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WO2008006672A1 - Mécanisme de moulin à amortissement du bruit de corps pour un moulin à denrées alimentaires - Google Patents

Mécanisme de moulin à amortissement du bruit de corps pour un moulin à denrées alimentaires Download PDF

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Publication number
WO2008006672A1
WO2008006672A1 PCT/EP2007/056060 EP2007056060W WO2008006672A1 WO 2008006672 A1 WO2008006672 A1 WO 2008006672A1 EP 2007056060 W EP2007056060 W EP 2007056060W WO 2008006672 A1 WO2008006672 A1 WO 2008006672A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
mill according
container
mill
grinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2007/056060
Other languages
German (de)
English (en)
Inventor
Joachim Damrath
Stefan Holzer
Winfried BÄR
Dietmar Freitag
Gerd FÖRSTER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BSH Hausgeraete GmbH
Original Assignee
BSH Bosch und Siemens Hausgeraete GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BSH Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Publication of WO2008006672A1 publication Critical patent/WO2008006672A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47J—KITCHEN EQUIPMENT; COFFEE MILLS; SPICE MILLS; APPARATUS FOR MAKING BEVERAGES
    • A47J42/00—Coffee mills; Spice mills
    • A47J42/38—Parts or details
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47J—KITCHEN EQUIPMENT; COFFEE MILLS; SPICE MILLS; APPARATUS FOR MAKING BEVERAGES
    • A47J31/00—Apparatus for making beverages
    • A47J31/42—Beverage-making apparatus with incorporated grinding or roasting means for coffee

Definitions

  • the invention relates to a food mill with a structural unit comprising a Mahlgut actuallyer, a grinder in a grinding room and a drive motor for it and which is mounted elastically in a device housing.
  • a characteristic of the unit is the mechanically rigid connection between its components, ie between the grinding stock, the grinding chamber and the engine and gearbox. In the following, simplifying only the engine is mentioned, in which the transmission should be included.
  • Such a food mill may be a flour mill or a coffee grinder, in particular one that is installed in a coffee machine.
  • the device housing may then be, for example, that of the coffee machine, and the Mahlgut disposer takes on coffee beans.
  • Coffee machines are popular and widely used items in homes and offices because of their ease of use. Their acceptance, however, suffers from the noise that their use can cause. Especially in areas where concentrated work or frequent telephone calls with customers, the operating noise of loud coffee machines is very disturbing.
  • the most audible source of noise in operation is the grinder at a first crushing stage, namely breaking the grains or beans.
  • Acoustically second is the drive motor of the grinder.
  • the grinder at the second crushing stage namely when grinding and grinding the grains or beans.
  • These noise sources produce emissions of two fundamentally different types: airborne and structure-borne noise emissions.
  • Airborne noise emissions are due to oscillating ambient air, which as such reaches the human ear directly. To avoid this, the airborne sound path between the emission source and the human ear z. B. be interrupted by a housing. An airborne sound insulation can be achieved by absorption.
  • structure-borne noise emissions are due to vibrations and vibrations of parts of the equipment which, for their part, cause the ambient air to vibrate, resulting in so-called secondary airborne noise. vortig. Only this and not the structure-borne sound waves are perceptible to the human ear. To avoid this either the vibrations can be avoided or vibration-sensitive components can be decoupled or the secondary airborne sound can be insulated.
  • DE 22 140 22 describes a unit for a coffee grinder, which consists of a hopper, a grinder and an electric motor. This unit is clamped against a device housing by means of clamping screws and preloaded rubber buffer vibration isolation. This creates an effective structure-borne sound insulation. It makes use of the principle of the mass-spring system by decoupling an oscillating mass, in this case the structural unit, by means of springs, namely the rubber buffers, from their surroundings, the device housing. The correctly dimensioned spring prevents the vibrations of the vibrating mass from being transmitted to the environment. The dimensioning of the spring relates to its dynamic stiffness, which is tuned to the size of the vibrating mass and the frequency of its vibration.
  • the invention thus turns away from an additional load of the elastic material due to a fastening force. Rather, it pursues the principle of securing the elastic material between the mass to be insulated, namely the structural unit, and the environment to be protected, that is to say the housing, by means of a pretension-free mounting.
  • a holder without a biasing force on the elastic material may for example consist of a frame which mechanically holds the elastic support in the required position between the assembly and the housing. The frame must only hold the bearing material in the two degrees of freedom at right angles to the loading direction. On the one hand, it has to rise so high that it reliably fulfills its holding function even with transverse forces, and on the other hand, it must be so low that it does not restrict the spring travel of the elastic material. A contact between the housing and the unit must therefore not arise.
  • the elastic material may consist of a bondable, planar or plate-shaped material.
  • the term "plate-shaped" means that the material has a large extent in at least one of the two directions perpendicular to the direction of loading, which means that the elastic material provides suitable adhesive surfaces as a prerequisite for its attachment by gluing
  • it is also much less susceptible to failure, because it almost eliminates the formation of an unwanted sound bridge and thus the deactivation of the elastic bearing, in contrast to a screw connection.
  • any elastic material can be used.
  • the elasticity can in principle be based on shape and / or material elasticity. Therefore, in particular foamed elastic materials, for example rubber, mixtures of cork and rubber or so-called foamed rubber into consideration.
  • the elastic material is a foamed plastic. It can draw its elastic property from its foam structure and additionally have a corresponding material elasticity.
  • a polyurethane may be used, which is available for example under the brand Sylomer ® commercially. Foamed polyurethane is characterized by a simple processability, because it can be easily punched or even cut by hand, depending on the thickness. In addition, it can be produced accurately in tight tolerances in different densities.
  • this elastic material can be accurately designed for the particular load case, so dimensioned effective.
  • Another advantage of this material is its - in contrast to rubber - largely linear Fe- derkennline, which excludes a stiffening of the spring in their work area, even under higher loads.
  • a uniformly high efficiency of elastic storage can be ensured, which is independent of whether the Mahlgut matterser is full or almost empty.
  • the unit can swing in the direction of all three degrees of freedom in operation.
  • the elastic support must at least join in these movements.
  • Each elastic element which has a main direction of action as a spring, can therefore also be subject to transverse forces perpendicular to its main direction of action. You can permanently weaken the elastic material or the spring.
  • the unit is therefore stored spatially. This means that it has elastic bearings whose main direction of action is directed in the direction of the three degrees of freedom of the assembly. This ensures that the respective bearing load is almost free of lateral forces.
  • Each individual bearing can thus be constructed simpler and achieve a longer service life. A simpler structure of the bearing in turn leads to a simplification of assembly.
  • a mounting of the assembly in the direction of all three degrees of freedom requires the arrangement of corresponding bearing surfaces on which the elastic material can be attached.
  • the unit must therefore have several, mostly flat surfaces. If the assembly is used in several different types of equipment, for example in different coffee machines, so more storage space for different installation situations may be required.
  • the assembly may have a frame or cage that provides these storage areas available.
  • the assembly is arranged in a largely closed housing. The surfaces of the walls of the housing can serve completely as storage areas.
  • the dynamic bedding modulus of the sheet-like elastic material (it corresponds to the dynamic stiffness of a spring) in addition to the volume density also results from the size of the bearing surface of the material, this construction thus offers a further possibility of variation in the dimensioning of the spring of the mass-spring system. For example, if only a small height is available, then the required dynamic Stiffness can be achieved not only by the bulk density of the material, but also by changing the size of the storage area.
  • a largely enclosed housing for the unit provides protection against the emission of airborne sound.
  • Such a unit is so not only structure-borne, but also airborne sound insulation.
  • Necessary openings on the one hand represent the discharge opening for the flour and an operating opening for filling the ground material container. If no closable collecting space for the flour is formed within the housing, the discharge opening must remain open.
  • the operating opening of the grinding stock container can be closed by a lid.
  • the housing can be closed in the region of the grinding stock with an airtight lid closing. On the one hand this counteracts the escape of airborne sound. On the other hand, the flavor of coffee beans can be maintained longer, in particular.
  • an improved airborne sound protection can be achieved according to a further advantageous embodiment of the invention in that the assembly is arranged in a double-shell housing of an inner housing and an outer housing.
  • the housing of the assembly can form the inner housing.
  • the double-shell construction of the inner and outer housings also offers advantages for the design of the mass-spring system.
  • the inner housing With an air gap between the inner and outer housing, the inner housing is the too resilient mass, which is elastically mounted relative to the outer housing.
  • an air gap of constant size is created between the two housings.
  • the elastic material to be arranged as a spring can accordingly also have a constant material thickness. It can therefore be cost-effectively punched out of a flat material of constant thickness, for example.
  • the dynamic bedding modulus of the spring element can be adjusted by varying its dimensions.
  • the arrangement of the elastic material is thus possible on the entire outer surface of the inner housing (or the entire inner surface of the outer housing) and in principle is not subject to any restrictions. This facilitates both the construction and the assembly of the elastic bearing.
  • a particularly high sound insulation causes according to a further advantageous embodiment of the invention, a detuning of the respective natural frequencies of the two housings against each other.
  • the walls of the inner housing and the outer housing may be formed differently thick.
  • different soft materials can be used for the outer and inner housings. Because of the higher concentrated loads experienced by the inner housing, it should be made of the harder material.
  • the two housings reliably receive different natural frequencies, so that upon reaching the natural frequency of the inner housing and the associated increased sound radiation via its walls, the natural frequency of the outer housing is reliably not achieved.
  • a likewise double-shell lid can close an operating opening in each case of the outer and inner housings.
  • a double-shell lid not only means a higher production cost, but for full effectiveness, he would have to close exactly both the outer and the inner casing tight. This can hardly be ensured constructively with reasonable effort. If the inner housing is made of a sturdier material than the softer outer housing, the cover serves at the same time as constructive stiffening of the outer housing in the area of the operating opening.
  • the entire air gap is available for the arrangement of the elastic material. Because of the large available storage area, it is possible to use as soft and thus highly effective elastic material as possible. In the aging process, however, this is subject to a greater tendency to creep, that is to say it deviates from the load over time. Thus, the effectiveness of the elastic storage can at least diminish over time.
  • the inner housing relative to the outer housing is therefore only partially stored. A partial or partial bearing generates higher individual loads per bearing and thus requires a harder elastic material that is subject to a much lower age-related creep. Thus, the effectiveness of elastic storage can be maintained long term. Due to the design arise on the housing structurally softer and harder areas.
  • Softer areas form, for example, planar wall sections which are not supported or stiffened by transverse walls or webs. Due to their constructive softness, they are good at insulating structure-borne noise.
  • the inner housing is decoupled at rigid portions of the housing by means of elastic material relative to the outer housing. Stiff portions of both the inner housing and the outer housing in particular represent the housing corners. There, the static weight and dynamic vibration forces can be reliably transmitted.
  • the elastic material is glued to one of the two housing, so either on the outer housing or on the inner housing.
  • the bonding then serves only to secure the position.
  • On a second bonding with the respective other housing can be dispensed with because of the spatial mounting of the inner housing in the outer housing.
  • the bearing elements are subject to almost no lateral forces, but are mainly loaded in their main direction of action and only on pressure. This promotes their life.
  • the effectiveness of the airborne sound insulation of the closed housing can, according to a further advantageous embodiment, be further improved by the fact that a sound-absorbing material is applied to the inside of the housing.
  • a sound-absorbing material is applied to the inside of the housing.
  • This is usually a porous coating, for example foam. It can basically be applied to the inside of the inner housing or the outer housing. If it is located in the outer housing, it must not fill the air gap between the inner and outer housing. It must rather maintain a movement possibility of the inner housing relative to the outer housing for all occurring during operation load cases, without touching it, so as not to affect the effectiveness of the elastic storage.
  • the motor is arranged within the Mahlgut actuallyers.
  • the grinding material container thus fulfills a double function, namely, on the one hand, the reception of the ground material and, on the other hand, that of an airborne sound housing for the engine.
  • the grist container must be dimensioned larger to accommodate the engine, but overall results in this arrangement, a considerable space savings, so that the mill receives a more compact design.
  • the separate insulating housing for the engine can be omitted, so that the manufacture of the mill cheaper.
  • the motor is attached to the grinding stock container.
  • Mahlgut simplyer sturdier form, to accommodate the additional load of the engine can.
  • At least one of the housing consists of a material with high internal damping. It is an inelastic, quasi gel-like material that hardly counteracts a restoring force on a force acting on it. Such a material is characterized by a high impact strength.
  • a soft polyurethane, thermoplastic polyethylene (TPE) or a hard silicone may be considered. These materials should be suitable for injection molding in terms of ease of processing.
  • the high internal damping causes a damping especially of high frequencies, which are considered in the perception of man as particularly unpleasant.
  • FIG. 1 shows an exploded view of a structural unit according to the invention without a cover
  • FIG. 2 is a plan view of the assembly
  • FIG. 3 shows a longitudinal section through the structural unit according to the section line N-II in FIG. 2
  • FIG. 4 shows a cross section through the structural unit according to the section line III-III in FIG.
  • FIG. 5 shows a detail view from FIG. 3.
  • the food mill according to the invention comprises a container 1, a grinder 2 and a drive 3. It is shown in FIG. 1 without a cover for a loading opening 10.
  • the container 1 is made of plastic and is double-shelled. It comprises an outer container 1 1 as an outer shell and an inner container 12 as an inner shell.
  • the inner container 12 also serves as Mahlgut actuallyer, in the interior 14, among other things, about one kilogram of coffee beans can be added.
  • the inner container 12, the grinder 2 and the drive 3 represent a structural unit and the outer container 12 a housing in the sense of claim 1.
  • the inner container 12 On one of its long sides, the inner container 12 has a mounting recess 17 and on its underside a circular discharge opening not visible in this illustration 15, which is aligned with an equally circular discharge opening 16 at the bottom of the outer container 1 1.
  • the grinder 2 consists of a flat, substantially cylindrical grinder housing 21 made of plastic. It contains, in a milling space 20, a fixed and stable centering disk 22 made of metal, a plastic plain bearing disk 23 for a milling cone 24 and a grinding ring 25 with a central feed opening 26.
  • the drive 3 includes in a housing of a receiving base 31 and a receiving upper part 32 an electric motor 33 airtight. He is elastically mounted on rubber elements, not shown, within the lower part 31 and upper part 32 with a small spring travel and acts via a gear from a worm 34 and a worm wheel 35 on a shaft 36. Both the motor 33 and the gear 34, 35 is in the Recording lower and upper part 31, 32 stored. The storage ensures the correct center distance and meshing angle and thus in addition to the reduced meshing noise high efficiency and long life of the engine 33 and gearbox 34, 35th
  • the lower and upper receiving parts 31, 32 are made of a plastic that is resistant to distortion. They are clipped in the mounting recess 17 on the inner container 12. At its opposite end, the receiving lower and upper parts 31, 32 are supported by tension on supports on the inner container 12, of which a support 37 can only be seen in FIG.
  • a knurled nut 39 is also arranged for not otherwise explained adjustment of the grinder 2.
  • the shaft 36 has at its the drive-side worm wheel 35 opposite output side end a square 38. It extends through the feed opening 26 of the grinding disk 25 and engages by means of the square 38 in the grinding cone 24 a.
  • the latter is rotatably mounted on the metal centering disk 22 and the mill housing 21 via the plain bearing disk 23.
  • the plain bearing washer 23 is made of a high-density polyethylene (HDPE) or a polyoxymethylene / polyacetate (POM) so that it does not liquefy (weld) under friction on the metal.
  • HDPE high-density polyethylene
  • POM polyoxymethylene / polyacetate
  • the sliding bearing in the grinder 2 makes a ball bearing dispensable, which is more susceptible to contamination by small particles.
  • the grinder 2 and the drive 3 are completely disposed within the container 1 and there in the interior 14 of the inner container 12.
  • a direct connection of the grinder 2 or the drive 3 to the outer housing 1 1 does not exist.
  • a structure-borne sound excitation by vibration or airborne noise of both the grinder 2 and the drive 3 gets so only the inner container 12, airborne sound only a lid 13 (see Figure 3).
  • Figure 2 provides a plan view of the assembly to illustrate the relative position of the drive 3 and the grinder 2 within the container 1, and also illustrates the course of the sectional views of Figures 3 and 4.
  • FIG. 3 illustrates in a longitudinal section the relative position of the individual parts shown in Figure 1 to each other.
  • the outer container 1 1 takes the inner container 12 and the Mahlgut actuallyer completely on to form a substantially double-shell container 1.
  • the lid 13 closes the container 1 airtight.
  • the partially cut receiving upper part 32 and lower part 31 give the view freely on the motor 33 from the direction of the connected screw 34. It is on the worm wheel 35 into engagement the shaft 36 which drives the grinding cone 24 through the feed opening 26 of the fixed grinding ring 25 therethrough.
  • the shaft 36 is rotatably mounted in the grinder housing 21.
  • the grinder housing 21 is disposed below the inner container 12 and closes the discharge opening 15. It forms as it were the lower continuation and protrudes with a retracted storage area 27 still through the discharge opening 16 of the outer container 1 1 therethrough.
  • the container 1 In the lower region of the container 1 so its Doppelschaltechnik is formed by the outer container 1 1 on the one hand and the grinder housing 21 on the other.
  • the container 1 At the storage section 27 and the discharge opening 28 arranged thereon for the ground material, the container 1 is not designed with double-shelled construction. This is followed by an unillustrated shaft of the brewing chamber, which ensures sound insulation.
  • the sound insulation in the opposite region of the cover 13 is described in detail in the application 2005E01366.
  • the interior 14 is more or less filled with coffee beans. So they surround the drive almost completely (see also Figure 4).
  • the coffee beans Via a funnel section 19 on the inner container 12 above its discharge opening 15, the coffee beans reach the feed opening 26 in the grinding ring 25. By gravity, they slip between the grinding ring 25 and the grinding cone 24, where they are first broken and then ground. As regrind, they pass into a receiving space 29 below the grinding ring 25. From there, the ground material falls through the centering disk 22 and the outlet opening 28 into a shaft, not shown, to the brewing chamber.
  • the spokes of the centering disc 22 (see Figure 1) are formed in a roof shape in cross section, so that no ground coffee can deposit on them.
  • FIG. 5 shows a detailed view from FIG. 3, specifically where the lid 13 strikes the container 1.
  • FIG. 5 shows the upper edge of the outer container 1 1 and the inner container 12.
  • the outer container 1 1 forms there a collar 1 1 1, which protrudes from the outer container 1 1 inwards. It extends over the gap 18 across over the upper edge of the inner container 12 over without coming into contact with this.
  • Approximately in the continuation of the wall of the outer container 1 1 connects to the collar 1 1 1 an approach 1 12, which consists of a taper 1 13 and a rib 1 14.
  • the collar 1 1 1 thus covers the gap 18 between the outer container 1 1 and the inner container 12.
  • the collar 1 1 1 1 rotates around the entire inner circumference of the outer container 12, the inner container 12 can be mounted in the outer container 1 1.
  • the outer container 1 1 is soft enough for reasons mentioned later, so that the edge of the inner container 12 can be snapped in the assembly behind the collar 1 1 1.
  • the lid 13 comprises a circumferential around its entire periphery edge bar 131, to which a sealing strip 132 is attached. Outside its attachment in the edge beam 131 of the sealing strip 132 forms in a direction perpendicular to the plane of the lid 13, a throat 133 with a subsequent thickening 134. The throat 133 and the thickening 134 form on the respective outer side of a relief which is designed inversely to the inside of the neck 1 12. This shape of the sealing strip 132 together with a matched softness of its material allows the sealing strip 132 with the approach 1 12 can enter into an airtight mechanical connection between the lid 13 and outer container 1 1.
  • the drive 3 forms with its engine and transmission noises a first emission source for airborne and structure-borne noise. He is rigidly attached to the inner container 12.
  • the use of the worm 34 reduces the airborne sound radiation of the drive 3, because a worm gear, in contrast to the otherwise commonly used planetary gearboxes, despite the fast-running motor 33, does not emit any significant meshing noises.
  • Vibrations of the motor 33 are transmitted via its rigid mounting in the receiving lower and upper part 31, 32 directly to the inner container 12. He also experiences vibrations through the grinder 2.
  • the structure-borne sound insulation of the motor 33 is therefore described below together with the grinder 2.
  • the airborne sound radiation of the high-speed electric motor 33, in particular its collector noise, is insulated by its airtight encapsulation in the lower and upper receiving part 31, 32. A second airtight encapsulation is the container 1 with the lid 13.
  • the motor 33 is thus double airborne sound insulation. A sound propagation of the vibrations emitted by the engine 33 in its environment is thus effectively prevented.
  • a second emission source is the grinder 2.
  • the beans are first broken between the grinding cone 24 and the grinding ring 25 and then finely ground.
  • These two processes are among the main emission sources of an automatic coffee machine. On their insulation so the main focus of the construction.
  • the crushing and grinding noises are only so far to insulate that a user can still hear the grinding process outside the machine acoustically. This meets his expectation of noise during operation of the coffee machine.
  • the noise reduction is therefore primarily aimed at the perceived as unpleasant high-frequency noise, including the engine 33 (s.o.).
  • the grinding cone 24 and the grinding ring 25 are mounted in the grinder housing 21 and thus indirectly on the inner container 12.
  • all emission sources which generate structure-borne noise by vibration are mounted on the inner container 12.
  • the inner shell 12, 21 is with respect to the outer shell 1 1 vibration technology, namely elastically decoupled to avoid transmission of vibrations from the inner shell 12, 21 on the outer shell 1 1.
  • the transmission path of the vibrations is therefore interrupted between the inner shell 12, 21 and the outer shell 1 1. This interruption causes the vibrations from the inner shell not carried on the outer shell 1 1 and radiated as airborne sound or transmitted from there to other components of the coffee machine. Thus, other components are not excited to vibrate and radiate no airborne sound.
  • the elastic material acts as a spring, which absorbs a mass, namely the inner shell 12, 21, against a "base", in this case the outer shell 1 1.
  • the vibrations of the inner shell 12, 21 are, as it were, "swallowed” by the elastic material 41, so that they are not transferred to the outer shell 1 1.
  • the strips 41 are punched out of a plate material, which is equipped on one side adhesive.
  • the strips 41 are glued to the inside of the outer container 1 1, so that they are only in touching contact with the inner container 12 without being firmly connected to it.
  • a fixed connection is not necessary because the inner container 12 is held in four directions (see Figure 2), thus defined in the two horizontal degrees of freedom. Due to the lack of permanent connection between the strip 41 and the inner container 12, this can be easily removed for repair purposes, for example.
  • the vertical degree of freedom elastic bearing plates 42 of the same material as the strips 41 in the region of the discharge opening 16 on the inside of the outer shell 1 1 glued (see Fig. 3 and 4). They surround all sides the retracted bearing portion 27 of the mill housing 21st
  • the elastic strips 41 and plates 42 can be easily assembled due to their self-adhesive equipment.
  • the required smooth surfaces provide the outer shell 1 1 and the inner shell 12, 21st Due to the constant distance of the containers 1 1, 12 from each other, the strips 41 and the plates 42 can each be performed in the same thickness and therefore cost-effectively punched or cut from a plate material.
  • the outer shell 1 1 are mounted in the corner regions on rigid sections of the inner shell 12, 21 and the outer shell 1 1 in order to achieve the greatest possible effectiveness. Because the low compliance of the "base", the outer shell 1 1 in their corners and at its discharge opening 16, the elastic bearings 41, 42 unfold their resilient, structure-borne noise insulating effect "Softer” and can easily give in to a load. Thus, they have a greater internal damping, which causes the outer container 1 to "swallow" sound. When subjected to airborne sound, the outer container 1 1 can not be made to vibrate, ie it does not emit any airborne sound itself also a contribution to a good airborne sound insulation.
  • This effect is supported by the use of Santoprene ® as a material for the outer container 1 1.
  • This TPE has a high internal damping and is relatively soft.
  • the compared to the material for the inner container 12 higher softness is unproblematic in the outer container 1 1, because he has to record in contrast to the inner container 12 no significant point loads, but only area loads from the strips 41 and plates 42 to constructively stiffer container sections.
  • the lid 13 connects exclusively to the outer container 1 1 (see Fig. 5). By virtue of its connection to the upper edge of the outer container 1 1 via its stable edge bar 131, it stiffens the relatively soft outer container 11 in the region of its loading opening 10. It is not in direct contact with the inner container 12. As a result, vibrations and vibrations can not occur to be transferred to him. A structure-borne sound insulation in the plane of the cover 13 is therefore unnecessary, a double-shell construction of the lid 13 so not required.
  • the cover 13 is essentially the airborne sound insulation. Therefore, it closes on the one hand airtight to the Au- On the other hand, also made of a material with a high internal damping, so the "sound swallows".

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Mechanical Engineering (AREA)
  • Apparatus For Making Beverages (AREA)

Abstract

Moulin à denrées alimentaires, en particulier moulin à café dans une machine à café entièrement automatique, comportant une unité structurale qui comprend un récipient à denrées à moudre (1), un mécanisme (2) situé dans une chambre de mécanisme et un moteur d'entraînement (3) pour le mécanisme et qui est montée de manière élastique dans un boîtier. Ledit moulin est amélioré par le fait que le support élastique est constitué d'une matière (41; 42) qui peut être collée.
PCT/EP2007/056060 2006-07-14 2007-06-19 Mécanisme de moulin à amortissement du bruit de corps pour un moulin à denrées alimentaires Ceased WO2008006672A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006032710.1 2006-07-14
DE200610032710 DE102006032710A1 (de) 2006-07-14 2006-07-14 Körperschallgedämmtes Mahlwerk für eine Lebensmittelmühle

Publications (1)

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WO2008006672A1 true WO2008006672A1 (fr) 2008-01-17

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PCT/EP2007/056060 Ceased WO2008006672A1 (fr) 2006-07-14 2007-06-19 Mécanisme de moulin à amortissement du bruit de corps pour un moulin à denrées alimentaires

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WO (1) WO2008006672A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010000239B4 (de) * 2010-01-28 2020-12-17 SEVERIN ELEKTROGERÄTE GmbH Elektrische Kaffeemaschine
DE202012102131U1 (de) 2012-06-12 2013-09-18 Eugster/Frismag Ag Kaffeemaschine
DE102016101839A1 (de) 2016-02-03 2017-08-03 Eugster/Frismag Ag Mahlwerk, Mühle, Kaffeezubereitungsvorrichtung mit Mühle sowie Mahlverfahren

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2120534A (en) * 1982-05-19 1983-12-07 Tokyo Shibaura Electric Co Coffee maker
WO2002028244A1 (fr) * 2000-10-02 2002-04-11 Kenneth Hou Jensen Aps Appareil et procede permettant de doser et de moudre des grains de cafe
US20020047061A1 (en) * 2000-07-06 2002-04-25 Wulfman Edward I. Coffee grinder silencer

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2120534A (en) * 1982-05-19 1983-12-07 Tokyo Shibaura Electric Co Coffee maker
US20020047061A1 (en) * 2000-07-06 2002-04-25 Wulfman Edward I. Coffee grinder silencer
WO2002028244A1 (fr) * 2000-10-02 2002-04-11 Kenneth Hou Jensen Aps Appareil et procede permettant de doser et de moudre des grains de cafe

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