen axialen Schnitt entlang der Schnittlinie A-A in Figur 4c) darstellt; e) eine Explosionsdarstellung der einzelnen Elemente dieses Ausführungsbeispiels darstellt;

Fig. 5

Verschiedene Ansichten des einstückig ausgebildeten Mahlkegels mit Antriebswelle, wobei a) eine perspektivische Ansicht darstellt; b) eine Ansicht von oben darstellt; c) eine Ansicht von der Seite darstellt;

Fig. 6

Unterschiedliche Ansichten des Mahlringes darstellt, wobei in a) eine perspektivische Ansicht dargestellt ist, in b) eine Ansicht von der Seite; in c) ein axialer Schnitt dargestellt ist; in d) ein Detail gemäss Ausschnitt D in b) dargestellt ist;

Fig. 7

Unterschiedliche Ansichten des Zahnrades, wobei in a) eine perspektivische Ansicht dargestellt ist, in b) eine Aufsicht dargestellt ist; und in c) ein axialer Schnitt entlang der Schnittlinie A-A in b) dargestellt ist;

Fig.

8 Unterschiedliche Ansichten des Führungselements, wobei in a) eine perspektivische Ansicht von schräg unten dargestellt ist, in b) eine perspektivische Ansicht von schräg oben dargestellt ist; in c) eine seitliche Ansicht dargestellt ist; in d) eine Aufsicht von oben dargestellt ist; in e) ein axialer Schnitt entlang der Schnittlinie A-A in d) dargestellt ist;

Fig. 9

Unterschiedliche Ansichten des Verstellringes, wobei in a) eine perspektivische Ansicht von schräg unten dargestellt ist, in b) eine perspektivische Ansicht von schräg oben dargestellt ist; in c) eine seitliche Ansicht dargestellt ist; in d) ein axialer Schnitt entlang der Linie A-A in f) dargestellt ist; in e) eine Ansicht von unten dargestellt ist; in f) eine Ansicht von oben dargestellt ist; in g) der Schnitt entlang der Linie B-B in e) dargestellt ist, und in h) der Ausschnitt C aus Figur 9 g) dargestellt ist; und

Fig. 10

Unterschiedliche Ansichten des Flügelrades, wobei in a) eine perspektivische Ansicht dargestellt ist, in b) ein axialer Schnitt entlang der Linie A-A in c) dargestellt ist und in c) eine Aufsicht dargestellt ist.

The invention will be explained in more detail with reference to embodiments in conjunction with the drawings. Show it:

Fig. 1

A perspective view of a coffee grinder according to a first embodiment;

Fig. 2

A view of the coffee grinder according to Figure 1 from above;

Fig. 3

A section through the coffee grinder according to Figure 1 along the section line AA in Figure 2;

Fig. 4

A coffee grinder according to another embodiment, wherein a) is a perspective view obliquely from above; b) shows a perspective view obliquely from below; c) represents a view from above; d) shows an axial section along the section line AA in Figure 4c); e) represents an exploded view of the individual elements of this embodiment;

Fig. 5

Various views of the integrally formed Mahlkegels with drive shaft, wherein a) represents a perspective view; b) represents a view from above; c) represents a view from the side;

Fig. 6

Different views of the Mahlringes, wherein in a) a perspective view is shown in b) a view from the side; in c) an axial section is shown; in d) a detail according to detail D in b) is shown;

Fig. 7

Different views of the gear, wherein in a) a perspective view is shown, b) is shown in a plan view; and in c) an axial section along the section line AA in b) is shown;

FIG.

8 different views of the guide element, wherein in a) a perspective view is shown obliquely from below, in b) is a perspective view obliquely from above; in c) a side view is shown; in d) a top view is shown; in e) an axial section along the section line AA in d) is shown;

Fig. 9

Different views of the adjusting ring, wherein in a) a perspective view is shown obliquely from below, in b) is a perspective view shown obliquely from above; in c) a side view is shown; in d) an axial section along the line AA in f) is shown; in e) a view from below is shown; in f) a view from above is shown; in g) the section along the line BB in e) is shown, and in h) the section C from FIG. 9 g) is shown; and

Fig. 10

Different views of the impeller, wherein in a) a perspective view is shown in b) an axial section along the line AA in c) is shown and in c) is shown a plan view.

WAYS FOR CARRYING OUT THE INVENTION

In the following, the invention will be explained with reference to several examples. The explanation of these examples and their operation serves to illustrate the technical feasibility of the invention and different designs. However, the embodiments should not be construed as limiting the subject matter of the invention as defined in the appended claims.

FIG. 1 shows a perspective view of a first embodiment of a coffee grinder according to the invention. The coffee grinder 1 in this case comprises a motor 5, which is controlled / supplied via a cable 6, which can be used for electrical supply and / or optionally also for controlling the motor. Furthermore, a housing 7 is present, in which or on which the essential functional elements are arranged. The coffee grinder comprises a grinding cone 2 which is arranged within a grinding ring 3. In an upper region, the filling region 19, the two elements 2 and 3 are formed conically in opposite directions to form a large gap. In this filling gap conveying grooves 29 are also provided both on the grinding cone and on the grinding ring, which are to lead the material to be ground in the actual grinding area. The material to be ground may be granular material from the food sector, in particular preferably coffee beans. Likewise, such a mill can also be used for crushing pepper or the like.

The grinding ring 3 is surrounded by an adjusting ring 4, which has outwardly over ribs 18, via which the adjusting ring 4 can be rotated and thus the grinding gap of the mill can be adjusted. Furthermore, a guide element 8 for arranged the Mahlring. The guide element 8 has a resiliently molded onto this latching lug 9, which engages in a row 31 of depressions in the adjusting ring 4 and thus defines 4 defined positions for the rotation of the adjusting ring.

On the guide element 8 is normally also formed an outlet opening 34 for the ground millbase.

Below these elements, a gear 10 is arranged. This gear 10 is in operative connection with the grinding cone and serves to drive the same. The gear 10 is composed of a plurality of components such as an inner hard portion 11, an outer hard portion 13, the teeth, and an intermediate elastic portion 12. This elastic portion is made of rubber having a hardness of 20-95 Shore A, preferably 25-90 Shore A, particularly preferably 30-50 Shore A, formed. This gear, which is rigidly connected via the drive shaft 22 of the grinding cone 2 with the grinding cone 2, is driven by a drive gear 14, which is normally arranged directly on the shaft of the motor 5. In the present case, the tip of this drive gear 14 passes through the housing 7 in an opening 15th

FIG. 2 shows a top view of a coffee grinder according to FIG. 1. It can be seen, inter alia, that the rubber-elastic region 12 between the inner hard region 11 and the outer hard region, the toothing 13 of the toothed wheel 10, is arranged in such a way a permanent relative displacement of the elements 11 and 13 is prevented. For this purpose, outwardly directed projections or ribs or webs 17 are arranged on the inner hard area, which protrude into the elastic region 12. Similarly, oppositely directed to the outer hard area, the teeth 13, inwardly directed projections, ribs or webs 16 are arranged, which also project into the intermediate region 12. The projections 16 and 17 are preferably arranged symmetrically offset in the direction of rotation. By this toothing of the elements 16 and 17 in the elastic region 12 it is ensured that the region 12 acts only in an elastic respect and no slippage between the elements 11 and 13 is possible.

As can be seen from the sectional view according to FIG. 3, such a coffee grinder comprises considerably fewer individual elements than the prior art, which is one of the great advantages of the proposed design.

The adjusting ring 4 engages in a rotatable guide 20 (freely rotatable) in the Mahlring 3, and thus ensures that the relative axial position of the elements 3 and 4 is fixed, but not their relative rotational position. The connection 20 is preferably designed as a click connection. In the example according to FIG. 3, it is designed such that a groove is present in the grinding ring and a corresponding rib in the adjusting ring, but of course it is also possible to provide a rib on the grinding ring and a groove in the adjusting ring.

The adjusting ring 4 sits outside on the guide element 8. As the actual bearing for the drive shaft or spindle 22 of the grinding cone 2, a guide bush 24 is arranged, which is fixed in the guide element 8.

As can be seen from the actual task of the coffee grinder, the grinding ring 3 and the grinding cone 2 are made of a hard material such as steel or ceramic, otherwise these elements would be successively destroyed by the grinding process. It is essential, inter alia, that the actual grinding cone 2 is formed integrally with its drive shaft 22. In other words, the drive shaft 22 is made of the same material as the grinding cone. This drive shaft 22 is mounted in a sliding guide in the guide bush 24. Below the guide bushing 24, the gear 10 is arranged. Between the gear 10 and the guide bush 24 while a spring element 25 is arranged in the form of a corrugated spring. In addition, the drive shaft 22 via thread grooves 23 and the gear wheel in turn on the inner cylindrical surface of the hub 26 via corresponding guide ribs 28. Furthermore, the thread grooves 23 end in the drive shaft 22 in so-called collecting pockets 36. Furthermore, it must be emphasized that the direction of rotation of the mill relative to Screwing the thread grooves 23 in the guide rib 28 is formed such that when the normally prevailing operating direction of rotation of the Mahlkegels the attachment between the gear 10 and drive shaft 22 is tightened.

In general, the attachment of the grinding cone with the molded-on drive shaft 22 in this construction is extremely simple. Thus, namely, the grinding cone 2 and its drive shaft can be inserted from above into the guide bushing 24 and from below the gear 10 are placed at intermediate spring element 25 and turned up. In this case, the thread groove 23 successively screwed into the guide rib 28 until reaching the collecting bag 36 against the spring force of the spring 25, wherein the attachment between the gear 10 and shaft 22 automatically clicks on reaching the collecting bag 36.

Adjusting ring 4, guide member 8 and the further arranged between grinding cone and guide bushing 24 impeller 30 and the hard elements of the gear 10 are made of plastic, typically of a molded plastic. In particular, the gear is preferred to use glass fiber reinforced plastic. The gear 10 has a construction with an inner hub 26, the outgoing spokes 27 and the already explained inner hard construction 11 (to some extent rim), wherein the elements 26, 27 and 11 are preferably integrally formed.

As can be seen from the synopsis of Figures 1 - 3, thus resulting due to the integral formation of grinding cone 2 and drive shaft 22 with respect to the production but also with respect to the assembly very simple construction, which leads to a reduction in the number of necessary parts leads. In addition, results from the rubber-elastic region 12, a partial decoupling of the actual grinder from the engine. It is due to the elastic region 12 to a certain extent elastic decoupling, which on the one hand leads to an increased ease of movement during the grinding process, and on the other hand, a considerable noise attenuation during grinding entails.

Furthermore, it follows from the synopsis of FIGS. 1-3 (as well as on the basis of the example shown below) that the proposed grinder is of a highly modular design and can be adapted to different external conditions. For example, it is possible to guide the motor from above into the housing 7, furthermore, it is possible for the gearwheel 10 to also be in the form of a worm wheel or a bevel gearwheel form and, for example, the drive gear 14 tangentially coupled to the gear 10. Since such grinders are installed, for example, in coffee machines as an individual component, this flexibility is of enormous advantage, since it makes it possible to adapt such a grinder, for example, to the predetermined dimensions in an already designed coffee machine.

The following figures show a further embodiment of a coffee grinder according to the invention. In Figure 4a) and b) perspective views of this further embodiment are shown, wherein in a) a view is shown obliquely from above and in b) a view obliquely from below. In essence, the construction is analogous to the construction according to FIGS. 1-3, but the housing element 7 is designed substantially only as a greatly reduced support element. In particular, from Figure 4 can also be the very slim axial design can be detected. It can be seen from FIG. 4c) that the proposed grinder also has very small dimensions in radial expansion.

Among other things, from Figure 4d) can be seen that the adjusting ring 4 with guide grooves 33 respectively. an actual guide thread is equipped, which cooperates with outer guide ribs 32 on the guide element 8. If the adjusting ring 4 is rotated, due to the free rotation between the grinding ring 3 and the adjusting ring 4 and due to the guide grooves 38 provided in the grinding ring 3 and the guide ribs 39 disposed in the guide element 39, the grinding ring 3 shifts exclusively due to the pitch of the thread 32/33 in the axial direction, and so the spacing of the actual Mahlspaltes can be adjusted. This is the so-called Mahlgradverstellung (adjustment of the fineness of the ground good).

From Figure 4e), the dramatic reduction in the number of components can be detected. In essence, only about 14 components are needed, and there are only 4 screws 35 required due to the large number of click mechanisms used, which is very surprising in view of the high axial load during the grinding process.

FIG. 5 shows in detail the grinding cone 2 with the drive shaft 22 formed integrally with the grinding cone. In particular, it can be seen that the Thread grooves 23 end at their end in a collecting bag 36, respectively. By cooperating with the aforementioned guide ribs 28 on the hub 26 of the gear 10 so a definitive stop and latching position for the relative fixation of grinding cone resp. Drive shaft 22 can be ensured on the gear 10. Furthermore, typical and possible dimensions of such a grinding cone can be taken from FIGS. 5b) and c).

FIG. 6 shows the grinding ring with the already explained axial guide recesses 38, which ensure that, when turning on the adjusting ring 4, the grinding ring is displaced exclusively in the axial direction. In addition, it can be seen that the free rotation of the adjusting ring 4 and the grinding ring 3 can be ensured by the circumferential groove 37. From the figures 6b) - d) possible dimensions for such a grinding ring can be taken.

Figure 7 shows the gear 10 in different views. From Figure 7a), the very light construction can be seen, which nevertheless has a sufficient stability due to the struts. Possible dimensions (in each case mm) can be taken from FIGS. 7b) and c), and these, as well as the other dimensions mentioned in the context of this disclosure, are of course only to be understood as an example and approximate and simply represent one of the possible realizations. Other dimensions are of course possible depending on load conditions and depending on space. It can be seen in particular from FIGS. 7a) -c) that the guide rib 28 is a somewhat lenticular projection which sweeps over only part of the radial circumference and which is arranged at two opposite positions. Accordingly, the drive shaft 22 has two corresponding thread grooves 23 which cooperate with these guide ribs 28.

In Figure 8 different views of the guide element are shown. In particular, it can be seen that the guide element 8 has outer guide ribs 32 with a certain pitch. Furthermore, the inner axial guide ribs 39 for the corresponding axial guide recesses 38 in the grinding ring 3 can be detected.

In particular, it is especially the latching lug 9, which is molded directly on the guide element 8 via a tongue such that the hemisphere at the end is elastically sprung and thus can be completely dispensed with the separate arrangement, for example, a coil spring. As already explained, engages the locking lug 9 in corresponding recesses 31 in the adjusting ring 4 and sets so clearly different rotational position of the adjusting ring. In the present case, the guide ribs 32 are formed only in segments, but it can also be a continuous train. Furthermore, four axial guide ribs 39 are arranged in the present case, but it is of course also possible to arrange only such a guide rib or two, three or, for example, six such axial guide ribs. However, the arrangement of four such guide ribs is optimal in terms of jamming in many situations.

In Figure 9 different views of the adjusting ring 4 can be seen. In particular, the row 31 of depressions on the lower edge can be recognized, in which the latching lug 9 engages in the different rotational positions. As can be seen from Figure 8d), two such locking lugs 9 are arranged opposite one another, and accordingly the adjusting ring 4 also has two 180 ° segments of parallel to the pitch of the guide groove, respectively. the guide thread 33 extending scenes. Furthermore, it can be recognized, for example, from FIG. 9b) that the guide in the circumferential groove 37 is ideally realized via a nub 40, which allows the adjusting ring to be clicked onto the grinding ring 3 via a click mechanism. For this purpose, the Einrastnoppe 40 is easily movable formed, for example, in turn, a tongue. Or simply by the inherent deformability of the material, as is done in the present case (see Figure 9d)).

Finally, FIG. 10 shows different views of the impeller 30, which is arranged between the underside of the grinding cone and the corresponding guide of the guide element 8. The impeller 30 is preferably clipped from below onto the grinding cone. The impeller 30 has on the outside via wings 41, which serve the ground good from the chamber below the grinder drive out through the opening 34. For this purpose, the impeller 30 must rest rotationally fixed on the drive shaft 22, and accordingly, on the inner contour of the impeller 30, limits 42 are provided which engage in corresponding linear grooves of the drive shaft 22 directly below the cone 2.

• Verstellring mit Wellenkontur für Verstellrasterung;
• Mahlring, der im Verstellring eingeklipst mit Nuten gegen das Verdrehen im Gehäuse gesichert;
• Mahlkegel mit einstückig dazu ausgebildeter integrierter Lagerwelle;
• Flügelrad ist auf den Mahlkegel resp. auf die Lagerwelle aufgeklipst;
• Lagerwelle des Mahlkegels verfügt über Einrastverschluss an das Zahnrad;
• das Führungselement verfügt über eine angespritzte Halbkugel für die Verstellrasterung;
• eine Wellfeder erlaubt eine spielfreie Befestigung der Lagerwelle des Mahlkegels am Zahnrad;
• das Zahnrad ist als Zweikomponentenspritzgussteil ausgebildet, wobei ein Zwischenbereich als Dämpfungsbereich aus einem elastischen Material gebildet ist.

Thus, among other things, individual or combinations of the following elements can be regarded as essential elements:

• Adjusting ring with wave contour for Verstellrasterung;
• Mahlring, which is clipped in the adjusting ring with grooves secured against twisting in the housing;
• Grinding cone with integrally formed integrated bearing shaft;
• Impeller is on the Mahlkegel resp. clipped onto the bearing shaft;
• Bearing shaft of the grinding cone has snap-lock on the gear;
• the guide element has a molded hemisphere for Verstellrasterung;
• a corrugated spring allows a backlash-free attachment of the bearing shaft of the grinding cone on the gear;
• the gear is formed as a two-component injection-molded part, wherein an intermediate region is formed as a damping region of an elastic material.

LIST OF REFERENCE NUMBERS

1

coffee grinder

2

milling cone

3

grinding ring

4

adjusting

5

engine

6

Supply / control of 5

7

casing

8th

Guide element for grinding ring

9

locking lug

10

gear

11

inner hard area of 10

12

elastic range of 10

13

Toothing of 10

14

drive gear

15

Opening in 7 for 14

16

Projections / ribs on 13

17

Projections / ribs on 11

18

Ribs on 4

19

Grinding gap, filling area of 1

20

rotatable guide from 3 to 4 (tongue and groove)

21

Molars on 2

22

Drive shaft / spindle of 2

23

Thread grooves in 22

24

Guide bush for 22

25

Bungee / wave spring

26

Hub of 10

27

Spokes of 10

28

Guide rib on 26 for 23

29

transporting grooves

30

impeller

31

Row of depressions in 4

32

Guide rib at 8 for 4

33

Guide groove / Führenzngsgewinde in 4

34

Outlet opening for regrind

35

screw

36

collecting pocket

37

circumferential groove in 3 for circumferential rib of 4

38

axial guide recesses in 3 for 8

39

axial guide ribs on 8 for 38

40

Snap knob for 4 (spring)

41

wing

42

limiter

Claims (17)

Grinding tool (1) for comminuting granular material from the food sector, such as, in particular, cereal grains, coffee beans, peppercorns, salt or sugar, with a first refining element (2) and a second refining element in the form of a first refining element (2) surrounding a refining gap Mahlringes (3), wherein either the Mahlring (3) is fixed and the first grinding element (2) by a drive (5) is driven, or the first grinding element (2) is stationary and the Mahlring (3) of the drive (5) is driven,
characterized in that
between the drive (5) and the non-stationary grinding element (2, 3) in the drive chain at least one coupling element (10) is arranged, which at least partially (12) is designed so rubber-elastic that the drive (5) to the non-fixed grinding element ( 2, 3) is elastically coupled. Grinding tool (1) according to claim 1, characterized in that it is the coupling element (10) is a gear which is elastically formed with respect to torsion. Grinding tool (1) according to claim 2, characterized in that the gear (10) is constructed as a two- or multi-component component, wherein at least in the region of the hub (26) and in the region of the toothing (13) arranged a hard, rigid plastic material is, and wherein in the intermediate region, an elastic material (12) is preferably circumferentially arranged such that between the region of the hub (26) and the region of the toothing (13) has an elastic coupling. Grinding tool according to claim 3, characterized in that it is the elastic material (12) is a material having a hardness in the range of 20-95 Shore, preferably 25-90 Shore A, particularly preferably 30-50 Shore A, more preferably in order Rubber, elastomer or rubber with such a hardness. Grinding tool according to one of claims 3 or 4, characterized in that the elastic region (12) is a substantially hollow-cylindrical region (12), which is delimited on its outside by the region of the toothing (13) and on its inside by the hub (26), optionally between the hub (26) and the hollow cylindrical portion (12) hard spokes (27) and an inner hard area (11) may be arranged so that the inner hard area (11) on the inside adjacent to the hollow cylindrical portion (12). Grinding tool according to claim 5, characterized in that the hollow cylindrical portion (12) non-positively and / or positively connected to the region of the toothing (13) and / or with the inner hard region (11) is bonded respectively with these areas. Grinding tool according to one of claims 5 or 6, characterized in that on the axially inner side of the region of the toothing (13) and / or on the axially outer side of the inner hard portion (11) in the elastic region (12) protruding projections and / or webs and / or ribs (16, 17) are arranged. Grinding tool according to claim 7, characterized in that the projections and / or webs and / or ribs (16, 17) have a radial height which is less than the radial width of the elastic region (12), wherein in particular preferably the radial height in the range of 30-70%, particularly preferably in the range is formed of 50% of the radial width of the elastic region (12). Grinding tool according to one of claims 7 or 8, characterized in that the projections and / or webs and / or ribs (16) at the region of the toothing (13) and the projections and / or webs and / or ribs (17) on the inner hard Region (11) are arranged circumferentially offset, more preferably symmetrical. Grinding tool according to one of claims 2-9, characterized in that it is the gear (10) is a spur gear, a worm gear or a bevel gear. Milling tool according to one of the preceding claims, characterized in that the first grinding element is a grinding cone (2), that the grinding ring (3) is stationary, and that the grinding cone (2) has a coaxial, at least in the bearing area cylindrical, in a bearing (24) rotatably mounted drive shaft (22) is indirectly connected to the drive (5), wherein the drive shaft (22) and the grinding cone (2) are integrally formed. Grinding tool (1) according to claim 11, characterized in that the drive shaft (22) via a self-locking latching connection with a gear (10) is connected. Grinding tool (1) according to claim 11 or 12, characterized in that the drive shaft (22) is provided with an external thread or at least one thread groove (23), and this external thread or the at least one thread groove (23) directly into a cylindrical inner surface the hub (26) of a gear (10) provided inside thread respectively guide rib (28) engages and / or that the drive shaft (22) at least one, preferably two thread grooves (23), and that the gear (10) at least one, preferably two Guide ribs (28), which are preferably formed only over an angular range of 5-30 °, has, in particular preferably the external thread or the thread grooves (23) have a collecting pocket (36) into which the connection between the drive shaft (22) and gear (10) engages self-locking when reaching the stop. Grinding tool according to one of claims 11-13, characterized in that between a preferably designed as a sliding bearing (24) and the gear (10) a spring element (25) is arranged, which ensures a restoring force in the axial direction to support the Selbsteinrastung, said it is preferable that this spring element (25) is a corrugated spring. Grinding tool according to one of claims 11-14, characterized in that the bearing (24) and / or the gear (10) are at least partially made of plastic, as particularly preferably produced in an injection molding process. Grinding tool according to one of the preceding claims, characterized in that the grinding cone (2) and the drive shaft (22) arranged thereon and / or the grinding ring (3) made of metal, in particular preferably made of steel, of a body coated with a hardened material, or of ceramic. Grinding tool according to one of the preceding claims, characterized in that the drive (5) is a manual drive or, more preferably, an electromotive drive (5), wherein the gear (10) is particularly preferably driven via a drive gear (14). , which is arranged directly on the shaft of the electric motor (5).

Images