Furniture drive with electric drive motor and brake device

Abstract

A furniture drive with an electric drive motor and a brake device, wherein the drive motor has an output shaft which protrudes beyond the motor housing, wherein the brake device has at least one brake element and an accumulator, wherein the accumulator permanently applies a brake force to a friction surface of the at least one brake element, and wherein the accumulator and the brake element are designed as one piece, wherein: the static or dynamic friction coefficient between the friction surface of the brake element and the output shaft differs by at least a factor of 1.3, and an EMK brake is provided for the drive motor.

Description

[0001] The present invention relates to a furniture actuator having an electric drive motor and a braking device for the electric drive motor, wherein the drive motor has an output shaft and the braking device has at least one braking element and an accumulator acting on the output shaft, wherein the accumulator permanently applies braking force to the braking element, and wherein the accumulator and the braking element are constructed integrally with each other.

[0002] Electric drive motors are used in a variety of applications, including electric furniture actuators for adjusting furniture components. Furniture components can be, for example, the head or foot sections of a bed or chair. The driving force of the drive motor is typically transmitted to the furniture components via a worm gear drive with a downstream spindle driver. The worm gear drive consists of a worm mounted or formed on the output shaft of the drive motor, together with a worm wheel engaged with the worm. Worm gear drives offer the advantage of high frictional interlocking, thereby preventing furniture components under weight from falling when the motor is off.

[0003] Especially in the nursing field, the requirements for self-interlocking are very high. For example, even if the patient is in an unfavorable position, the headboard or footboard of the bed should not lower. To meet these high requirements, in addition to interlocking via a worm gear drive, it may be necessary to provide a braking device that brakes the motor's output shaft when the motor stops, thereby reliably preventing furniture parts from falling.

[0004] Such a braking device can be configured as an active controllable brake, which is, for example, electromechanically actuated to brake the output shaft of the motor when the motor stops.

[0005] Alternatively, an inactively controlled brake can also be used for the output shaft of the electric drive motor. Such brakes are known from documents DE 202004 008 713 U1 and DE 20 2004 008 714 U1. In these braking devices, the output shaft is subjected to a slight permanent brake, which is overcome by the torque of the drive motor during operation, but is still large enough to prevent accidental rotation of the electric drive motor due to the loading of adjustable furniture components, in conjunction with the self-locking of the worm gear mechanism, when the machine is stopped.

[0006] The braking devices proposed in the aforementioned literature all possess an accumulator device (e.g., a spring) that permanently applies braking force to the braking element. For example, the braking force presses the braking element against a brake rotor, which is connected to the output shaft of the motor in an anti-rotational manner. Compared to actively controlled braking devices, this braking device has a simpler structure and is therefore generally less expensive. However, this braking device is not without its manufacturing challenges, as it is essential to ensure that the accumulator and braking element, which are typically made of different materials, are securely connected to each other without increasing manufacturing workload.

[0007] A passive braking device is known from document WO 2017 / 016618 A1, in which the accumulator and braking element are constructed as a single unit. This is based on the idea that, with proper shaping, the braking element itself can achieve a spring effect sufficient to apply the desired braking force. For example, the braking device can be constructed as annular, wherein the closed annular base has a central opening for accommodating a portion of the output shaft of the drive motor. Preferably, radially and / or obliquely extending, and inwardly and / or outwardly opening slits are introduced into the base. Since the base is closed in the circumferential direction, the base can apply a radially acting braking force to the output shaft guided through the central opening.

[0008] The braking device described in document WO 2017 / 016618 A1 is easy to manufacture and inexpensive, and has been particularly successful in electric furniture actuators.

[0009] The purpose of this invention is to further improve the furniture actuator of the above type with an electric drive motor and a braking device, so as to achieve the best possible braking effect when stationary with only low loss during operation.

[0010] This task is accomplished by a furniture actuator having the features of the independent claims. Advantageous designs and improvements are given in the dependent claims.

[0011] The furniture actuator of the type described at the beginning, according to the invention, is characterized in that, in the braking device, the static friction coefficient or dynamic friction coefficient between the friction surface of the braking element and the output shaft differs by at least 1.3 times, and particularly by at least 1.5 times. Furthermore, the furniture actuator is also provided with an EMK (electro-dynamic) brake, which is activated, for example, by inducing a short circuit at the connector of the drive motor through the control device of the furniture actuator.

[0012] This invention is based on the understanding that the combination of an EMK brake and a passive friction brake achieves particularly good braking characteristics when there is a relatively large difference between the static and dynamic friction coefficients of the paired braking elements / output shafts. This can be achieved, for example, through appropriate material selection and surface properties, where the output shaft is typically made of solid but unhardened steel. The larger the difference, the better the braking effect when the drive motor is stopped and the lower the braking effect when the drive motor is rotating, resulting in low losses during operation.

[0013] Because of the regenerative effect, the higher the drive motor speed, the more effective the EMK brake. Therefore, with the EMK brake, the drive motor can quickly transition from high to low speeds. The EMK brake can be easily implemented with only a few components. Once a low speed is reached, the passive braking mechanism comes into play because the higher static friction coefficient relative to the dynamic friction coefficient results in a higher braking effect not only when the output shaft is stationary, but also at low speeds and near-stationary conditions. This is because, due to the elastic deformation within the braking device, even when the output shaft is still rotating at low speeds, the friction surfaces experience a brief period of stillness relative to the output shaft surface, leading to a transition from dynamic to static friction. Even when static friction is overcome again as the output shaft continues to rotate, the static friction effect remains briefly active, thus averaging higher than pure dynamic friction. Therefore, the braking effect is actually greater than that of the dynamic friction coefficient. At a given speed, the larger the ratio between the static and dynamic friction coefficients, the greater the time proportion during which this effect occurs. As the time proportion increases, the increment in braking effect due to this effect while the output shaft is still rotating also increases.

[0014] Because of the significant difference between the dynamic and static frictions of the braking device, a distinct transition range for the braking effect is formed, extending from low speed (i.e., near-stationary speed) to zero speed. This distinct transition range is in the range of zero to 1 revolution per second. Preferably, the span and physical characteristics of the transition range are independent of the direction of rotation, but alternatively, and depending on the geometry and surface properties of the friction surfaces, they vary according to the direction of rotation.

[0015] Particularly preferably, the furniture actuator is configured as a spindle actuator, particularly a spindle lifting actuator. Through the spindle, and if necessary, in conjunction with a worm gear actuator, the furniture actuator already possesses a high degree of self-locking capability. Safety braking is achieved by combining the passive braking device according to the invention with the EMK brake.

[0016] For example, zinc or bronze, or plastics that are as heat-resistant as possible (e.g., PEEK (polyether ether ketone)) can be used as materials for braking components.

[0017] The aforementioned materials are generally softer than those commonly used in output shafts (i.e., unhardened solid steel), so braking of the output shaft will not cause surface damage. Nevertheless, the hardness of these materials is sufficient to achieve a braking effect, and wear is minimized, resulting in a longer service life. Furthermore, if other media such as lubricants are used simultaneously, and these media can be applied in thin layers, the service life will be further extended. If chosen properly, lubricants will not decrease the coefficient between static and kinetic friction; on the contrary, they may even increase it.

[0018] In a favorable design for furniture actuators, the accumulator and braking elements are made of the same material, which can further reduce manufacturing costs and manufacturing difficulty.

[0019] In another advantageous design of the furniture actuator, the braking device is configured as annular, wherein the closed annular base has a central opening for accommodating a portion of the output shaft of the drive motor. Preferably, radially and / or obliquely extending, and inwardly and / or outwardly opening slits are introduced into the base. Because the base is closed in the circumferential direction, it can apply a radial braking force to the output shaft guided through the central opening, i.e., without the need for external support.

[0020] The slits reduce the material thickness of the annular matrix, making it easier for the matrix to expand and achieve the desired spring effect. Here, the desired spring force and spring travel can be set for the matrix material used by varying the number and depth of the slits. Therefore, a relatively hard and not particularly elastic material can be used for the matrix, so that despite the application of braking force, wear on the matrix is ​​minimal, and a spring effect with sufficient spring travel and the desired, and particularly not too strong, spring force is still produced. Preferably, multiple slits can be arranged in a star shape. Preferably, inwardly opening slits and outwardly opening slits can alternate circumferentially.

[0021] In the aforementioned annular design of the braking device, the braking device can be inserted into the output shaft in a simple and space-saving manner, resting against the motor housing, or inserted into a receiving portion within the motor housing. To secure the braking device, it is only necessary to prevent axial slippage of the motor shaft, which can be achieved through retaining or locking protrusions. Furthermore, it is also necessary to prevent rotation of the braking device, which can also be achieved, for example, through locking or retaining protrusions arranged on the motor housing. These protrusions can, for example, engage in the aforementioned cutouts in the base of the braking device. Alternatively, protrusions can be arranged on the outer periphery of the base, these protrusions cooperating with recesses of retaining elements arranged, for example, on the motor housing, and securing the braking device non-rotatably to the motor housing. Retaining or locking protrusions or retaining elements can be arranged or formed on the motor housing itself or on the motor bracket.

[0022] Particularly advantageously, the surface of the substrate itself forms the friction surface of at least one braking element. In this way, a particularly simple structure of the braking device is achieved, especially when the braking element is made of plastic by injection molding.

[0023] Alternatively, at least one additional ring segment can be applied to the substrate, the ring segment pointing towards the central opening. In this case, the surface of the ring segment forms the friction surface of at least one braking element. Thus, regardless of the material of the substrate, a friction surface particularly suitable for braking can be provided.

[0024] In another advantageous design of the furniture drive, the braking device is constructed in or on the motor bracket, such as a motor retaining plate or a motor flange housing. This further reduces the manufacturing and installation costs of the furniture drive. One embodiment of the motor flange housing is formed by the housing portion or transmission housing portion of the furniture drive, to which the motor is mounted and secured via a flange. Here, the housing or transmission housing has a housing for the braking device. The housing can be configured as a recess into which the braking device can be inserted. The housing for the braking device has protrusions or recesses as described above for anti-rotational connection and anti-rotational retention of the braking device.

[0025] Alternatively, the braking device can also be integrated into the electric drive motor with the same advantages, and therein it also functions as a sliding bearing for the output shaft. Specifically, the rear axle bearing of the drive motor is typically not constructed as a ball bearing, but rather as a sliding bearing. The sliding bearing provided according to the standard can be replaced by the braking device according to the invention, which has the function of a sliding bearing.

[0026] This braking device can be used in gearless drive motors, where the output shaft is the motor's armature shaft. However, it can also be used in geared motors, where the motor and transmission mechanism are, if necessary, a single unit, and where the output shaft is a gear shaft.

[0027] The invention will now be described in more detail with reference to exemplary embodiments and the accompanying drawings. In the drawings: Figure 1 An isometric overall view of the furniture drive is shown; Figure 2 The diagram is shown in partial exploded view. Figure 1 Furniture driver; Figure 3 It shows the one without a drive motor. Figure 1 Side view of the furniture drive; Figure 4a , Figure 4b Isometric views of the drive motor are shown, with the braking device positioned on the output shaft of the drive motor. Figure 4c It shows that there is no braking device. Figure 4a and Figure 4b A diagram of the drive motor; Figure 5a , Figure 5b They are shown respectively Figure 4a and Figure 4b Top view and isometric view of the braking element; Figures 6a to 6c Isometric views of another embodiment of the braking device are shown respectively; and Figure 7a , Figure 7b , Figure 8 Top views of another embodiment of the braking device are shown.

[0028] First of all Figure 1 The electric furniture actuator 20 is shown in an isometric overall view. The furniture actuator 20 is a so-called spindle lifting actuator, in which the rotational motion of the drive motor 1 is converted into linear lifting motion by means of a spindle.

[0029] For this purpose, the furniture drive 20 has a transmission housing 21, on which the drive motor 1 is fixed. The transmission housing 21 is provided with a mounting element 22, which is a mounting hole, through which the furniture drive 20 is connected to the furniture on one side.

[0030] The transmission box 21 is also equipped with a guide tube 23 or is integrated with the guide tube 23, which guides the lifting tube 24 that can move back and forth through the aforementioned main shaft. The free end of the lifting tube 24 is also connected to the furniture to transmit the motion to the furniture.

[0031] Figure 2 An isometric exploded view of the furniture drive 20 is shown. Figure 3 A side view of a portion of the furniture drive 20 is shown. Figure 3 In this case, the drive motor 1 is removed so that the area of ​​the transmission box 21, where the drive motor 1 is fixed, can be observed.

[0032] In this example, a cup-shaped motor flange receiving portion 25 is formed on the transmission housing 21, and the drive motor 1 passes through the flange plate (see...). Figure 4a The reference numeral 3) in the attached drawing is inserted into the motor flange receiving portion 25, and the drive motor 1 is tightened to the motor flange receiving portion 25. For example... Figure 2 As shown, the drive motor 1 itself has a housing 2, and the output shaft 5 extends beyond the housing 2 in the direction of the transmission box 21. The output shaft 5 is equipped with a worm gear 6. When the drive motor 1 is installed, the worm gear 6 extends into the transmission box 21 and meshes with a worm wheel (not visible here), which drives the aforementioned main shaft.

[0033] A recess is formed at the center of the motor flange receiving portion 25. This recess serves as a brake ring receiving portion 26, and the brake device 10 is inserted into this recess in a form-fit manner. The brake device 10 acts on a section of the output shaft 5, such as when engaged. Figure 4a , Figure 4b More detailed description. The annular braking device 10 has a cutout 12 along its circumference, into which a protrusion 27 of the brake ring receiving portion 26 engages, so that the braking device 10 is held in the brake ring receiving portion 26 in an anti-rotational manner.

[0034] Figure 4a and Figure 4b The electric drive motor 1 with braking device 10 is shown in isometric views in the same manner. Figure 4c The same view also shows drive motor 1 without a brake. Drive motor 1 and Figures 1 to 3 Similar to the drive motor in [the text], and can also be used... Figures 1 to 3 Furniture driver 20.

[0035] The drive motor 1 also has a housing 2 with a flange plate 3, on which fastening fittings (Befestigungsmöglichkeit) for the drive motor 1 are provided. Furthermore, a bearing 4 for the output shaft 5 of the drive motor 1 (see...) Figure 4cThe bearing 4 is arranged at the center of the flange plate 3. The bearing 4 can be held in the bearing housing of the flange plate 3, and can be accessed from the outside or inserted from the inside of the housing 2. A similar bearing for the output shaft 5 is arranged on the opposite side of the housing 2. Here, the bearing 4 provided in the flange plate 3 is, for example, a rolling bearing, such as a ball bearing or a roller bearing. The bearings arranged on the opposite sides can also be such rolling element bearings or sliding bearings.

[0036] The output shaft 5 extends beyond the flange plate 3. In addition to an optional journal, the end of the output shaft 5 is provided with a worm gear 6. The worm gear 6 can be a separate component mounted on the output shaft 5, or it can be integrally constructed with the output shaft 5. In the region of the bearing 4, the output shaft 5 first extends beyond the flange plate 3 as a shaft section 7, and then the worm gear 6 is connected to this shaft section 7. The shaft section 7 is constructed as a cylinder with a smooth surface, wherein the diameter of the shaft section 7 at least slightly exceeds the outer diameter of the worm gear 6.

[0037] like Figures 4a to 4c As shown, the braking device 10 is configured as annular in each case and inserted into the output shaft 5 such that the braking device 10 rests substantially against the flange plate 3 and acts on the shaft section 7 of the output shaft 5.

[0038] according to Figure 4a and Figure 4b Two embodiments of the braking device 10 are respectively in Figure 5a and Figure 5b It is shown in more detail below. Figure 5a and Figure 5b The upper part shows a top view of the braking device 10, and the lower part shows an isometric view of the braking device 10.

[0039] Figure 4a and Figure 5a The braking device 10 shown has a one-piece substrate 11. In this example, the substrate is made of a solid metallic material (e.g., zinc or bronze) or a hard and preferably heat-resistant plastic (e.g., PEEK). The material combination and surface properties of the friction surfaces of the shaft section 7 and the braking device 10 are selected such that the static or dynamic coefficient of friction between the friction surfaces and the output shaft differs by at least 1.3 times, and particularly by at least 1.5 times. Taking polymer plastics as an example, the type of crosslinking also has a significant impact on the level of this coefficient. In particular, radiation-crosslinked plastics have a higher static coefficient of friction than dynamic coefficient of friction. Here, the thickness of the substrate 11 is in the range of a few millimeters, and therefore substantially corresponds to the length of the shaft section 7 (see...). Figure 4c ).

[0040] An outwardly projecting notch 12, hereinafter also referred to as the outer notch 12, is introduced into the base 11. Six outer notches 12 are provided here, evenly distributed in a star shape. Due to the outer notches 12, radially protruding segments 13 are retained in the outer region of the base 11, which can be used to secure the braking device 10 in an anti-rotation manner. For example, a protrusion can be formed on the segment 13, which engages into a position-fixed retaining groove (relative to the housing 2 of the drive motor 1). Alternatively, a position-fixed protrusion engaging into the notch 12 (see...) can also be used. Figure 2 Reference numeral 27 in the attached figure is used to provide anti-rotation retention, such as Figure 2 As shown in the embodiments.

[0041] Offset relative to the outer cut 12 is the inner cut 15, which cuts the base 11 outward from the central opening 14. Due to the outer cut 12 and the inner cut 15, the braking device 10 obtains a spring effect in the radial direction. Between the inner cuts 15 within the region of the central opening 14, sections of the base 11 are retained, which act as braking elements 17 pressing against corresponding shaft sections 7 of the output shaft 5. By adjusting the number and depth of the inner cuts 15 and the outer cut 12, the spring effect of the base 11 can be varied over a wide range to meet desired requirements.

[0042] exist Figure 4b and Figure 5b The diagram shows a second embodiment of the braking device 10. The basic structure of the braking device 10 corresponds to that shown in the diagram. Figure 4a and Figure 5a The basic structure of the first embodiment. However, the difference is that the outer cut 12 and the inner cut 15 do not extend radially, but rather extend obliquely outward or inward. In an alternative design, it can be specified that only the outer cut 12 or only the inner cut 15 extends obliquely, while other types of cuts 12, 15 extend radially.

[0043] By using the inclined positions of at least one type of cutout 12, 15, asymmetry in braking behavior is achieved with respect to the rotation direction of the output shaft 5 relative to the braking device 10. Depending on the rotation direction of the output shaft 5, the braking element 17 is affected upwards or downwards, thereby enhancing the braking effect in one direction and weakening the braking effect in the other. For example, this can be achieved in an electric furniture actuator, where a braking effect is enhanced in the direction in which furniture parts may begin to lower due to increased weight.

[0044] exist Figures 6a to 6c The image shows three other embodiments of the braking device 10 according to this application, reproduced in isometric views. The basic structure of these braking devices 10 also corresponds to that according to... Figure 4a and Figure 5a The basic structure of the first embodiment is hereby explicitly referred to in its description. In these and all subsequent embodiments, the same reference numerals denote elements that are the same as or function the same as those in the foregoing embodiments.

[0045] According to Figure 6a The braking device 10 has three braking elements 17 instead of the six braking elements 17 shown in the first embodiment, and correspondingly, it also has three internal cutouts 15 and three external cutouts 12. In principle, the braking device 10 shown can also be configured to have only two braking elements 17, without changing the basic structure and operating mode.

[0046] In essence, it also corresponds to the following: Figure 4a and Figure 5a The first embodiment Figure 6b and Figure 6c In the embodiment shown, five braking elements 17 are provided, along with five corresponding internal cutouts 15 and external cutouts 12. Figure 6b In one embodiment, the substrate 11 is thinner inside in the radial direction than its outer edge. Figure 6c In one embodiment, the braking device 10 has a greater thickness in the region of the braking element, which can be selected, for example, to be the same as the thickness of the outer region.

[0047] By using the outline of the base 11 shown, material savings can be achieved, thereby reducing costs or weight, and the spring force can be affected.

[0048] Other parameters that can affect the spring force are the total diameter (outer diameter) of the braking device 10, the number of braking elements 17 or internal cutouts 15 and external cutouts 12, and the depth of internal cutouts 15 or external cutouts 12.

[0049] In essence, it also corresponds to the following: Figure 4a and Figure 5a The first embodiment Figure 7a and Figure 7b In the embodiment shown, three braking elements 17 are provided.

[0050] exist Figure 7a In one embodiment, the substrate 11 is constructed as a closed loop and is designed to be elastic. For example, the elastic effect is achieved through the arcuate connection portion of the substrate 11 between the braking elements 17. Figure 7aThe embodiment has outwardly projecting protrusions 18 on the outer circumferential surface of the annular base 11, here in the form of a stem, for anti-rotational connection. Each protrusion 18 is angularly offset from the braking element 17, wherein the angular offset is 60°, thus the protrusions 18 and the braking element 17 are arranged symmetrically. However, it should be noted that the position of the protrusions 18 relative to the braking element 17 can also be chosen differently than shown here, for example, arranged concentrically and identically to each other.

[0051] according to Figure 7b The embodiment has an inwardly oriented cutout 12 on the outer circumferential surface of the annular base 11 for an anti-rotation connection. Since the cutout extends from the outside into the braking element 17, in this embodiment, the base 11 can still be considered closed or substantially closed. For example, according to... Figure 7a and Figure 7b The embodiment shows three protrusions 18 or three inwardly oriented cuts 12, wherein alternatively, at least one protrusion 18 or one cut 12 is provided.

[0052] Figure 8 The illustration shows another alternative design for the braking device 10, which has a base 11 and three braking elements 17. This is also a ring-shaped design, where the base 11 is configured as a disc-shaped ring with a continuous cut that begins at a central opening 14, is introduced into the base, and extends through the base to the outer circumferential surface. Therefore, the cut can be considered as a combination of an inner cut 15 and an outer cut 12. Furthermore, a protrusion 18 is provided on the outer circumferential surface of the base 11 to prevent torsion. Only one web is shown as an example; alternatively, more webs may be provided.

[0053] according to Figure 7a , Figure 7b and Figure 8 The arrangement of the braking device and the corresponding anti-rotation connection in the implementation scheme are carried out according to the above implementation scheme, which is hereby stated.

[0054] Reference Marker 1. Drive motor 2. Outer shell 3 Flange plate 4 bearings 5 Output shaft 6. Worm 7-axis section 10. Braking device 11 Matrix 12 External incision 13 Extended sections 14. Center opening (shaft housing) 15 Internal incision 17 Braking components 18. Protrusion 20 Furniture Drivers 21. Transmission box 22 Installation device 23. Guide tube 24. Riser pipe 25 Motor flange housing 26 Brake ring receiving part 27. Protrusion.

Claims

1. A furniture actuator having an electric drive motor (1) and a braking device (10). in, The drive motor (1) has an output shaft (5) that extends beyond the motor housing (2). The braking device (10) includes at least one braking element (17) and an accumulator, wherein the accumulator permanently applies braking force to the friction surface of the at least one braking element (17), and wherein the accumulator and the braking element (17) are constructed as a single unit. Its features are, The static or dynamic friction coefficient between the friction surface of the braking element (17) and the output shaft (5) differs by at least 1.3 times, and An EMK brake was provided for the drive motor (1).

2. The furniture drive (20) according to claim 1, wherein, The accumulator and the braking element (17) are made of the same material.

3. The furniture drive (20) according to claim 1 or 2, having an annular base (11) that is at least circumferentially closed in the outer region.

4. The furniture actuator (20) according to claim 3, comprising a central opening (14) having an inner surface forming the friction surface of the braking device (10).

5. The furniture drive (20) according to claim 4, having at least one cut (15) introduced into the annular base (11) from the central opening (14).

6. The furniture drive (20) according to any one of claims 4 to 5, having at least one additional cut (12) introduced into the annular base (11) from the outer periphery of the annular base (11).

7. The furniture actuator (20) according to claim 5 or 6, wherein, The annular substrate (11) has multiple cuts (15) and / or multiple additional cuts (12) in each case, which are arranged in a star shape.

8. The furniture drive (20) according to claim 7, wherein, The annular substrate (11) has multiple cuts (15) and multiple additional cuts (12) in each case, wherein the cuts (15) and the additional cuts (12) alternate in the circumferential direction.

9. The furniture drive (20) according to any one of claims 4 to 8, wherein, The annular matrix (11) is made of solid material in the shape of a disk.

10. The furniture actuator (20) according to claim 9, wherein, The annular matrix (11) is made of zinc, bronze or PEEK.

11. The furniture actuator (20) according to claim 8 or 9, wherein, The surface of the annular base (11) forms the friction surface of the at least one braking element (17).

12. The furniture actuator (20) according to claim 8 or 9, wherein, At least one additional ring segment is applied to the annular base (11) and points toward the central opening (14), wherein the surface of the at least one ring segment forms the friction surface of the braking element (17).

13. The furniture drive (20) according to any one of claims 1 to 12, wherein, The braking device (10) is arranged in or on the motor bracket.

14. The furniture drive (20) according to any one of claims 1 to 12, wherein, The braking device (10) is integrated into the electric drive motor (1).

15. The furniture actuator (20) according to claim 14, wherein, The braking device (10) is configured as a sliding bearing for the output shaft (5) of the electric drive motor (1).

16. The furniture drive (20) according to any one of claims 1 to 15, wherein, The EMK brake is activated by a short circuit at the terminal of the drive motor (1) by the control device of the furniture actuator (20).

17. The furniture drive (20) according to any one of claims 1 to 16, wherein the furniture drive is configured as a spindle drive.

18. The furniture drive (20) according to claim 17, wherein, The spindle drive is a spindle lifting drive.

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