Swing anchor pump

Description

State of the art

[0001] The invention relates to a vibrating armature pump according to claim 1, a beverage dispenser according to claim 13, a piston part according to claim 14 and a working piston according to claim 15.

[0002] In particular, DE 10 2010 044 775 A1 already proposes a vibrating armature pump which has a two-part working piston consisting of a piston part and a magnetic part, which are designed separately from each other and are pressed together only by spring force.

[0003] EP0288216 A1 discloses another oscillating armature pump from the prior art.

[0004] The object of the invention is, in particular, to provide a generic device with improved properties with regard to higher stability, component savings, and / or increased user-friendliness. This object is achieved according to the invention by the features of claim 1, while advantageous embodiments and further developments of the invention can be found in the dependent claims. Advantages of the invention

[0005] The invention relates to a vibrating armature pump, particularly for a beverage vending machine, for pumping a liquid, comprising a pressure cylinder, a working cylinder, and a working piston. The working piston has a piston section designed to be guided within the pressure cylinder and, together with the pressure cylinder, to define a pressure chamber. The working piston further comprises a magnetic section designed to be guided within the working cylinder. The working piston is designed to be set into a stroke, particularly an oscillating, motion along a working axis in order to increase and / or decrease the volume of the pressure chamber.

[0006] It is proposed that the working piston have at least one first connection point designed to connect the piston part and the magnet part, particularly directly, and to transmit forces of any direction along the working axis from the magnet part to the piston part. Connecting the components can achieve increased stability and improved force transmission. Furthermore, it can prevent the piston part and magnet part from striking each other, which can lead to reduced noise. This can also result in a reduced number of components or material savings. In particular, the number of springs required to move the working piston to a rest position can be reduced, or springs can be made shorter if their sole purpose is to prevent the working piston from striking the end of the cylinder.

[0007] The beverage dispenser is specifically designed to dispense at least one beverage freely from a beverage outlet, whereby it is specifically designed that the beverage is filled into an open beverage container, in particular a dish such as a glass, cup, jug, or mug, or alternatively collected in a drip tray of the beverage dispenser. The liquid is specifically a liquid required for beverage preparation, in particular water, or alternatively hot water. Alternatively, the liquid may be a ready-made beverage. In particular, the beverage dispenser may be designed, depending on the operating program, to pump different liquids using the vibrating armature pump, wherein at least one of these liquids is a rinsing liquid.

[0008] The pressure chamber and / or the pressure cylinder have, in particular, at least one outlet designed to allow pressurized liquid to escape from the pressure cylinder after the action of the piston. Preferably, the outlet is located on one side, more preferably an end face, or alternatively a side of the cylinder, of the pressure cylinder, preferably opposite the side through which the piston is inserted. The pressure cylinder has, in particular, a circular cylindrical shape. Alternatively, it is conceivable that the pressure cylinder has a tapered shape, wherein, in particular, the inner diameter of the pressure cylinder decreases from the side through which the piston is inserted. In particular, the inner diameter differs from one end of the pressure cylinder to the other end by a maximum of 0.01 mm, more specifically a maximum of 0.03 mm, and preferably a maximum of 0.1 mm.

[0009] For example, the piston part and the magnet part are made of different materials. Alternatively, it is possible that the piston part and the magnet part are made of the same material.

[0010] For example, the piston part is made of a material that is chemically inert, at least essentially, to water, in particular stainless steel or plastic.

[0011] Preferably, the magnetic component is at least partially, in particular at least 50%, for example at least 80%, preferably at least 90%, and in particular completely, made of a magnetic or magnetizable material. Alternatively, the magnetic component could have at least one, in particular non-magnetic, support body to which at least one permanent magnet is attached and / or in which at least one permanent magnet is encapsulated. In particular, the magnetic component has permanent magnetization. Alternatively, it is conceivable that the magnetic component is made of a ferromagnetic or paramagnetic material. For example, the magnetic component is designed as a turned part, i.e., manufactured in particular at least partially by means of a turning process and / or a CNC process.

[0012] Preferably, the oscillating armature pump comprises at least one coil unit designed to deflect the magnetic element, and thus in particular the working piston, from a rest position and thereby set it into stroke motion, at least when a coil of the coil unit is energized. In particular, the oscillating armature pump comprises a spring unit, with in particular at least one coil spring, designed to exert a force on the working piston in a deflected state from its rest position, acting in the direction of the rest position. In particular, the spring unit comprises at least one compression spring arranged on an end face of the working cylinder. In particular, the spring unit comprises two compression springs, each arranged on one of the opposite end faces of the working cylinder.Alternatively or additionally, it is conceivable that the spring unit has at least one tension spring, or that the spring unit has at least one spring which is intended to act as a tension spring or as a compression spring depending on a state of the oscillating armature pump, in particular depending on a position of the working piston.

[0013] The working axis is preferably parallel to a central axis of the working cylinder and / or a central axis of the pressure cylinder and / or corresponds to one or advantageously both of these central axes.

[0014] The connection point is preferably designed as a force-fit or form-fit connection, in particular by crimping and / or riveting. Alternatively, the connection point can be designed as a material-fit connection, in particular as a welded, soldered or adhesive bonded joint.

[0015] The term "intended" is understood to mean, in particular, specifically programmed, designed, and / or equipped. The fact that an object is intended for a specific function is understood to mean, in particular, that the object fulfills and / or executes this specific function in at least one application and / or operating state.

[0016] Furthermore, it is proposed that the piston component be a deep-drawn part manufactured using a deep-drawing process. This allows for particularly simple manufacturing. In particular, thinner walls and thus larger inner diameters, or alternatively smaller outer diameters, and / or a lower weight can be achieved compared to a piston component manufactured using a turning process.

[0017] According to a further inventive concept, a vibrating armature pump, in particular for a beverage vending machine, for pumping a liquid, is proposed, comprising a pressure cylinder, a working cylinder, and a working piston, which has a piston part that is provided to be guided in the pressure cylinder and, together with the pressure cylinder, to define a pressure chamber, and which has a magnetic part that is provided to be guided in the working cylinder, wherein the working piston is provided to be set into a stroke movement, in particular an oscillating movement, along a working axis in order to increase and / or decrease a volume of the pressure chamber, wherein the piston part is a deep-drawn part that is manufactured by means of a deep-drawing process.

[0018] The previously described further developments also apply to this inventive idea. The further development variants relate to all previously described inventive ideas.

[0019] Furthermore, it is proposed that the piston part be at least substantially cylindrical and have a diameter, in particular an outer diameter, of less than 6 mm, especially less than 5 mm, for example less than 4.5 mm. This allows, in particular, higher pressures to be achieved in the pressure chamber and / or it allows a lower force to be applied to the working piston, in particular the magnetic part, in order to achieve the same pressure. A reduced volume in the pressure cylinder can be compensated for, in particular, by a longer stroke or by a higher number of stroke cycles.

[0020] According to a further embodiment, it is proposed that the piston section has an increasing outer diameter starting from an end located in the pressure chamber when installed. In particular, the piston section is at least partially conical. Specifically, the smallest and largest outer diameters of the piston section differ, particularly at least in the portion intended for insertion into the pressure cylinder, by a maximum of 0.1 mm, more specifically by a maximum of 0.03 mm, preferably by a maximum of 0.01 mm. Specifically, the smallest and largest outer diameters of the piston section differ, particularly at least in the portion intended for insertion into the pressure cylinder, by a maximum of 0.01 mm, more specifically by a maximum of 0.02 mm, preferably by a maximum of 0.05 mm. This can result in material savings and / or a higher pressure in the pressure cylinder.

[0021] Furthermore, it is proposed that the piston part be designed at least substantially as a hollow cylinder and have a wall thickness of less than 0.5 mm, in particular less than 0.4 mm, advantageously less than 0.3 mm. This will result in significant material savings.

[0022] Furthermore, the oscillating armature pump can have at least one rod seal designed to seal the pressure chamber and / or the pressure cylinder against the piston. In particular, the rod seal is designed to surround the piston in an annular manner when the pump is ready for operation. Specifically, the rod seal is arranged and / or anchored in a groove and / or slot in a wall of the pressure cylinder. Alternatively, it is conceivable that the rod seal is arranged and / or anchored to the piston. The rod seal allows, particularly compared to a ring seal, a seal against varying outer diameters of the piston and / or inner diameters of the pressure cylinder.

[0023] According to a further embodiment, the working piston can have at least one compensating element arranged between the magnetic part and the piston part, which has a compensating opening designed to fluidically connect a first working chamber and a second working chamber in the working cylinder, which are separated from each other by the magnetic part, in particular so that the fluid flows through the magnetic part when the working piston moves. This ensures, in particular, reliable operation of the pump. Specifically, the magnetic part has at least one longitudinal recess, in particular a longitudinal bore, designed to fluidically connect the end faces of the magnetic part.

[0024] Preferably, the compensating piece is formed integrally with the piston part, which in particular allows for a low number of components. In particular, the piston part and the compensating piece are manufactured from a single piece.

[0025] Alternatively, the compensating piece could be designed as part of the magnet component. Furthermore, the compensating piece could be manufactured independently of the magnet component and the piston component, connecting the magnet component and the piston component via the connection point and another connection point.

[0026] Furthermore, it is proposed that the working piston have at least one inlet valve, which is arranged in a cavity of the piston part and which is designed to regulate the passage of fluid from the working cylinder into the pressure cylinder. This allows for a particularly space-saving design.

[0027] According to alternative embodiments, the pressure cylinder can have an inlet valve, particularly on a cylindrical surface, wherein, preferably, the piston part is designed to be sealed against the pressure chamber.

[0028] According to a preferred embodiment, it is proposed that the inlet valve has a valve spring, preferably designed as a coil spring, with a conical shape. In particular, the valve spring is designed as a compression spring, which is intended to draw a sealing element into a sealing seat formed on the piston part. This allows for particularly low noise levels. Alternatively, the valve spring can be designed as a tension spring and / or have a cylindrical shape. Furthermore, a coffee machine, in particular a capsule coffee machine, also called a coffee maker, is proposed, which has a previously described vibrating armature pump. Drawings

[0029] Further advantages will become apparent from the following description of the drawings. The drawings illustrate an embodiment of the invention. The drawings, the description, and the claims contain numerous features in combination. A person skilled in the art will expediently consider the features individually and combine them into meaningful further combinations.

[0030] They show: Fig. 1 a beverage vending machine according to the invention in a schematic representation, Fig. 2 a vibrating armature pump according to the invention with a working piston according to the invention in a schematic sectional view, Fig. 3 a piston part according to the invention in a perspective sectional view, Fig. 4 the working piston according to Figure 2 in a schematic sectional view, Fig. 5 a working piston according to the invention in a schematic sectional view and Fig. 6 a working piston according to the invention in a schematic sectional view. Description of the exemplary implementations

[0031] Figure 1 Figure 1 shows a beverage vending machine 10. The beverage vending machine 10 is designed as a coffee machine. The beverage vending machine 10 is designed as a capsule coffee machine. The beverage vending machine 10 has a control unit 12. Furthermore, the beverage vending machine 10 has a dispensing unit 14 by means of which a beverage can be dispensed. The beverage vending machine 10 has a base 18. The base 18 is designed, in particular, as a sieve to catch, for example, any overflowing beverage. Between the base 18 and the dispensing unit 14, a storage space 16, for example, for a beverage container, in particular a cup or a mug, is arranged.

[0032] Furthermore, the beverage dispenser 10 features a vibratory armature pump 20. The vibratory armature pump 20 is designed to pump a liquid. The vibratory armature pump 20 is designed to force heated water under pressure into a coffee dosing capsule.

[0033] The vibrating armature pump 20 has a pressure cylinder 22 (see Figure 2 Furthermore, the oscillating armature pump 20 has a working cylinder 24. The pressure cylinder 22 has a smaller inner diameter than the working cylinder 24. The inner diameter of the working cylinder 24 is three to five times larger than the inner diameter of the pressure cylinder 22. The oscillating armature pump 20 also has a working piston 30 (see also Fig. 4 The working piston 30 has a piston section 32, which is guided in the pressure cylinder 22 and, together with the pressure cylinder 22, defines a pressure chamber 26. The working piston 30 also has a magnetic section 34, which is guided in the working cylinder 24. The working piston 30 is designed to be set into a stroke movement, in particular an oscillating movement, along a working axis 31 in order to alternately increase and decrease the volume of the pressure chamber 26.

[0034] The working piston 30 has at least a first connection point 36 which is intended to connect the piston part 32 and the magnet part 34, in particular directly, to each other and to transmit forces of any direction along the working axis 31 from the magnet part 34 to the piston part 32.

[0035] The piston part 32 is a deep-drawn part, manufactured using a deep-drawing process (see below). Fig. 3 The magnetic part 34 is designed as a turned part. The magnetic part 34 has a crimp collar 342. The connection point 36 has a flange 322. The connection point 36 is achieved by forming the crimp collar 342. The connection point 36 has a positive-locking connection between the piston part 32 and the magnetic part 34. After forming, the crimp collar 342, together with the magnetic part 34, forms a groove that encloses the flange 322 of the piston part 32.

[0036] Alternatively, the piston part can be attached to the magnet part 34 by means of a simple press fit. According to another alternative, the piston part can have a flange, while the magnet part is flat, and the flange is intended to be soldered or welded to the magnet part.

[0037] The piston part 32 is at least essentially cylindrical and has an outer diameter between 5.6 mm and 4.2 mm.

[0038] The piston part 32 has an increasing outer diameter, particularly due to its manufacture as a deep-drawn part, starting from the pressure chamber 26.

[0039] The piston part 32 is at least essentially hollow cylindrical and has a wall thickness of 0.25 mm.

[0040] The oscillating armature pump 20 also has a rod seal 23, which is designed to seal the pressure chamber 26 against the piston part 32.

[0041] The working piston 30 has a compensating piece 38 arranged between the magnetic part 34 and the piston part 32. The compensating piece 38 has a compensating opening 39, which is designed to fluidically connect a first working chamber 242 and a second working chamber 244 in the working cylinder 24, which are spatially separated by the working piston 30, in particular by the magnetic part 34. The fluid can flow through the magnetic part 34 when the working piston 30 moves. The magnetic part 34 is cylindrical, in particular hollow cylindrical. The magnetic part 34 has a through-opening 35, in particular a central bore. For example, the through-opening 35 extends from one side of the magnetic part 34 facing the first working chamber 242 to one side of the magnetic part 34 facing the second working chamber 244.The compensating opening 39 is designed in particular as a transverse bore, especially perpendicular to the working axis 31. For example, the compensating piece 38 has at least four compensating openings 39, i.e., in particular two intersecting transverse bores. The first working chamber 242 is located on a side of the magnetic part 34 facing away from the pressure cylinder 22. The second working chamber 244 is located on a side of the magnetic part 34 facing away from the pressure cylinder 22.

[0042] The compensating piece 38 has a hollow cylindrical shape. The compensating piece 38 has a larger outer diameter than the piston part 32. The compensating piece 38 is also referred to as a cup. The compensating piece 38 has an annular area that connects to the piston part 32. The flange 322 of the connection point 36 is located on the compensating piece 38.

[0043] The compensating piece 38 is formed integrally with the piston part 32, specifically as a single workpiece. The compensating piece 38, together with the piston part 32, is manufactured by deep drawing from a single green body.

[0044] The working piston 30 has an inlet valve 40, which is arranged in a cavity of the piston part 32 and is designed to regulate the passage of fluid from the working cylinder 24 into the pressure cylinder 22. The cavity extends lengthwise through the piston part 32.

[0045] The inlet valve 40 has a valve spring 42 with a conical shape. The valve spring 42 is anchored to the piston part 32 and is designed to press a sealing element 44 of the inlet valve 40 against a sealing seat 33 of the piston part 32. The sealing seat 33 is formed by a valve seat. The sealing seat 33 is formed integrally with the piston part 32. The sealing seat 33 is manufactured by deep drawing. The sealing seat 33 is formed by a conical, inwardly tapering end section of the piston part 32. However, it would also be conceivable that the sealing seat 33 is formed by a separate component that is integrally molded onto the piston part 32. The oscillating armature pump 20 has a coil unit 60 which is designed, at least when current is flowing, to deflect the solenoid part 34 from a rest position and thus set it into stroke motion.The coil unit 60 includes, in addition to a coil, in particular a coil core which frames the coil in order to focus an external magnetic field of the coil (not shown in detail).

[0046] The oscillating armature pump 20 has a spring assembly 62 designed to generate forces to move the working piston 30 to its rest position. The spring assembly 62 has a first spring 64 located in the first working chamber 242. The spring assembly 62 has a second spring 66 located in the second working chamber 244. The first spring 64 is designed as a compression spring and is designed to push the magnetic element 34 towards the second working chamber 244. The second spring 66 is also designed as a compression spring and is designed to push the magnetic element 34 towards the first working chamber 242. The springs 64 and 66 are each designed as coil springs.

[0047] According to alternative designs, the spring unit has only a single spring.

[0048] During a working cycle of the oscillating armature pump 20, the working piston 30 first performs a reverse movement. During this reverse movement, the working piston 30 is moved out of the pressure cylinder 22, thus increasing the volume of the pressure chamber 26. An outlet of the pressure chamber 26 has an outlet valve 50 that allows only the flow of liquid out of the pressure chamber 26. This creates a vacuum in the pressure chamber 26, which causes the inlet valve 40 to open. The liquid now flows from the working cylinder 24, through the cavity in the piston section 32 and the inlet valve 40, into the pressure chamber 26.

[0049] During the reverse movement, some of the liquid continues to flow from the first working chamber 242 into the second working chamber 244 through the through-opening 35 in the magnet part 34 and the compensating opening 39 in the compensating piece 38. This enables pressure equalization between the first and the second working chambers 242, 244.

[0050] The reverse movement is actively driven, for example, by a force exerted by the coil unit 60, at least on the magnet part 34, to move the working piston from its rest position. Alternatively, the force can be a restoring force from the spring unit 62, which drives the working piston back into its rest position. Following the reverse movement, a forward movement is performed. During the forward movement, the working piston 30 is moved into the pressure cylinder 22, thus reducing the volume of the pressure chamber 26. This creates overpressure in the pressure chamber 26, which causes the inlet valve 40 to close. When a defined pressure is reached, the outlet valve 50 opens, allowing the fluid to escape from the pressure chamber 26 via the outlet valve 50.

[0051] The working cylinder 24 has an inlet 52 that supplies fluid from a reservoir. The inlet 52 of the working cylinder 24 is located at an end of the working cylinder 24 opposite the pressure cylinder 22. During forward movement, fluid continues to flow through the inlet 52 into the first working chamber 242. Additionally, to equalize pressure, fluid flows from the second working chamber 244 through the equalization port 39 and the through-port 35 into the first working chamber 242.

[0052] The forward movement is driven, for example, by a force that is a restoring force of the spring unit 62, which drives the working piston back to its rest position. Alternatively or additionally, the force can be exerted by the coil unit 60, at least on the magnet part 34, to move the working piston from its rest position. According to an alternative embodiment, it is conceivable that during an oscillating stroke movement, the coil unit drives the magnet part alternately in different directions, in particular by reversing the current direction in the coil and in the case of an embodiment of the magnet part with permanent magnetization.

[0053] In the Figures 5 to 6Two further embodiments of the invention, in particular of the working piston, are shown. To distinguish between the embodiments, the letters a or b are appended to the reference numerals of the further embodiments, whereby the same reference numerals are used for identical or at least functionally related components. The further description is essentially limited to the differences between the embodiments, whereby with regard to identical components, features and functions, reference is made to the description of the exemplary embodiment of the Figures 1 to 4 Reference can be made to the drawings and / or the description of the embodiment of the [document / model]. With regard to identically designated components, especially those with the same reference numerals, reference can also be made to the drawings and / or the description of the embodiment. Figures 1 to 4 be referred.

[0054] Figure 5Figure 1 shows an alternative working piston 30a with a magnetic part 34a and a piston part 32a. The working piston 30a has a connection point 36a. The working piston 30a also has a compensating piece 38a. The compensating piece 38a is formed integrally with the magnetic part 34a. The connection point 36a is formed between the compensating piece 38a and the piston part 32a. The piston part 32a has a flange 322a. The compensating piece 38a has a crimp collar 342. After the flange 322a is applied and the crimp collar 342 is formed, the crimp collar 342 positively engages the flange 322a.

[0055] Figure 6 shows another alternative working piston 30b. In contrast to a design according to Figures 1 to 4A magnetic part 34b of the working piston 30b has a magnetic collar 344b. The magnetic collar 344b is cylindrical, or alternatively conical, and extends parallel to a compensating piece 38b. The magnetic collar 344b surrounds the compensating piece 38b. The magnetic collar 344b serves to increase the magnetic mass of the working piston 30b in order to achieve higher forces during a stroke movement of the working piston 30b. A second spring (66 in Figure 2 ) a spring unit for setting a rest position of the working piston 30b can be arranged between the magnetic collar 344b and the compensating piece 38b.

[0056] According to further embodiments, it is conceivable that the compensating piece is designed separately from both the piston part and the magnet part. In such an embodiment, the working piston can have two connection points, wherein the magnet part is connected to the compensating piece at a first connection point and the compensating piece is connected to the piston part at a second connection point. Reference symbol list

[0057] 10 vending machine 34 Magnetic part 12 Control unit 342 Crimp collar 14 Output unit 344 Magnetic collar 16 Parking space 35 Passage opening 18 Installation area 36 liaison point 20 Oscillating armature pump 38 Compensating piece 22 Pressure cylinder 39 Compensation opening 23 Rod seal 40 Inlet valve 24 Working cylinder 42 valve spring 242 Chamber of Labour 44 Sealing body 244 Chamber of Labour 50 outlet valve 26 hyperbaric chamber 52 inlet 30 working piston 60 coil unit 31 Working axis 62 spring unit 32 piston part 64 Feather 322 brim 66 Feather 33 sealing seat

Claims

1. Oscillating armature pump, in particular for a beverage machine (10), for conveying a liquid, having - a pressure cylinder (22), - a working cylinder (24), - a working piston (30) comprising a piston part (32) that is configured to be guided in the pressure cylinder (22) and to delimit a pressure chamber (26) together with the pressure cylinder (22), and comprising a magnet part (34) that is configured to be guided in the working cylinder (24), the working piston (30) being configured to be set in stroke motion, in particular oscillating stroke motion, along a working axis (31) in order to enlarge and / or reduce a volume of the pressure chamber (26), wherein the working piston (30) has at least one first connection point (36) that is configured to, in particular directly, connect the piston part (32) and the magnet part (34) to one another and to transmit forces having any direction from the magnet part (34) to the piston part (32) along the working axis (31), characterized in that the working piston (30) has at least one inlet valve (40), which is arranged in a cavity of the piston part (32) and is configured to closed-loop control a passage of the liquid out of the working cylinder (24) into the pressure cylinder (22), wherein the inlet valve (40) comprises a valve spring (42), the valve spring (42) being realized as a compression spring, which is configured to pull a sealing body (44) into a sealing seat (33) that is moulded on the piston part (32), in particular wherein the piston part (32) is a deep-drawn part manufactured by a deep-drawing procedure.

2. Oscillating armature pump as claimed in claim 1 or 2, characterized in that the piston part (32) is realized in an at least substantially cylindrical shape and has a diameter of less than 6 mm.

3. Oscillating armature pump as claimed in any one of the preceding claims, characterized in that the piston part (32) has an outer diameter that increases starting from the pressure chamber (26).

4. Oscillating armature pump as claimed in any one of the preceding claims, characterized in that the piston part (32) is realized in an at least substantially hollow-cylindrical shape and has a wall thickness of less than 0.5 mm.

5. Oscillating armature pump as claimed in any one of the preceding claims, characterized by at least one rod seal (23) that is configured to seal the pressure chamber (26) with respect to the piston part (32).

6. Oscillating armature pump as claimed in any one of the preceding claims, characterized in that the working piston (30) has at least one compensation piece (38) that is arranged between the magnet part (34) and the piston part (32) and has a compensation opening (39) configured to fluidically interconnect a first working chamber (242) and a second working chamber (244) in the working cylinder (24), which are separated from one another by the magnet part (34), in particular in such a way that the liquid rinses the magnet part (34) throughout when the working piston (30) moves.

7. Oscillating armature pump as claimed in claim 6, characterized in that the compensation piece (38) is realized integrally with the piston part (32).

8. Oscillating armature pump as claimed in claim 1, characterized in that the inlet valve (40) comprises the valve spring (42) having a conical or partially cylindrical shape.

9. Oscillating armature pump as claimed in any one of the preceding claims, characterized by at least one coil unit (60), which is configured, at least in a state when current flows through a coil of the coil unit (60), to deflect the magnet part (34) out of a rest position and thus to set the magnet part (34) into the stroke motion.

10. Oscillating armature pump as claimed in any one of the preceding claims, characterized by a spring unit (62), which is configured to generate forces that are provided to move the working piston (30) into the rest position.

11. Beverage machine, in particular coffee machine, having an oscillating armature pump (20) as claimed in any one of the preceding claims.